Homopolar DC electromagnetic transmission and application system thereof

Abstract

A homopolar DC electromagnetic transmission (HET) and an application system thereof are provided. The HET includes two rotors, a stator, an external auxiliary system and an adjustment control system. Each of the rotors has one or more axisymmetric rotor magnetic conductors, and the stator has one or more direct current magnet exciting coils wound around an axis of a rotation shaft. A main magnetic circuit is guided to be a closed ring. The HET includes at least two main magnetic circuits. The HET includes a closed main current loop. The loop is connected with all the rotor magnetic conductors, a rotor electric conductor, a dynamic/static circuit connecting medium, stator conductors and stator magnetic conductors in series or in series and parallel. A direction of main current on the rotor magnetic conductors is perpendicular to a direction of magnetic flux (ϕ) on meridian plane.

Claims

1. A homopolar DC electromagnetic transmission, comprising: two rotors, a stator, an external auxiliary system, and a regulation and control system, wherein: the two rotors are respectively connected to a first shaft and a second shaft, wherein the first shaft is independent to the second shaft, both the first and the second shafts extend along an axial direction, each rotor at least has one axisymmetric rotor magnetic and electric conductor (3), and two sides of each rotor magnetic and electric conductor (3) are respectively connected to one rotor electric conductor (4) in the axial direction; the stator at least has one DC magnet exciting coil (9) wound around the axial direction, and the stator comprises two stator magnetic and electric conductors (7) and two stator electric conductors (6), each of the stator magnetic and electric conductors (7) surrounds one of the rotor magnetic and electric conductors (3) in a radial direction perpendicular to the axial direction, and each of the stator electric conductors (6) surrounds one of the rotor electric conductors (4) in the radial direction; a main magnetic circuit (22) is guided to be a closed loop by axisymmetric magnetic conduction structural members on the rotor and the stator; at least two main magnetic circuits (22) pass through rotor magnetic and electric conductors (3) and stator magnetic and electric conductors (7); and the first shaft and the second shaft guide magnetic flux of the two main magnetic circuits (22) to be connected to magnetic flux passing through the rotor magnetic and electric conductors (3); a closed main current (I0) circuit (23) is constructed on the two rotors and a stator and is connected in series with all the rotor magnetic and electric conductors (3), rotor electric conductors (4), rotor and stator circuit connecting media (5), stator electric conductors (6, 11) and stator magnetic and electric conductors (7); and the main current direction of each rotor magnetic and electric conductor (3) is mutually perpendicular to a direction of the magnetic flux (Φ) in a meridian plane.

2. The homopolar DC electromagnetic transmission according to claim 1, wherein the homopolar DC electromagnetic transmission is applied to a fuel engine power system for vehicles; and the system comprises an engine for burning fuel to output shaft power, a transmission system which transmits engine power to a drive bridge main reducer, and a corresponding control system, wherein the transmission system comprises the homopolar DC electromagnetic transmission.

3. The homopolar DC electromagnetic transmission according to claim 1, wherein the homopolar DC electromagnetic transmission is applied to a flywheel power system for vehicles; and the system comprises an energy storage flywheel device, a transmission system from a flywheel device to the drive bridge main reducer and a corresponding control system, wherein the transmission system includes the homopolar DC electromagnetic transmission.

4. The homopolar DC electromagnetic transmission according to claim 1, wherein the homopolar DC electromagnetic transmission is applied to a fuel engine and flywheel hybrid power system; and the system comprises an engine used for burning fuel to output shaft work, an energy storage flywheel device, a transmission system which is connected with the engine, the flywheel device and a drive bridge main reducer and a corresponding control system, wherein the transmission system includes the homopolar DC electromagnetic transmission.

5. The homopolar DC electromagnetic transmission according to claim 1, wherein the homopolar DC electromagnetic transmission is applied to a mechanical connection and load charging system for energy storage flywheel of vehicles; and the system comprises a loading joint and a rotation shaft which are in mechanical connection with a loading disc at the lower end of the flywheel rotation shaft during operation, a motor or a DC power supply connected with an AC power grid and a transmission system for transfering the output energy of the motor or the DC power supply to the loading joint, wherein the transmission system includes the homopolar DC electromagnetic transmission.

6. The homopolar DC electromagnetic transmission according to claim 1, wherein the homopolar DC electromagnetic transmission is applied to a wind power generation system; and the system comprises a wind wheel, a generator, a transmission system which is connected with the wind wheel and the generator and a corresponding control system, wherein the transmission system includes the homopolar DC electromagnetic transmission.

7. The homopolar DC electromagnetic transmission according to claim 1, wherein the homopolar DC electromagnetic transmission is applied to a wind power generation system with the energy storage flywheel; and the system comprises a wind wheel, a generator, an energy storage flywheel device, an energy transfer system and a corresponding control system, wherein the energy transfer system includes the homopolar DC electromagnetic transmission.

8. The homopolar DC electromagnetic transmission according to claim 1, wherein the homopolar DC electromagnetic transmission is applied to an energy storage and conversion system; and the system comprises an energy storage flywheel device, a moto, a transmission device between a flywheel and the motor and a corresponding control system, wherein the transmission device adopts the homopolar DC electromagnetic transmission.

Description

DESCRIPTION OF DRAWINGS

(1) In the following figures, half of a section view (or a schematic diagram) on one side of a central axis is drawn only based on an axisymmetric structure in some figures.

(2) FIG. 1 is a meridian plane schematic diagram of a centralized type, two-axis single-magnetic flux (without two-axis sharing), far-axis coil, solid shaft, axial plane type, permanent magnet excited HET;

(3) FIG. 2 is a meridian plane schematic diagram of a centralized type, two-axis (one-single one-double magnetic flux) (two-axis sharing), far-axis coil, solid shaft, axial plane type, permanent magnet excited, intermediate external terminal led-out, HET;

(4) FIG. 3 is a meridian plane schematic diagram of a centralized type, two-axis (one-single one-double magnetic flux) (two-axis sharing), far-axis coil, solid shaft, axial plane type, permanent magnet excited, external terminal led-out on one side of single magnetic flux, HET;

(5) FIG. 4 is a meridian plane schematic diagram of a centralized type, two-axis (one-single one-double magnetic flux) (two-axis sharing), far-axis coil, solid shaft, axial plane type, permanent magnet excited, HET;

(6) FIG. 5 is a meridian plane schematic diagram of a centralized type, two-axis two-double magnetic flux (two-axis shared), far-axis coil, solid shaft, axial plane type, HET;

(7) FIG. 6 is a meridian plane schematic diagram of a centralized type, two-axis two-double magnetic flux (without two-axis sharing in form), far-axis coil, solid shaft, axial plane type, same two-axis rotation direction, HET;

(8) FIG. 7 is a meridian plane schematic diagram of a centralized type, two-axis two-single magnetic flux (without two-axis sharing in form), solid shaft, axial plane type (axial magnetic flux gap, axial attraction offset design), HET;

(9) FIG. 8 is a meridian plane schematic diagram of a separated type, single-magnetic flux, near-axis coil, solid shaft, axial plane type, HET half-coupled member;

(10) FIG. 9 is a meridian plane schematic diagram of a separated type, double-magnetic flux, near-axis coil, solid shaft, axial plane type, HET half-coupled member;

(11) FIG. 10 is a meridian plane schematic diagram of a separated type, double-magnetic flux, near-axis coil, hollow shaft, axial plane type, HET half-coupled member;

(12) FIG. 11 is a meridian plane schematic diagram of a separated type, double-magnetic flux, outer rotor, axial plane type, HET half-coupled member;

(13) FIG. 12 is a meridian plane schematic diagram of a separated type, double-magnetic flux, two-stage external series, near-axis coil, solid shaft, axial plane type, HET half-coupled member;

(14) FIG. 13 is a meridian plane schematic diagram of a separated type, double-magnetic flux, three-stage external series, near-axis coil, solid shaft, axial plane type, HET half-coupled member;

(15) FIG. 14 is a meridian plane schematic diagram of a separated type, double-magnetic flux, two-stage internal series, near-axis coil, solid shaft, axial plane type, HET half-coupled member;

(16) FIG. 15 is a meridian plane schematic diagram of a separated type, double-magnetic flux, near-axis coil, solid shaft, axial plane type, rotor electric conductor not-full-height HET half-coupled member;

(17) FIG. 16 is a meridian plane schematic diagram of a centralized type, two-axis two-double magnetic flux (without two-axis sharing in form), near-axis coil, solid shaft, axial plane type, opposite two-axis rotation directions, HET;

(18) FIG. 17 is a meridian plane schematic diagram of a separated type, single-magnetic flux, near-axis coil, solid shaft, axial plane type, shaft end collector design, HET half-coupled member;

(19) FIG. 18 is a meridian plane schematic diagram of a centralized type, double-circuit, solid shaft, axial plane type, HET;

(20) FIG. 19 is a meridian plane schematic diagram of a separated type, double magnetic flux, near-axis coil, solid shaft, axial plane type, HET half-coupled member;

(21) FIG. 20 is a meridian plane diagram of a centralized type, two-axis two-single magnetic flux (without two-axis sharing in form), solid shaft, axial plane type (axial magnetic flux gap, axial attraction offset design), HET;

(22) FIG. 21 is a meridian plane diagram of a centralized type, two-axis two-double magnetic flux (two-axis shared), near-axis coil, solid shaft, axial plane type, HET;

(23) FIG. 22 is a meridian plane diagram of a centralized type, two-axis two-double magnetic flux (two-axis shared), near-axis coil, solid shaft, axial plane type, external terminal led-out, HET;

(24) FIG. 23 is a meridian plane diagram (I) of a flexible flywheel and separated HET half-coupled member (part A);

(25) FIG. 24 is a meridian plane diagram of a flexible flywheel and centralized HET (part A);

(26) FIG. 25 is a meridian plane diagram of a flexible flywheel shell and protective sleeve;

(27) FIG. 26 is a meridian plane diagram (II) of a flexible flywheel and a separated HET half-coupled member (part A);

(28) FIG. 27 is a schematic diagram of arrangement of a flywheel and a separated HET non-flywheel shaft half-coupled member for a four-wheel-drive car power system;

(29) FIG. 28 is a schematic diagram of arrangement of an engine, a flywheel and a separated HET non-flywheel shaft half-coupled member for a car hybrid power system;

(30) FIG. 29 is a diagram of external terminal and mixed flexible cable (I) of two-stage external series separated HET half-coupled members;

(31) FIG. 30 is a diagram of a load-end vertical separated half-coupled member HETho meridian plane (section A-A of FIG. 29) (double-magnetic flux, near-axis coil, two-stage external series, non-full-height conductor);

(32) FIG. 31 is a diagram of an energy supply end vertical separated half-coupled member HEThi meridian plane (double magnetic flux, near-axis coil, solid shaft, two-stage external series, non-full-height conductor);

(33) FIG. 32 shows a load joint, an upper-end structure of a load rotation shaft and supporting members (an intersection angle 135° is formed between left half section and right half section);

(34) FIG. 33 shows a load joint and a flywheel loading disc (an intersection angle 135° is formed between left half section and right half section);

(35) FIG. 34 is a meridian plane schematic diagram of a centralized type, two-axis single magnetic flux (without two-axis sharing), far-axis coil, solid shaft, axial plane type, HET;

(36) FIG. 35 is a meridian plane schematic diagram of a centralized type, two-axis (one-single one-double magnetic flux) (two-axis sharing), far-axis coil, solid shaft, axial plane type, intermediate external terminal led-out, HET;

(37) FIG. 36 is a meridian plane schematic diagram of a centralized type, two-axis (one-single one-double magnetic flux) (two-axis sharing), far-axis coil, solid shaft, axial plane type, external terminal led-out on one side, HET;

(38) FIG. 37 is a meridian plane schematic diagram of a centralized type, two-axis (one-single one-double magnetic flux) (two-axis shared), far-axis coil, solid shaft, axial plane type, led-out external terminal free, HET;

(39) FIG. 38 is a meridian plane schematic diagram of a separated type, double magnetic flux, near-axis coil, solid shaft, axial plane type, single-stage, horizontal HET half-coupled member (section A-A of FIG. 39);

(40) FIG. 39 shows external terminal and mixed flexible cable of single-stage separated HET half-coupled members;

(41) FIG. 40 shows a wind power generation system having HET;

(42) FIG. 41 shows a wind power generation system having flywheels and HET;

(43) FIG. 42 is a diagram (I) of an intersecting cross-shaft universal joint;

(44) FIG. 43 is a diagram (II) of an intersecting cross-shaft universal joint;

(45) FIG. 44 is a diagram of revolute pairs of universal joints;

(46) FIG. 45 is a diagram of intersecting cross-shaft universal joints;

(47) FIG. 46 is a diagram of semi-rings at ends of circular chains;

(48) FIG. 47 is a diagram of rings of circular chains;

(49) FIG. 48 is a diagram of rings with beams of circular chains;

(50) FIG. 49 is a diagram of circular chains with an intermediate circular ring;

(51) FIG. 50 is a diagram of circular chains with three intermediate circular rings;

(52) FIG. 51 is a meridian plane diagram (I) of a set of flexible flywheel bodies;

(53) FIG. 52 is a meridian plane diagram (II) of a set of flexible flywheel bodies;

(54) FIG. 53 is a meridian plane diagram (III) of a set of flexible flywheel bodies;

(55) FIG. 54 is a meridian plane diagram (IV) of a set of flexible flywheel bodies;

(56) FIG. 55 shows a spline, thread and flange connecting structure of a rotation shaft and a pulling torque transfer flexible transmission part;

(57) FIG. 56 shows a thread and flange connecting structure of a rotation shaft and a pulling torque transfer flexible transmission part;

(58) FIG. 57 shows a direct thread connecting structure of a rotation shaft and a pulling torque transfer flexible transmission part (semi-rings of circular chains are shown in the figure);

(59) FIG. 58 shows an external flange connecting structure for a center shaft and a pulling torque transfer flexible transmission part;

(60) FIG. 59 shows connection between multiple sets of series wheel bodies and a multi-section cylindrical center shaft (I);

(61) FIG. 60 shows an axial permanent magnetic bearing and a lower-end radial bearing (I);

(62) FIG. 61 shows an axial permanent magnetic bearing and a lower end radial bearing (II);

(63) FIG. 62 shows a suspended flexible flywheel upper-end structure (I);

(64) FIG. 63 shows a suspended flexible flywheel upper-end structure (II);

(65) FIG. 64 shows a suspended flexible flywheel device (rated stored energy of 1567 kWh);

(66) FIG. 65: an attractive stationary disc for axial supporting permanent magnetic bearings;

(67) FIG. 66 is a meridian plane diagram of a horizontal separated HET half-coupled member HETfhe (double magnetic flux, near-axis coil, hollow shaft, axial plane type, single-stage);

(68) FIG. 67 is a meridian plane diagram of a vertical separated HET half-coupled member HETfhf (double magnetic flux, near-axis coil, solid shaft, axial plane type, single-stage);

(69) FIG. 68 shows connection between a flywheel-side vertical separated HET half-coupled member (HETfhf) and a suspended flexible flywheel;

(70) FIG. 69 is a meridian plane diagram of a suspended flexible flywheel (176) and a flywheel-side HET half-coupled member (HETfhf, 177);

(71) FIG. 70 shows connection between multiple sets of series wheel bodies and a multi-section cylindrical center shaft (II);

(72) FIG. 71 shows a suspended flexible flywheel device (rated stored energy of 38465 kWh);

(73) FIG. 72 is a meridian plane diagram of a motor-side horizontal separated HET half-coupled member (section A-A of FIG. 39) (double magnetic flux, near-axis coil, solid shaft, axial plane type, single-stage);

(74) FIG. 73 is a meridian plane diagram of a flywheel-side vertical separated HET half-coupled member (section A-A of FIG. 74) (double magnetic flux, near-axis coil, solid shaft, axial plane type, two-stage external series);

(75) FIG. 74 shows an external terminal and a mixed flexible cable of two-stage external series separated HET half-coupled members (II);

(76) FIG. 75 shows connection between a flywheel-side vertical separated HET half-coupled member and a suspended flexible flywheel; and

(77) FIG. 76 shows a flywheel energy storage and conversion system including HET.

DETAILED DESCRIPTION

(78) (a) Homopolar DC Electromagnetic Transmission (HET)

(79) In the detailed design solution of a separated HET, two half-coupled members with the same structure and size are arranged. Each of the half-coupled members is of double magnetic flux, single-stage, single circuit, near-axis coil, solid half and axial plane type. A meridian plane diagram of the HET half-coupled members is shown in FIG. 19.

(80) The sizes of each of the half-coupled members are as follows: a shaft surface radius of a rotation shaft is 53 mm, a radius of a stator body is 138.65 mm, a radius of an external terminal is 213.5 mm, and an axial length of a stator is 280 mm. A designed value of a rotation speed of a rotation shaft of each of the half-coupled members is 10000 r/min, and a designed value of electromagnetic power is 240 kW. A designed value of main current is 40794 A. In a design point, a sum of total exciting current ohmic heat power of the HET, “connecting region clearance” friction power NaK liquid friction power and main current ohmic heat power is about 4% of the designed value 240 kW of the electromagnetic power.

(81) Each rotor has a rotor magnetic and electric conductor (3), and two rotor electric conductors (4), two stator electric conductors (6), two magnet exciting coils (9), two stator magnetic and electric conductors (7), two NaK metal liquid “connecting region clearances” (5) and matched channels and pipelines thereof with symmetrical structures are arranged on left and right sides of the rotor. A double-magnetic-flux magnetic circuit is also of a symmetrical structure except both ends. Supporting end covers (36) at both ends are made of aluminum alloys, and symmetry of the magnetic circuit is not influenced. Although axial magnetic attraction on the rotor is not generated, a non-magnetic requirement for a magnetic fluid sealing element (37) arranged on an end cover inner ring is met. Currents with the same amplitude and opposite directions are conducted to the two magnet exciting coils, and a generated double-magnetic-flux magnetic field is basically in bilateral symmetry. The two magnet exciting coils are connected in series together to serve as a coil which has an exciting current.

(82) A rotation shaft (2) is formed by interference fit of two parts, that is, a central fine shaft and an outer-ring annular shaft. Rolling bearings are arranged at both ends of the central fine shaft; one end with a shaft extension end is connected with an external rotation shaft, and the central fine shaft is made of 45 steel or steel 40Cr. The outer-ring annular shaft is made of 20 steel. The magnetic fluid sealing element (37) is paired with the outer-ring annular shaft, and the outer-ring annular shaft has an inner groove herein, thereby decreasing leakage flux of magnetic fluid seal and further reducing stress concentration.

(83) The magnetic and electric conductors (3) and the electric conductors (4) on the rotors are of a whole-circle structure, are in interference fit with the rotation shaft (2) and in electric insulation with the rotation shaft (2). The magnetic and electric conductors (3) are made of 20 steel, while the electric conductors (4) are made of chromium-copper Cu-0.5Cr. Bottoms of two end surfaces of the magnetic and electric conductors (3) are widened to be conical, which is favorable for magnetizing and decreasing stress concentration caused by the interference fit. The electric conductors (4) adopt a full-height design with the same outer diameter as that of the magnetic and electric conductors (3). Joint seams between the magnetic and electric conductors (3) and the electric conductors (4) are filled with NaK metal liquid. Top ends and bottom ends of the joint seams are sealed by fluorine rubber sealing bodies and adhesives. Two liquid injection holes which are circumferentially and uniformly distributed are formed in the bottoms of the electric conductors (4) and communicated with the outside and the metal liquid joints. Stoppers are arranged at outer ends of the liquid injection holes. A vacuum suction method is adopted during assembly and liquid injection. One liquid injection hole is used for vacuumizing, and the other liquid injection hole is used for injecting the NaK metal liquid. Liquid filled in the bottom liquid injection hole may be supplemented to a volume space which is increased with the rotation of the joints, thereby ensuring that the joints are always filled with the metal liquid.

(84) The stator electric conductors (6) are designed to be of a non-whole-circle top and bottom semi-split structure, so as to avoid an interference with the rotor electric conductors (4) in an integrated design during assembly (if each of the electric conductors (4) is divided into a left body and a right body, the stator electric conductors (6) may be in whole-circle split installation). Meanwhile, it is favorable for processing or installing needed channels, pipelines and connecting lines on a split surface. The electric conductors (6) are made of red copper. An inlet channel and an outlet channel for the NaK metal liquid are designed on the electric conductors (6). The outlet channel includes a branch clearance (25), a uniform-delivery buffer region clearance (27), and 16 circumferentially uniformly distributed through holes in radial arrangement (for insertion of a round pipe (28)). The inlet channel includes a second branch clearance (26), a uniform-delivery buffer region clearance (29), and 16 circumferentially uniformly distributed through holes in radial arrangement (for insertion of a round pipe (30)). The round pipes (28, 30) are made of the red copper, and when the round pipes are inserted into corresponding through holes, contact surfaces are sealed by the fluorine rubber sealing adhesives. In order to prevent the metal liquid that enters the channel from being heated too fast and causing temperature rise, a thermal insulating clearance (31) is designed, and a thermal insulating clearance is designed on an extended circuit of the round pipe (30). In order to conveniently process narrow clearances (25, 26, 27, 29 and 31) on the electric conductors (6), the electric conductors (6) are divided into 4 split bodies ((6a, 6b, 6c, 6d) sleeved in sequence, so that a wall surface of each narrow clearance is completely exposed outside during machining. A connecting seam allowance (the seam allowance has a cylindrical surface and an end surface) of the 6a and 6b and a connecting seam allowance of the 6b and 6c are sealed by fluorine rubber conductive adhesives, thereby maintaining electrical conductivity. A connecting seam allowance of the 6c and 6d is located on the top and sealed by a fluorine rubber sealing adhesive.

(85) Two axisymmetric grooves (32) are formed in the stator electric conductors (6a, 6d), inner ends of the axisymmetric grooves are semicircular, fluorine rubber hoses (33) are installed in the grooves, and the hoses are hidden in the grooves and not protruded when an internal or external pressure is a barometric pressure. Each of the hose is communicated with a ventilating pipe (34), and the ventilating pipe is made of fluorine rubber, inserted into a hose opening and adhered and sealed. The ventilating pipes pass through the electric conductors (6) and the magnetic conductors (10) and are connected to an external auxiliary system. Center lines of the ventilating pipes are located on a split surface of the electric conductors (6), that is, semicircular grooves are correspondingly formed in two half split surfaces of the electric conductors (6), and a whole circular groove is formed to accommodate the ventilating pipes when the upper and lower half split surfaces are merged. During assembly, wall surfaces of the ventilating pipes and the grooves are sealed by the fluorine rubber sealing adhesives. The ventilating pipes are axially arranged on adjacent surfaces of the electric conductors (6) and the magnetic conductors (10). When the magnetic conductors (10) in the whole-circle structure are axially installed, the ventilating pipes pass through axial through holes of corresponding magnetic conductors (10).

(86) Semicircular grooves are formed in upper and lower half split surfaces of the electric conductors (6a, 6d) close to the hoses (33), and a vent hole (35) is formed when the upper and lower half split surfaces are merged. Before the vent hole reaches a boundary of the electric conductor (6a) or the electric conductor (6d), a vent hole connecting pipe is communicated with the vent hole. The vent hole connecting pipe is made of fluorine rubber, and installation, arrangement and corresponding processing operations of the vent hole connecting pipe are the same as those of the ventilating pipes (34).

(87) The upper and lower half split surfaces of the stator electric conductors (6) are sealed by the fluorine rubber sealing adhesives during assembly and mergence.

(88) The two stator magnetic and electric conductors (7), two external terminals (16) and the two stator magnetic conductors (10) are of the whole-circle structure. The magnetic and electric conductors (7) and the magnetic conductors (10) are made of electromagnetic pure iron, and the external terminals (16) are made of the red copper. Joints between the stator electric conductors (6) and the magnetic and electric conductors (7) are filled with the NaK liquid, the NaK liquid is supplied by 4 circumferentially uniformly distributed small holes (44), and top ends and bottom ends of the joints are sealed by fluorine rubber sealing bodies and adhesives. Connecting surfaces of the magnetic and electric conductors (7) and the external terminals (16) are conical surfaces, the joints are filled with the NaK liquid, the NaK liquid is supplied by 4 circumferentially uniformly distributed small holes (38), and top ends and bottom ends of the joints are sealed by the fluorine rubber sealing bodies and adhesives. Mechanical connection between the two external terminals (16) and the two magnetic conductors (10) is fastened by bolts arranged in staggered directions, that is, the two external terminals and the magnetic conductor on the left side are fastened by singular bolts, and the two external terminals and the magnetic conductor on the right side are fastened by even-number bolts. Elastic taper washers (39) made of rubber are designed for transferring axial force of the bolts used for fastening the magnetic conductors (10), and axially pressing the magnet exciting coils (9), the stator electric conductors (6a, 6b) and the stator magnetic and electric conductors (7) in sequence.

(89) 16 groups of coaxial grooves and through holes which are circumferentially and uniformly distributed are formed in the two external terminals (16), spindles (40) of coaxial external conductors are bound with surfaces of the grooves, and binding surface clearances are filled with gallium-indium-tin alloy liquid (a ratio of gallium to indium to tin is 62:25:13) and sealed by fluorine rubber sealing rings (42). Pipe walls (41) of the coaxial external conductors are bound with surfaces of the through holes, and binding surface clearances are filled with the gallium-indium-tin alloy liquid (the ratio of gallium to indium to tin is 62:25:13) and sealed by fluorine rubber sealing rings (43). A vacuum suction method is adopted while filling the gallium-indium-tin alloy liquid. The spindles (40) and the pipe walls (41) are made of pure aluminum. Clearances are reserved between the spindles (40) and the pipe walls (41), and the heat is taken away by transformer oil flowing in the clearances.

(90) The magnet exciting coils (9) adopt a continuously wound whole-circle structure in which a plug joint or a split surface does not exist.

(91) A surface layer of being resistant to erosive wear and conductive is processed on a rotor wall surface of the “connecting region clearances” (5). The surface layer is an electroplated silver-antimony alloy.

(92) In the external auxiliary system, a circulating NaK liquid outer flow path is formed corresponding to each of the “connecting region clearances” (5). Liquid inlet ends of the flow paths are communicated with a manifold pipe of 16 round pipes (28), and liquid outlet ends of the flow paths are communicated with a manifold pipe of 16 round pipes (30). In each of the outer flow path, starting from one side of the liquid inlet end of the flow path, a volume regulating valve, a solid impurity filter, a circulating pump, a bubble gathering discharger and a radiator are arranged in sequence.

(93) The volume regulating valve is of a diaphragm structure, the diaphragm is made of fluorine rubber, an axial movement of the diaphragm is driven by a stepping motor with linear displacement output, and an adjustable volume chamber encircled and sealed by the diaphragm and the valve body is communicated with the outer flow path.

(94) The solid impurity filter takes a nickel powder metallurgy porous material as a filter element, so that total NaK liquid in the outer flow path flows through the filter element, and solid impurities are intercepted on the front part of the filter element.

(95) The circulating pump adopts a centrifugal pump and is driven by a motor with an adjustable rotation speed, and a rotation shaft of a centrifugal impeller is sealed by a fluorine rubber filler.

(96) The bubble gathering discharger takes the nickel powder metallurgy porous material as a gas-liquid separation element. The total NaK liquid flows through a channel encircled by inner side surfaces of the element at a low speed. A chamber communicated with an air chamber around the “connecting region clearances” (5) is formed in an outer side surface of the element. Bubbles in the NaK liquid are driven to pass through pores of the separation element by virtue of an inside and outside differential pressure, so as to filter the bubbles and return to an original air chamber. However, the NaK liquid is limited due to extremely high surface tension and cannot pass through the pores of the separation element.

(97) The radiator is of a shell-and-tube structure, the NaK liquid flows in heat exchange tubes, the transformer oil flows in a tube shell, and outer walls of the heat exchange tubes are provided with fins.

(98) The HET includes a set of transformer oil circulating system which includes a transformer oil circulating pump, a transformer oil air-cooled heat exchanger and a solid impurity filter. The circulating pump adopts a centrifugal pump or an axial flow pump. The transformer oil is driven to flow through shell sides of 4 NaK liquid radiators and intermediate clearances of the coaxial external conductors in parallel and flow through an inside-tube flow channel of a finned-tube air-cooled heat exchanger and the solid impurity filter in a centralized manner. Cooling air is driven by an external fan. The circulating pump is positioned in front of the air-cooled heat exchanger and behind the filter. The transformer oil is sequentially subjected to continuous repeated circulating processes such as heat-absorbing temperature rise and depressurization on the radiators and the coaxial conductors, depressurization on the filter, pressurization and temperature rise on the circulating pump and heat release cooling and depressurization on an air cooler.

(99) Magnetic fluid dynamic sealing elements (37) are arranged on inner sides of bearings at both ends of the rotation shaft. In addition to static seal mentioned above, static seals in the following positions are arranged on the stators: between the element 37 and the element 36, between the element 36 and the element 10, between the element 10 and the element 16, between two of the elements 16 (insulated and sealed), between the round pipes (28, 30) and the element 10 (adopting a sealing ring 45), between the ventilating pipe (34) and the element 10 and between the connecting pipe of the vent hole (35) and the element 10. A closed gas chamber composed of the above seals and other related objects thereof is filled with nitrogen.

(100) The nitrogen and metal liquid should be filled when the complete set of HET system is assembled. The operating method includes the following steps: vacuumizing a closed space occupied by the nitrogen and NaK liquid, wherein the space is a mutually communicated space (the sealing hose (33) is not in expansive seal, and interior of the hose is vacuumized), and the space includes NaK liquid joints in stator bodies, NaK liquid outer flow paths and the chamber in the outer side surface of the gas-liquid separation element of the bubble filter; pressurizing the sealing hose (33) with the nitrogen, and enabling an outer wall of the hose to be in sealed contact with the wall surface of the rotor; continuously retaining vacuumizing operations of the two vent holes (35), starting to inject liquid into a NaK liquid outer pipeline according to a serial line sequence, filling the NaK liquid into a vacuum chamber communicated with the “connecting region clearances” (5), and enabling the NaK liquid to be full of the space sealed by the hose (33) by virtue of a vacuum suction effect; and decompressing the hose (33) to remove the seal, filling the gas chamber with the nitrogen via the vent holes (35), and controlling an inside-tube nitrogen pressure of the hose (33) to be consistent with a pressure in the gas chamber.

(101) The two magnet exciting coils of each of the half-coupled members are connected in series in a manner of opposite rotation directions, are considered as a dual coil and are conducted with the same exciting current. The exciting current corresponding to the rotor 1 and the rotor 2 is recorded as I1 and I2 respectively. Since a magnetic field of two separated half-coupled members has independence, total magnetic flux ΣΦ1 and ΣΦ2 may be expressed as follows:
ΣΦ1=Ff1(|I0|,I1)  (a21)
ΣΦ2=Ff2(|I0|,I2)  (a22)

(102) Further, since the two half-coupled members have the same structure size and consistent regularity, functional forms Ff1( ) and Ff2( ) are the same and may be recorded as a functional form Ff( ) that is,
ΣΦ1=Ff(|I0|,I1)  (a23)
ΣΦ2=Ff(|I0|,I2)  (a24)

(103) Meanwhile, a calculated amount of corresponding regularity content may be reduced by half, and only calculation should be performed on one of the half-coupled members.

(104) During operating control of an output torque, any one of 5 adjustment and control methods should be selectively used as follows:

(105) A first type of first adjustment and control methods:

(106) A main current upper limit value I0max in an adjustment range is selected as a designed value, and a lower limit value I0min is zero.

(107) Two numerical values are obtained by calculation or test as follows:
ΣΦmaxd=Ff(|I0max|,Iid)  (a25)
ΣΦmind=Ff(|I0min|,Iid)  (a26)

(108) wherein Iid is respectively a designed value of the I1 and I2.

(109) Two relation curves changing along with exciting current Is are obtained by calculation or test as follows:
ΣΦmax=Ff(|I0max|,Is)  (a27)
ΣΦmin=Ff(|I0min|,Is)  (a28)

(110) wherein a range of the value Is ranges from zero to the designed value Iid.

(111) During operating adjustment, rotation speeds ω1 and ω2 of the two rotors are acquired in real time.

(112) When ω1 is more than or equal to ω2, I2 is taken as a constant value Iid, I1 is taken as adjustable exciting current Is, and electromagnetic law formula ((a1)-(a4), wherein R0 is a constant value) and the following formulas ((a29)-(a32)) are utilized:
ΣΦ1max=ΣΦmax=Ff(|I0max|,Is)  (a29)
ΣΦ1min=ΣΦmin=Ff(|I0min|,Is)  (a30)
ΣΦ2max=ΣΦmaxd=Ff(|I0max|,Iid)  (a31)
ΣΦ2min=ΣΦmind=Ff(|I0min|,Iid)  (a32)

(113) Or, when ω1 is less than ω2, I1 is taken as a constant value Iid, I2 is taken as adjustable exciting current Is, and electromagnetic law formula ((a1)-(a4), wherein R0 is a constant value) and the following formulas ((a33)-(a36)) are utilized:
ΣΦ2max=ΣΦmax=Ff(|I0max|,Is)  (a33)
ΣΦ2min=ΣΦmin=Ff(|I0min|,Is)  (a34)
ΣΦ1max=ΣΦmaxd=Ff(|I0max|,Iid)  (a35)
ΣΦ1min=ΣΦmind=Ff(|I0min|,Iid)  (a36)

(114) At the current rotation speed, an upper limit value Ismax and a lower limit value Ismin corresponding to the upper limit value and the lower limit value of the main current are calculated at any time, namely,
Ismax=F(I0max,ω1,ω2)  (a16)
Ismin=F(I0min,ω1,ω2)  (a17)

(115) The upper limit value (Ismax, I0max) and the lower limit value (Ismin, I0min) of the current obtained above simultaneously correspond to the upper limit value (Me1max, Me2max) and the lower limit value (Me1min, Me2min) of the electromagnetic torque at the current rotation speed, and such a corresponding relation is in monotonic change. The lower limit value of the electromagnetic torque is zero, and an upper limit value of the electromagnetic torque at a lower rotation speed is a design rated value.

(116) When regulation is executed, an operation range of the actuator may linearly correspond to the adjustable exciting current Is in a range located between the upper limit value Ismax and the lower limit value Ismin; both ends of the operation range correspond to the upper limit value and the lower limit value of the electromagnetic torque, but an intermediate value of the electromagnetic torque and the operation range are generally not in a linear relationship. A certain nonlinear correspondence rule may also be adopted between the operation range and the adjustable exciting current Is, so that the electromagnetic torque and the operation range tend to be in approximate linear correspondence. The nonlinear correspondence rule should be obtained by analysis summary of the calculated or tested data.

(117) A first type of the second adjustment and control methods:

(118) A relation curve that varies along with main current I0 is obtained by calculation or test as follows:
ΣΦd=Ff(|I0|,Iid)  (a37)

(119) A relationship curve changing along with main current I0 and exciting current Is is obtained by calculation or test as follows:
ΣΦ=Ff(|I0|,Is)  (a38)

(120) wherein the value of I0 ranges from zero to a designed value, and the value of Is ranges from zero to a designed value Iid.

(121) A selected torque command is specific to Me1 or Me2.

(122) When regulation is executed, rotation speeds ω1 and ω2 of the two rotors are acquired in real time.

(123) When ω1 is more than or equal to ω2, I2 is taken as a constant value Iid, I1 is taken as adjustable exciting current Is, and electromagnetic law formula ((a1)-(a4), (a5) or (a6), wherein R0 is a constant value) and the following formulas ((a39)-(a40)) are utilized:
ΣΦ1=ΣΦ=Ff(|I0|,Is)  (a39)
ΣΦ2=ΣΦd=Ff(|I0|,Iid)  (a40)

(124) Or, when ω1 is less than ω2, I1 is taken as a constant value Iid, I2 is taken as adjustable exciting current Is, and electromagnetic law formula ((a1)-(a4), (a5) or (a6), wherein R0 is a constant value) and the following formulas ((a41)-(a42)) are utilized:
ΣΦ2=ΣΦ=Ff(|I0|,Is)  (a41)
ΣΦ1=ΣΦd=Ff(|I0|,Iid)  (a42)

(125) A current rotation speed value and a given torque command (Me1 value or Me2 value, an application range of the value Me1 or Me2 meeting a limiting condition of each factor is calculated and determined in advance) are taken as input conditions, and then the needed adjustable exciting current Is is calculated at any time for use in the execution link.

(126) The value Is is a solving result of seven simultaneous equations ((a1)-(a4), (a5) or (a6), (a39) or (a41), (a40) or (a42)), and a functional form is as follows:
Is=F(Me1 or Me2,ω1,ω2)  (a20)

(127) A first type of the third adjustment and control methods:

(128) A relation curve that varies along with main current I0 is obtained by calculation or test as follows:
ΣΦd=Ff(|I0|,Iid)  (a37)

(129) A relationship curve that varies along with main current I0 and exciting current Is is obtained by calculation or test as follows:
ΣΦ=Ff(|I0|,Is)  (a38)

(130) wherein the value of I0 ranges from zero to a designed value, and the value of Is ranges from zero to a designed value Iid.

(131) A selected torque command is for Me1 or Me2, and an application range of the torque command is given. An application range of rotation speeds of two shafts is given. By utilizing electromagnetic law formula ((a1)-(a4), (a5) or (a6), wherein R0 is a constant value), formulas (a39) and (a40) are simultaneously utilized when ω1 is more than or equal to ω2, or formulas (a41) and (a42) are simultaneously utilized when ω1 is less than ω2, to calculate a matrix of the adjustable exciting current value Is that fully covers different rotation speed conditions and torque demands (the functional form is the same as that of a formula (a20)), and the total data are stored in the control system. When ω1 is more than or equal to ω2, the I2 is a constant value Iid and I1 is the adjustable exciting current Is; or when ω1 is less than ω2, the I1 is the constant value Iid, and the I2 is the adjustable exciting current Is.

(132) When regulation is executed, rotation speeds ω1 and ω2 of the two rotors are acquired in real time. A current rotation speed value and a given torque command (Me1 value or Me2 value) are taken as input conditions, related stored data is invoked from the control system, the corresponding adjustable exciting current value Is is calculated by adopting a spline interpolation function formula, and an adjustment coil is determined for use in the execution link.

(133) A second type of the first adjustment and control methods: The total loss is a sum of main current ohmic heat (I0.Math.I0.Math.R0) and exciting current ohmic heat (ΣPoi), wherein R0 and Ri are constant values.

(134) A relationship curve changing along with main current I0 and exciting current Ii is obtained by calculation or test as follows:
ΣΦ=Ff(|I0|,Ii)  (a43)

(135) wherein the value of I0 ranges from zero to a designed value, and the value of Ii ranges from zero to a designed value Iid.

(136) The Ii in the formula (a43) is replaced with I1 and I2, so as to obtain two formulas as follows:
ΣΦ1=Ff(|I0|,I1)  (a44)
ΣΦ2=Ff(|I0|,I2)  (a45)

(137) A selected torque command is for Me1 or Me2, and an application range of the torque command is given. An application range of rotation speeds of two shafts is given. By utilizing electromagnetic law formula ((a1)-(a4), (a5) or (a6), wherein R0 is a constant value) and the formulas (a44) and (a45), matrixes of optimal values I1 opt and I2opt of the exciting current that fully cover different rotation speed conditions and torque demands and satisfy a total loss minimum target are calculated, and the total data are stored in the control system.

(138) When regulation is executed, rotation speeds ω1 and ω2 of the two rotors are acquired in real time as input conditions. A given torque command (Me1 value or Me2 value) is also taken as an input condition, related stored data is invoked from the control system, the corresponding optimal values I1opt and I2opt of each exciting current are calculated by adopting a spline interpolation function formula for use in the execution link.

(139) A second type of the second adjustment and control methods:

(140) The total loss is a sum of main current ohmic heat (I0.Math.I0.Math.R0), exciting current ohmic heat (ΣPoi) and “connecting region clearance” liquid metal friction heat, wherein Ri is a constant value, R0 is a function of NaK liquid state parameters MLS, a variable in the parameters MLS is a NaK liquid capacity parameter, while a liquid center position parameter is fixed as a mean. The parameters MLS may influence the liquid metal friction heat.

(141) A relationship curve that varies along with main current I0 and exciting current Ii is obtained by calculation or test as follows:
ΣΦ=Ff(|I0|,Ii)  (a43)

(142) wherein the value of I0 ranges from zero to a designed value, and the value of Ii ranges from zero to a designed value Iid.

(143) The Ii in the formula (a43) is replaced with I1 and I2, so as to obtain two formulas as follows:
ΣΦ1=Ff(|I0|,I1)  (a44)
ΣΦ2=Ff(|I0|,I2)  (a45)

(144) A selected torque command is for Me1 or Me2, and an application range of the torque command is given. An application range of rotation speeds of two shafts is given. An application range of the NaK liquid capacity parameter of the “connecting region clearance” is given. By utilizing electromagnetic law formula ((a1)-(a4), (a5) or (a6), wherein R0 is a function of the NaK liquid capacity parameter) and the formulas (a44) and (a45), matrixes of optimal values I1opt and I2opt of the exciting current that fully cover different rotation speed conditions and torque demands and satisfy a total loss minimum target, as well as a matrix of optimal values of the NaK liquid capacity parameter are calculated, and the total data are stored in the control system.

(145) When regulation is executed, rotation speeds ω1 and ω2 of the two rotors are acquired in real time as input conditions. A given torque command (Me1 value or Me2 value) is also taken as an input condition, related stored data is invoked from the control system, the corresponding optimal values I1opt and I2opt of each exciting current as well as the optimal value of the NaK liquid capacity parameter are calculated by adopting a spline interpolation function formula for use in the execution link.

(146) Magnitude of direct current of the magnet exciting coils is controlled by a DC chopper.

(147) (b) Fuel Engine Power System for Vehicles Including HET

(148) A vehicle power system solution is mainly composed of an engine, a transmission system, a control system and the like. A front engine is in rear wheel drive; and the engine is a gasoline engine and has a maximum power of 240 kW and a rotation speed of 6000 r/min at the maximum power. A single gear speed increaser with a speed ratio of 1.667 is arranged between an output shaft of the engine and an input shaft of the HET. A maximum rotation speed of each of the two rotors of the HET is 10000 r/min. An output shaft of the HET is connected with a gear reducer with a two-gear speed ratio, and the gear reducer is connected with a main reducing gear of a rear drive axle by virtue of a universal transmission shaft.

(149) The used HET solution is the same as a solution adopted in the specific embodiment of “(a) Homopolar DC Electromagnetic Transmission (HET)”.

(150) Performance data of the gasoline engine is obtained by test in advance, and figure lines are formed as follows: on a torque-rotation speed diagram that takes the rotation speed as a horizontal axis and takes an output torque as a vertical axis, various equal throttle opening lines, equal output power lines and equal fuel efficiency lines (or a contour line of a ratio of a fuel consumption rate to the power) are drawn. A route starting from an idling condition and terminating at a maximal power condition is selected on the torque-rotation speed diagram. A selection method is as follows: passing through optimum efficiency points or better efficiency point on the equal power lines as much as possible along a progressive increase direction of the equal power lines, and giving consideration to move forwards along a progressive increase direction of the equal throttle opening lines. The above route is changed into a curve on a throttle opening-rotation speed diagram.

(151) The gasoline engine is equipped with a speed controller, and the speed is regulated according to the above circuit between the idling condition and the maximal power condition, thereby ensuring the gasoline engine to operate on the route and a control buffer zone nearby the route. During regulation, a rotation speed value and a throttle opening value are collected, and the curve on the throttle opening-rotation speed diagram is compared. When state points of the detected rotation speed and throttle opening are located on the right side of the curve (a higher rotation speed side), the throttle opening is decreased; otherwise, the throttle opening is increased.

(152) A driver location is set as follows: driving a torque pedal and a brake pedal, aheading at gear 1, aheading at gear 2, reversing at gear 1, and initializing an operating lever. Initial setting is performed before vehicle start only, and fails while running. Initial setting of aheading at gear 1 is as follows: a step speed change reducer is located in a gear-1 large transmission ratio state at an aheading speed of the vehicle ranging from zero to an intermediate switching speed, and located in a gear-2 small transmission ratio state in a range from the intermediate switching speed to a maximum speed. Initial setting of aheading at gear 2 is as follows: the step speed change reducer is always located in the gear-2 small transmission ratio state. Initial setting of reversing at gear 1 is as follows: the step speed change reducer is located in the gear-1 large transmission ratio state at a vehicle reversing running speed ranging from zero to an intermediate speed, and a speed limit does not exceed the intermediate speed. During reversing, the HET output shaft and a rear axle system thereof are reversed, and a special reverse gear block does not exist.

(153) Control of aheading and reversing drive torques of the vehicle is dominated and executed by an HET adjustment and control system. The driver gives a relative value command of the drive torques from zero to a maximum value by using a drive torque pedal, the HET adjustment and control system commands the HET to output a needed aheading forward drive torque or reversing backward drive torque, while the speed controller of the gasoline engine controls the gasoline engine to run in a follow-up manner on an adjustable route, and only the needed power should be supplied.

(154) A vehicle starting program is as follows: before starting, current of each of the magnet exciting coils of the HET is in a zero value state, liquid metals in the “connecting region clearances” are in a retracted open-circuit state, and the engine is in a stationary or idling condition; the stationary engine is started to the idling condition, initial setting of the aheading at gear 1 or the aheading at gear 2 or the reversing at gear 1 is executed by the operating lever, the torque command is given by the drive torque pedal, the liquid metals in the “connecting region clearances” are controlled to return by the HET adjustment and control system, and the drive torque is output, thereby starting the vehicle to run.

(155) A gear-shifting operation while running is automatically controlled by the HET adjustment and control system. When a preset gear shifting speed is reached, the output torque of the HET is controlled to be decreased to zero (that is, the exciting current is decreased to zero), an original gear is released, two synchronous to-be-engaged parts are rubbed by a synchronizer, a new gear is engaged, and the HET is enabled to output the needed torque according to the current driving torque command.

(156) A vehicle sliding program includes: returning the drive torque command to zero, returning the current of each of the magnet exciting coils of the HET to zero, enabling the liquid metals in the “connecting region clearances” to be in a retracted open-circuit, and returning the engine to the idling condition in a follow-up manner or until the vehicle shuts down.

(157) A vehicle parking program includes: returning the drive torque command to zero, returning the current of each of the magnet exciting coils of the HET to zero, enabling the liquid metals in the “connecting region clearances” to be in a retracted open-circuit, returning the engine to the idling condition in a follow-up manner or until the vehicle shuts down, transmitting a braking instruction followed by the torque command when braking is needed, until the vehicle is stopped.

(158) A kinetic energy recovery start button is set. The button may be pressed down under a condition that the vehicle slides or the engine shuts down or is not ignited (e.g., slope sliding). A special procedure is started. The accumulator or the motor is not started, and only kinetic energy of the vehicle is utilized. The engine is ignited and started to the idling condition by virtue of reversed power transmission of the HET.

(159) (c) Flywheel Power System for Vehicles Including HET

(160) A four-wheel-drive vehicle power system is mainly composed of two vertical axis type flexible flywheel devices, a transmission system from the flywheel devices to a drive axle main reducing gear, a control system thereof, and the like. The transmission system includes two sets of separated HETs independent of each other.

(161) The two vertical axis type flexible flywheel devices (71) are arranged on a vehicle chassis, arranged adjacent to each other along a longitudinal axis center line of the vehicle, and centered in a length direction of the vehicle. Each flywheel is connected with a frame (73) through four ear flanges (74) and a supporting assembly (75). The two flywheels have the same specification and dimension, while only rotation directions are opposite to each other.

(162) A specific embodiment (FIG. 23) of each of the vertical axis type flexible flywheel devices is as follows:

(163) Main parameters include: a rated rotation speed of 10000 r/min, an outer diameter of 1354.4 mm, a vacuum container height of 440.2 mm, a total height of 535.3 mm, a flywheel mass on the rotation shaft of 748.8 kg, and rated stored energy of 30.6 kWh.

(164) Two mass block bodies (53) are arranged and are made of high-strength glass fiber roving reinforced epoxy resin subjected to filament winding. In order to adapt to a big rounded angle of a shell (52), round chamfer is designed at a junction of two end surfaces of the mass block body on an outer ring and an excircle, based on an enough safety clearance existing between a deformable contour of the mass block body generated at a maximal rotation speed and the shell.

(165) A supporting body (54) is arranged and is made of an aluminum alloy.

(166) A bearing end surface pair (56) and an upward displacement-limiting end surface pair (57) are adopted between the mass block body on the outer ring and the mass block body on an inner ring; two end surface pairs are designed in a centralized manner; and axial positions of the two end surface pairs are flush with center of gravity of the mass block body on the outer ring. The bearing end surface pair (56) and the upward displacement-limiting end surface pair (57) are adopted between the mass block body on the inner ring and the supporting body; two end surface pairs are designed in a centralized manner; and axial positions of the two end surface pairs are flush with center of gravity of the two mass block bodies as much as possible. Two opposite end surfaces of the end surface pairs (56, 57) remain a margin on a radial height so as to compensate radial displacement dislocation generated during rotation, so that the end surface pairs always keep an effective action area in a range from a static state to the maximal rotation speed. A clearance does not exist between the two opposite end surfaces of the end surface pair (57), and the end surface pair (57) is combined with the bearing end surface pair (56) to achieve an axial positioning effect, thereby limiting angle misalignment changes in a forced manner and closely participating in transfer of force and torque. In order to achieve the purposes of increasing wear resistance of a contact surface of the end surface pairs, increasing an effective contact area, protecting a fiber reinforced plastic surface, realizing reliability, durability, vibration absorption and the like, the two opposite end surfaces of the end surface pairs (56, 57) are made of polyurethane rubber. An end-surface thin plate (65) and an end-surface thick block (66) made of the polyurethane rubber material are adhered with a matrix together. The end-surface thick block (66) has high elasticity and deformation adaptability, but high centrifugal load, and is installed on an outer ring matrix. The centrifugal load is borne by an inner hole surface of the matrix. Since a load of the bearing end surface pair (56) is higher, the selected matrix adhered and a main body of a wheel body structure are made into an integral structure, thereby ensuring that a load transfer path has full strength reserve. However, a matrix at one end of the non-bearing end surface pair (57) adopts an accessory structure, and the accessory is fixedly connected with a main matrix by virtue of an adhesive and is made of a material identical to that of the main matrix.

(167) Two flexible membrane rings (55) with large axial span are respectively arranged between the mass block body on the outer ring and the mass block body on the inner ring and between the mass block body on the inner ring and the supporting body. Each of the flexible membrane rings is directly adhered to an inner ring or outer ring main matrix connected with the flexible membrane ring. The flexible membrane ring is made of the polyurethane rubber, does not have pre-bending deformation in an installation state and is composed of roots at both ends and a middle body. The roots with semicircular heads are adhered with the main matrix, and a thickness of the body is in a gradually decreased design along a radial direction, thereby decreasing maximum stress. Since a larger axial distance exists between the flexible membrane rings between the two mass blocks and a positioning end surface pair, the two flexible membrane rings adopt an inclined design, thereby enabling the film rings to be located in a radial straightening state at the maximal rotation speed.

(168) A steel support disc (62) and a polyurethane rubber elastic material ring (63) are arranged between a steel rotation shaft (51) and the supporting body (54). A central inner hole of the support disc and the rotation shaft are in conical interference fitting. A disc body of the support disc is positioned below the supporting body. An elastic material ring is installed between the support disc and the supporting body, and the elastic material ring is adhered with the support disc and the supporting body. The elastic material ring achieves flexible connecting, bearing and axial positioning effects.

(169) A vacuum container shell (52) is designed into a two-half structure split by a vertical axis. A circle of flanges (67) is positioned at a middle part on a surface of an excircle of the shell. Flange edges are positioned on an inner side of the container. Fastening bolts are not arranged on flange edges on an inner side, and the flange edges are pressed by virtue of a pressure produced by vacuum of the container. Four sections of ear flanges (74) and fastening bolts thereof are arranged at 45-degree four corners, which do not influence the arrangement width and length, on the outer side of the container. A rubber sealing ring is arranged on the edges of the whole circle of flanges, vacuum sealing grease is arranged on an outer side of the rubber sealing ring, and a soft metal sealing ring is arranged on an inner side of the rubber sealing ring. Installation and support of the shell (and the whole flywheel device) may be realized by connecting the exposed ear flanges (74) and the supporting assembly (75) with a frame (73).

(170) The shell (52) is of a three-layer composite structure (FIG. 25). An intermediate layer is a glass chopped fiber reinforced epoxy resin, the two outer surfaces are made of aluminum alloys, and the intermediate layer is adhered with the outer surface layers. A magnetic fluid sealing assembly is arranged between the shell (52) and the rotation shaft (51).

(171) Radial supporting bearings of the rotation shaft (51) are two groups of rolling bearings. The rolling bearing positioned at the lower end bears a radial load and is a single-row deep groove ball bearing; and the rolling bearings positioned at the upper end bear the radial load and bidirectional axial load, serve as an axial positioning end and are a pair of angular contact ball bearings. A spherical rolling bearing for radial protection is arranged on the rolling bearing side at the lower end; and a CARB ring rolling bearing for radial protection is arranged on the rolling bearing side at the upper end.

(172) An axial supporting bearing of the rotation shaft (51) is a permanent magnet attraction type axial supporting magnetic bearing. An axial positioning bearing close to the upper end has a stepped rotary disc (59) and a stepped stationary disc (60). The stationary disc is directly fixedly connected with a bearing block. The rotary disc is positioned below the stationary disc. An air gap is formed between end surfaces on adjacent sides of the two discs. The rotary disc is of a 45-steel axisymmetric structure. The stationary disc is of an axisymmetric structure of an aluminium alloy, electromagnetic pure iron and Nd—Fe—B permanent magnet. The aluminium alloy structure is a matrix of the stationary disc; a mixed disc structure formed by arranging electromagnetic pure iron rings and Nd—Fe—B permanent magnet rings at intervals forms a side end surface opposite to the rotary disc; the permanent magnet rings are magnetized outwards or inwards along a radial direction; adjacent permanent magnet rings have opposite magnetizing directions; and upward magnetic attraction force in an air-gap field acts on the rotary disc and is designed for offsetting gravity of the rotors. The magnetic bearings do not have magnetic hysteresis or eddy losses.

(173) A loading disc (69) is arranged at the lower end of the flywheel rotation shaft and is used for connecting a load joint of an external loading system and the rotation shaft and performing high-power rapid load charging by transmitting mechanical torques to the flywheel rotation shaft. Rated design load power is 2000 kW.

(174) Each flywheel is correspondingly equipped with a set of HET. Each flywheel and a rotor of an HET corresponding to the flywheel (an HET input end rotor) share the same rotation shaft. The two sets of separated HET have the same specification and dimension.

(175) A specific embodiment of each set of the separated HET is as follows.

(176) Each set of the separated HET has two half-coupled members with the same electromagnetic structure and size. The two half-coupled members only have differences in bearings at both ends and supporting structures. A flywheel shaft-end half-coupled member (part A in FIG. 23) and the flywheel are vertically installed in a coaxial manner, and a non-flywheel shaft end half-coupled member (72) is horizontally installed on the frame and has a meridian plane diagram shown in FIG. 19. Each of the half-coupled members is of double-magnetic flux, single-stage, single-circuit, near-axis coil, solid shaft and axial surface type.

(177) Sizes of the half-coupled member are as follows: an axial surface radius of the rotation shaft is 53 mm, a radius of the stator body is 138.65 mm, a radius of an external terminal is 213.5 mm, and an axial length of the stator of the non-flywheel shaft end half-coupled member is 280 mm. A designed value of the rotation speed of the rotation shaft of each of the half-coupled members is 10000 r/min, and an electromagnetic power designed value is 240 kW. A main current designed value is 40794 A. In a design point condition, a sum of total exciting current ohmic heat power of the HET, circuit “connecting region clearance” NaK liquid friction power and main current ohmic heat power is about 4% of the electromagnetic power designed value 240 kW.

(178) Supporting end covers (36) at both ends of the non-flywheel shaft end half-coupled member and a supporting end cover (36) at the upper end of the flywheel shaft end half-coupled member serve as bearing blocks, and magnetic fluid sealing elements (37) are arranged on inner rings of the bearing blocks. A supporting end cover (36) at the lower end of the flywheel shaft end half-coupled member and an upper side wall of the vacuum container shell (52) of the flywheel are in matched connection with each other and can mutually slide to each other, and a rubber sealing ring is arranged on a sliding cylindrical surface. A dynamic seal at the lower end of the flywheel shaft end half-coupled member and a dynamic seal of the vacuum container shell (52) are merged into one magnetic fluid sealing element (37), that is, the former depends on the latter, and sealing performance of the latter is preferred.

(179) A center shaft of a rotor of the flywheel shaft end half-coupled member and a steel flywheel rotation shaft (51) share the same axis. The steel flywheel rotation shaft is made of 45 steel or steel 40Cr, an outer ring loop axis is made of 20 steel, and the magnetic fluid sealing element (37) and the center shaft are paired.

(180) Detailed description of other structures of the solutions of the HET half-coupled members and the second type of adjustment and control method of each set of the HET are the same as description in Chapter I in embodiments of “(a) Homopolar DC Electromagnetic Transmission (HET)”.

(181) In order to form an external conductor between two HET half-coupled members in a set of main current closed circuit, a coaxial conductor in which a spindle (40) is matched with a sleeve (41), and the spindle and the sleeve have opposite current directions.

(182) Two HET half-coupled members (that is, non-flywheel shaft end half-coupled members) (72) which do not share the rotation shaft with the flywheel are horizontally arranged on the frame. A half-coupled member rotation shaft corresponding to a front flywheel is connected with a front drive axle main reducing gear by virtue of a two-stage speed ratio reducer, while a half-coupled member rotation shaft corresponding to a rear flywheel is connected with a rear drive axle main reducing gear by virtue of a two-stage speed ratio reducer. The two two-stage speed ratio reducers have the same design. The front drive axle and the rear drive axle have the same reduction ratio, are both disconnected and adopt independent suspensions.

(183) Wires connected with an external DC power supply are connected in parallel on the external conductors on each flywheel shaft end HET half-coupled member, and are used for realizing (respectively) plug-in charging or unloading on each of the flywheels. The external power supply used for performing plug-in charging or unloading on the flywheels adopts an adjustable voltage DC power unit which is arranged in the vehicle and connected with power grid alternating current, and the maximal design power is 7 kW. During plug-in charging, the circuit “connecting region clearances” (5) of the non-flywheel shaft-end HET half-coupled member are disconnected, the circuit “connecting region clearances” (5) of the flywheel shaft end half-coupled members are connected, related magnet exciting coils enabling magnetic flux of the HET flywheel end rotor to reach a maximum value are connected, and the maximum exciting current is always maintained. A voltage size of the DC power supply is adjusted to be equal to electromotive force of the HET flywheel end rotor, and the voltage direction is opposite to the electromotive force direction. A main current circuit is connected with the DC power supply. The voltage of the DC power supply is increased to reach a rated limit value of plug-in main current or a rated limit value of plug-in power. The voltage of the DC power supply is continuously increased in a flywheel charging and speeding-up process, and the rated limit value of the plug-in main current and/or the plug-in power is maintained. Current limitation and power limitation are performed in sequence. When a starting point of the flywheel rotation speed is high, only power limitation is performed. When charging is ended, the voltage of the DC power supply is decreased to obtain zero current, the main current circuit is disconnected from the DC power supply, and HET magnet excitation is canceled. During plug-in unloading, a set-up procedure is the same as above, current directions are opposite, and operating procedures are opposite, that is, the voltage of the DC power supply is decreased to reach a rated limit value of plug-in unloading power or a rated limit value of plug-in unloading main current.

(184) Power control units are arranged on a vehicle driving seat as follows: a drive pedal, a brake pedal, aheading gear 1, aheading gear 2 and reversing gear 1 initial setting operating levers and a two-flywheel torque setting button.

(185) Instructions for driving torque relative values ranging from zero to a maximal value are correspondingly output in a drive pedal travel. The torque and the travel adopt a non-linear relation. The torque at an initial stage is increased slowly, so as to easily control a low running speed of the vehicle.

(186) Travel of the brake pedal is divided into a front travel and a rear travel. The front travel corresponds to kinetic energy recovery braking torque relative values ranging from zero to a maximal value. The rear travel corresponds to friction braking torque relative values ranging from zero to a maximal value. The maximal value of the kinetic energy recovery braking torque is simultaneously maintained in the rear travel. Kinetic energy recovery braking is to recover kinetic energy of the vehicle to the flywheels by virtue of reverse power flow transfer of the HET. Friction braking is to convert the kinetic energy of the vehicle into heat energy by adopting four vehicle friction braking discs.

(187) Initial setting operating levers of the aheading gear 1, aheading gear 2 and reversing gear 1 give consideration to aheading and reversing settings and initial speed ratio gear settings. Initial setting of aheading at gear 1 is as follows: a step speed change reducer is located in a gear-1 large transmission ratio state at an aheading speed of the vehicle ranging from zero to an intermediate switching speed, and located in a gear-2 small transmission ratio state in a range from the intermediate switching speed to a maximum speed. Initial setting of aheading at gear 2 is as follows: the step speed change reducer is always located in the gear-2 small transmission ratio state. Initial setting of reversing at gear 1 is as follows: the step speed change reducer is located in the gear-1 large transmission ratio state at a vehicle reversing running speed ranging from zero to an intermediate speed, and a speed limit does not exceed the intermediate speed. During reversing, the HET output shaft and a rear axle system thereof are reversed, and a special reverse gear block does not exist.

(188) The two-flywheel torque setting button is used for manually setting a rotation speed electromagnetic torque ratio of the two HET output end rotors by a driver before starting-up or during sliding. Meanwhile, the setting button has a function of automatically setting a torque ratio value in the control system, and automatic setting can be executed before starting-up or during sliding or while non-sliding running. The automatically set ratio value is calculated according to a logic rule in the control system. While running, manual setting and automatic setting are alternative, and the setting button has only one automatic gear.

(189) Control of adhead running and reversing driving torques of the vehicle is executed by the HET adjustment and control system. Adhead running or reversing intention is set before starting-up. The driver gives instructions for the relative values of the driving torques from zero to the maximal value by virtue of the drive pedal. According to the set electromagnetic torque ratio value of the two sets of HETs, the HET adjustment and control system commands the HET to output a needed adhead running forward driving torque or a reversing backward driving torque.

(190) Control of the kinetic energy recovery braking torque of the vehicle during adhead running or reversing is executed by the HET adjustment and control system. Adhead running or reversing intention is set before starting-up. The driver gives instructions for the relative values of the kinetic energy recovery braking torque from zero to the maximal value by virtue of the brake pedal. According to the set electromagnetic torque ratio value of the two sets of HETs, the HET adjustment and control system commands the HET to transmit the kinetic energy of the vehicle to the flywheels, thereby making a needed adhead running backward braking torque or a reversing forward braking torque.

(191) A vehicle starting program is as follows: before starting, current of each of the magnet exciting coils of the HET is in a zero value state, liquid metals in the “connecting region clearances” are in a retracted open-circuit state, initial setting of the aheading at gear 1 or the aheading at gear 2 or the reversing at gear 1 is executed by the operating lever, the ratio value of the electromagnetic torque of the two sets of the HETs is manually controlled or manually set, the torque command is given by the drive pedal, the liquid metals in the “connecting region clearances” are controlled to return by the HET adjustment and control system, and the drive torque is output, thereby starting the vehicle to run.

(192) A gear-shifting operation while running is automatically controlled by the HET adjustment and control system. When a preset gear shifting speed is reached, the output torque of the HET is controlled to be decreased to zero (that is, the exciting current is decreased to zero), an original gear is released, two synchronous to-be-engaged parts are rubbed by a synchronizer, a new gear is engaged, and the HET is enabled to output the needed torque according to the current driving torque command.

(193) (d) Fuel Engine and Flywheel Hybrid Power System for Vehicles Including HET

(194) A car hybrid power system includes: a gasoline engine (76), a vertical axis type flexible flywheel device (71), a transmission system connected with the engine, the flywheel device and a drive axle main reducing gear, and a control system thereof.

(195) The vertical axis type flexible flywheel device (71) is arranged on a vehicle chassis and connected with a frame (73) through four ear flanges (74) and a supporting assembly (75).

(196) A specific embodiment (FIG. 26) of the vertical axis type flexible flywheel device is as follows:

(197) Main parameters include: a rated maximal rotation speed of 13793.1 r/min, an outer diameter of 982 mm, a vacuum container height of 229 mm, a total height of 409.6 mm, a flywheel mass on the rotation shaft of 203.9 kg, and rated stored energy of 8.1 kWh.

(198) Two mass block bodies (53) are arranged and are made of high-strength glass fiber roving reinforced epoxy resin subjected to filament winding. In order to adapt to a big rounded angle of a shell (52), round chamfer is designed at a junction of two end surfaces of the mass block body on an outer ring and an excircle, based on an enough safety clearance existing between a deformable contour of the mass block body generated at a maximal rotation speed and the shell.

(199) A supporting body (54) is arranged and is made of an aluminum alloy.

(200) A bearing end surface pair (56) and an upward displacement-limiting end surface pair (57) are adopted between the mass block body on the outer ring and the mass block body on an inner ring; the two end surface pairs are designed in a centralized manner; and axial positions of the two end surface pairs are flush with center of gravity of the mass block body on the outer ring. The bearing end surface pair (56) and the upward displacement-limiting end surface pair (57) are adopted between the mass block body on the inner ring and the supporting body; the two end surface pairs are designed in a centralized manner; and axial positions of the two end surface pairs are flush with center of gravity of the two mass block bodies as much as possible. Two opposite end surfaces of the end surface pairs (56, 57) remain a margin on a radial height so as to compensate radial displacement dislocation generated during rotation, so that the end surface pairs always keep an effective action area in a range from a static state to the maximal rotation speed. A clearance does not exist between the two opposite end surfaces of the end surface pair (57), and the end surface pair (57) is combined with the bearing end surface pair (56) to achieve an axial positioning effect, thereby limiting angle misalignment changes in a forced manner and closely participating in transfer of force and torque. In order to achieve the purposes of increasing wear resistance of a contact surface of the end surface pairs, increasing an effective contact area, protecting a fiber reinforced plastic surface, realizing reliability, durability, vibration absorption and the like, the two opposite end surfaces of the end surface pairs (56, 57) are made of polyurethane rubber. An end-surface thin plate (65) and an end-surface thick block (66) made of the polyurethane rubber material are adhered with a matrix together. The end-surface thick block (66) has high elasticity and deformation adaptability, but high centrifugal load, and is installed on an outer ring matrix. The centrifugal load is borne by an inner hole surface of the matrix. Since a load of the bearing end surface pair (56) is higher, the selected matrix adhered and a main body of a wheel body structure are made into an integral structure, thereby ensuring that a load transfer path has full strength reserve. However, a matrix at one end of the non-bearing end surface pair (57) adopts an accessory structure, and the accessory is fixedly connected with a main matrix by virtue of an adhesive and is made of a material identical to that of the main matrix.

(201) Two flexible membrane rings (55) with large axial span are respectively arranged between the mass block body on the outer ring and the mass block body on the inner ring and between the mass block body on the inner ring and the supporting body. Each of the flexible membrane rings is directly adhered to an inner ring or outer ring main matrix connected with the flexible membrane ring. The flexible membrane ring is made of the polyurethane rubber, does not have pre-bending deformation in an installation state and is composed of roots at both ends and a middle body. The roots with semicircular heads are adhered with the main matrix, and a thickness of the body is in a gradually decreased design along a radial direction, thereby decreasing maximum stress. Since a larger axial distance exists between the flexible membrane rings between the two mass blocks and a positioning end surface pair, the two flexible membrane rings adopt an inclined design, thereby enabling the film rings to be located in a radial straightening state at the maximal rotation speed.

(202) A steel support disc (62) and a polyurethane rubber elastic material ring (63) are arranged between a steel rotation shaft (51) and the supporting body (54). A central inner hole of the support disc and the rotation shaft are in conical interference fitting. A disc body of the support disc is positioned below the supporting body. An elastic material ring is installed between the support disc and the supporting body, and the elastic material ring is adhered with the support disc and the supporting body. The elastic material ring achieves flexible connecting, bearing and axial positioning effects.

(203) A vacuum container shell (52) is designed into a two-half structure split by a vertical axis. A circle of flanges (67) is positioned at a middle part on a surface of an excircle of the shell. Flange edges are positioned on an inner side of the container. Fastening bolts are not arranged on flange edges on an inner side, and the flange edges are pressed by virtue of a pressure produced by vacuum of the container. Four sections of ear flanges (74) and fastening bolts thereof are arranged at 45-degree four corners, which do not influence the arrangement width and length, on the outer side of the container. A rubber sealing ring is arranged on the edges of the whole circle of flanges, vacuum sealing grease is arranged on an outer side of the rubber sealing ring, and a soft metal sealing ring is arranged on an inner side of the rubber sealing ring. Installation and support of the shell (and the whole flywheel device) may be realized by connecting the exposed ear flanges (74) and the supporting assembly (75) with a frame.

(204) The shell (52) is of a three-layer composite structure (FIG. 25). An intermediate layer is a glass chopped fiber reinforced epoxy resin, the two outer surfaces are made of aluminum alloys, and the intermediate layer is adhered with the outer surface layers. A magnetic fluid sealing assembly is arranged between the shell (52) and the rotation shaft (51).

(205) Radial supporting bearings of the rotation shaft (51) are two groups of rolling bearings. The rolling bearing positioned at the lower end bears a radial load and is a single-row deep groove ball bearing; and the rolling bearings positioned at the upper end bear the radial load and bidirectional axial load, serve as an axial positioning end and are a pair of angular contact ball bearings.

(206) An axial supporting bearing of the rotation shaft (51) is a permanent magnet attraction type axial supporting magnetic bearing. An axial positioning bearing close to the upper end has a stepped rotary disc (59) and a stepped stationary disc (60). The stationary disc is directly fixedly connected with a bearing block. The rotary disc is positioned below the stationary disc. An air gap is formed between end surfaces on adjacent sides of the two discs. The rotary disc is of a 45-steel axisymmetric structure. The stationary disc is of an axisymmetric structure of an aluminium alloy, electromagnetic pure iron and Nd—Fe—B permanent magnet. The aluminium alloy structure is a matrix of the stationary disc, a mixed disc structure formed by arranging electromagnetic pure iron rings and Nd—Fe—B permanent magnet rings at intervals forms a side end surface opposite to the rotary disc, the permanent magnet rings are magnetized outwards or inwards along a radial direction, adjacent permanent magnet rings have opposite magnetizing directions, and upward magnetic attraction force in an air-gap field acts on the rotary disc and is designed for offsetting gravity of the rotors. The magnetic bearings do not have magnetic hysteresis or eddy losses.

(207) The front gasoline engine includes: a maximal power of 60 kW, a rotation speed of 6000 r/min under a maximal power condition, a power of 40 kW under the maximal power condition, and a rotation speed of 4000 r/min under the maximal power condition.

(208) The transmission system includes three separated HET half-coupled members, i.e., a single flywheel, a separated HET and a two-wheel drive structure: the first half-coupled member (recorded as HETh11) shares the same rotation shaft with the flywheel (71), a rotation shaft of the second half-coupled member (recorded as HETh12) (72) is connected with a main reducing gear of the front drive axle by virtue of a three-stage speed ratio gear reducer (77), and a rotation shaft of the third half-coupled member (recorded as HETh3) (72) is connected with an output shaft of the engine (76) by virtue of a single-stage gear speed increaser. A main circuit of the three HET half-coupled members is connected in series with the external conductor by virtue of an external terminal (16) so as to form a main current closed circuit.

(209) The three HET half-coupled members are all double-magnetic flux, single-stage, single-circuit, near-axis coil, solid shaft, and axial surface type, and have the same electromagnetic structure and size. A meridian plane diagram of the flywheel shaft end half-coupled member HETh11 is shown in the part A in FIG. 26. A meridian plane diagram of each of the wheel-side half-coupled member HETh12 and the engine-side half-coupled member HETh3 installed on the frame is shown in FIG. 19.

(210) Sizes of the HET half-coupled members are as follows: a shaft surface radius of a rotation shaft is 53 mm, a radius of a stator body is 138.65 mm, a radius of an external terminal is 213.5 mm, and an axial length of a stator of the non-flywheel shaft end half-coupled member is 280 mm. A maximal designed value of a rotation speed of a rotation shaft of each of the half-coupled members is 13793.1 r/min, and a maximal designed value of main current is 29576 A. A maximal designed value of electromagnetic power of the HETh11 and HETh12 is 240 kW. A rated designed value of electromagnetic power of the HETh3 is 60 kW, and a maximal magnetic flux of the HETh3 is the same as that of the HETh11 or HETh12. Therefore, under a condition that the maximal magnetic flux and the maximal rotation speed of the HETh3 are used, when the electromagnetic power of 60 kW is reached, only ¼ of the maximal designed value of the main current should be used.

(211) Two magnet exciting coils of each of the half-coupled members are connected in series together in opposite rotation directions, are considered as a dual coil and are conducted with the same exciting current. The exciting current of the three half-coupled members is recorded as Ih11, Ih12 and Ih3 respectively. Since a magnetic field of the three separated half-coupled members mutually has independence, total magnetic flux may be expressed as follows:
ΣΦh11=Ffh11(|I0|,Ih11)  (d21)
ΣΦh12=Ffh12(|I0|,Ih12)  (d22)
ΣΦh3=Ffh3(|I0|,Ih3)  (d23)

(212) Further, since the three half-coupled members have the same electromagnetic structure size and consistent regularity, functional forms are the same and may be recorded as a functional form Ffh( ) that is,
ΣΦh11=Ffh(|I0|,Ih11)  (d24)
ΣΦh12=Ffh(|I0|,Ih12)  (d25)
ΣΦh3=Ffh(|I0|,Ih3)  (d26)

(213) Meanwhile, a calculated amount of corresponding regularity content may be reduced, and only calculation should be performed on one of the half-coupled members.

(214) An adjustment and control method based on a minimal sum principle of two losses adopted by the series system of the three HET half-coupled members is as follow:

(215) The total loss is a sum of main current ohmic heat (I0.Math.I0.Math.R0) and each exciting current ohmic heat (ΣPoi), wherein R0 and Ri are constant values.

(216) An application range of rotation speeds of three shafts, an application range of Mhe12 and an application range of Mhe3 or Mhe11 are given. By utilizing the electromagnetic law formulas ((d1), (d3), (d5), (d6), (d10), (d13), (d15) or (d11), and R0 is a constant value) and the above multidimensional variable function relationships ((d24), (d25), (d26)), a matrix of optimum values Iiopt of each exciting current that fully covers different rotation speed conditions and torque demands and satisfies a total loss minimum target is calculated, and all the data are stored in the control system.

(217) When regulation is executed, rotation speeds (ωh11, ωh12 and ωh3) of the three rotors are acquired in real time as input conditions, an instruction of the needed torque Mhe12, Mhe3 or Mhe11 is given as an input condition, related stored data is invoked from the control system, and a corresponding optimum value Iiopt of each exciting current is calculated by adopting a spline interpolating function formula for use in the execution link.

(218) An adjustment and control method, with a principle that a sum of three losses is minimal, adopted by the series system of the three HET half-coupled members is as follow.

(219) The total loss is a sum of main current ohmic heat (I0.Math.I0.Math.R0), each exciting current ohmic heat (ΣPoi) and circuit “connecting region clearance” liquid metal friction heat, wherein R0 is a function of liquid metal state parameters MLS, and Ri is a constant value.

(220) An application range of rotation speeds of three shafts, an application range of Mhe12, an application range of Mhe3 or Mhe11 and an application range of the circuit “connecting region clearance” liquid metal state parameters MLS are given. By utilizing the electromagnetic law formulas ((d1), (d3), (d5), (d6), (d10), (d13), (d15) or (d11), and R0 is a function of the liquid metal state parameters MLS) and the above multidimensional variable function relationships ((d24), (d25), (d26)), a matrix of optimum values Iiopt of each exciting current and a matrix of optimum values MLSopt of the liquid metal state parameters, which fully cover different rotation speed conditions and torque demands and satisfy a total loss minimum target, are calculated, and all the data are stored in the control system.

(221) When regulation is executed, rotation speeds (ωh11, ωh12 and ωh3) of the three rotors are acquired in real time as input conditions, an instruction of the needed torque Mhe12, Mhe3 or Mhe11 is given as an input condition, related stored data is invoked from the control system, and a corresponding optimum value Iiopt of each exciting current and an optimum value MLSopt of the liquid metal state parameters are calculated by adopting the spline interpolating function formula for use in the execution link.

(222) Wires connected with an external DC power supply are connected in parallel on the external conductors on each of the flywheel shaft end HET half-coupled members, and are used for realizing (respectively) plug-in charging or unloading on each of the flywheels. The external power supply used for performing plug-in charging or unloading on the flywheels adopts an adjustable voltage DC power unit which is arranged in the vehicle and connected with power grid alternating current, and the maximal design power is 7 kW. During plug-in charging, the circuit “connecting region clearances” (5) of the non-flywheel shaft end HET half-coupled member are disconnected, the circuit “connecting region clearances” (5) of the flywheel shaft end half-coupled members are connected, related magnet exciting coils enabling magnetic flux of the HET flywheel end rotor to reach a maximum value are connected, and the maximum exciting current is always maintained. A voltage size of the DC power supply is adjusted to be equal to electromotive force of the HET flywheel end rotor, and the voltage direction is opposite to the electromotive force direction. A main current circuit is connected with the DC power supply. The voltage of the DC power supply is increased to reach a rated limit value of plug-in main current or a rated limit value of plug-in power. The voltage of the DC power supply is continuously increased in a flywheel charging and speeding-up process, and the rated limit value of the plug-in main current and/or the plug-in power is maintained. Current limitation and power limitation are performed in sequence. When a starting point of the flywheel rotation speed is high, only power limitation is performed. When charging is ended, the voltage of the DC power supply is decreased to obtain zero current, the main current circuit is disconnected from the DC power supply, and HET magnet excitation is canceled. During plug-in unloading, a set-up procedure is the same as above, current directions are opposite, and operating procedures are opposite, that is, the voltage of the DC power supply is decreased to reach a rated limit value of plug-in unloading power or a rated limit value of plug-in unloading main current.

(223) In a situation that the flywheel has available energy or kinetic energy is being recovered, the engine is preferably started by adopting the energy of the flywheel or the recovered kinetic energy, directly dragged to an idling speed, and then ignited by virtue of fuel injection.

(224) When the vehicle is parked, an operation of starting the engine by the energy of the flywheel is performed by a control system as follows: the circuit “connecting region clearances” (5) of the three HET half-coupled members are connected, an instruction for a set electromagnetic torque Mhe3 for reversely dragging the engine to be started is given, the electromagnetic torque Mhe1 is set as zero, the HET series system is controlled by adopting a corresponding separated HET adjustment and control method, and the engine is started by utilizing the energy of the flywheel so as to reach the idling speed.

(225) When the vehicle runs, an operation of starting the engine by the energy of the flywheel or the recovered kinetic energy is performed by the control system as follows: the instruction for the set electromagnetic torque Mhe3 for reversely dragging the engine to be started is given, an original instruction of the electromagnetic torque Mhe12 is maintained, the HET series system is controlled by adopting the corresponding separated HET adjustment and control method, and the engine is started by utilizing the energy of the flywheel or less recovered energy thereof so as to reach the idling speed.

(226) The engine is equipped with a speed controller. An operating condition is adjusted and controlled on a working condition route connecting an idling speed condition, a maximum efficiency condition and a maximum power condition by the speed controller, and in an adjustable buffer zone nearby the route. On an overall working condition route represented on a torque-rotation speed diagram (vertical axis torque, horizontal axis torque), the rotation speed, torque, power and throttle opening at each point are always monotonically increased, and optimum efficiency points of a series of equipower lines are selected to form an optimal condition route. The above working condition route is changed into a curve on a throttle opening-rotation speed diagram. During adjustment, when detected state points of the rotation speed and the throttle opening are located on the right side of the route (a higher rotation speed side), the throttle opening is decreased; otherwise the throttle opening is increased.

(227) When the vehicle is parked, the engine charging the flywheel preferably selects the maximum efficiency condition. When shorter load time is needed, a higher power condition is used until the maximum efficiency condition is reached. Before the selected engine load condition is reached, a raising condition transition process starting from the idling condition exists. When the rotation speed of the flywheel is not lower than an indicator rotation speed before loading, that is, loaded power capacity is not lower than a load condition power of the engine, the raising condition transition process is very fast; and when the rotation speed of the flywheel is lower than the indicator rotation speed before loading, the raising condition transition process is synchronized with a process of raising the speed of the flywheel to the indicator rotation speed, and then a higher torque of the flywheel is controlled, thereby accelerating the transition process.

(228) Three typical solutions of charging the flywheel by the engine while parking the vehicle are as follows:

(229) a condition that an initial rotation speed of the flywheel is zero: the circuit “connecting region clearances” (5) of the three HET half-coupled members are connected, and the HET series system is controlled by adopting the corresponding separated HET adjustment and control method: giving an Mhe12 zero instruction, giving an Mhe11 instruction according to two sections, enabling the Mhe11 instruction on the former section to be identically equal to a maximum torque Mhe11max, converting into constant power control when the rotation speed ωh11 of the flywheel reaches an indicated rotation speed ωh11p, and enabling the Mhe11 instruction to be equal to a ratio Pload/ωh11 of the load condition power of the engine to the rotation speed of the flywheel;

(230) a condition that the initial rotation speed of the flywheel is not zero but lower than the indicated rotation speed: the circuit “connecting region clearances” (5) of the three HET half-coupled members are connected, and the HET series system is controlled by adopting the corresponding separated HET adjustment and control method: giving an Mhe12 zero instruction, giving an Mhe11 instruction according to three sections, enabling the Mhe11 instruction on the former section to adopt a curve changing from zero to the maximum torque Mhe11max rapidly, enabling the intermediate Mhe11 instruction to be equal to the maximum torque Mhe11max, converting into constant power control when the rotation speed ωh11 of the flywheel reaches an indicated rotation speed ωh11p, and enabling the Mhe11 instruction to be equal to the Pload/ωh11; and

(231) a condition that the initial rotation speed of the flywheel is higher than the indicated rotation speed: the circuit “connecting region clearances” (5) of the three HET half-coupled members are connected, and the HET series system is controlled by adopting the corresponding separated HET adjustment and control method: giving an Mhe12 zero instruction, giving an Mhe11 instruction according to two sections, enabling the Mhe11 instruction on the former section to adopt a curve changing from zero to the Pload/ωh11 rapidly, and enabling the Mhe11 instruction on the rear section to be equal to the Pload/ωh11.

(232) A load rotation speed upper limit value is set for the flywheel, that is, charge loading of the flywheel is ended when the rotation speed reaches the limit value. The upper limit value of the rotation speed is a maximal rotation speed 13793.1 r/min of the flywheel.

(233) A running rotation speed lower limit value of 9194.5 r/min is set for the flywheel. When the rotation speed of the flywheel reaches the running rotation speed lower limit value from a higher speed to a lower speed, the flywheel stops outputting power, and charge loading to the flywheel is started. The vehicle is not driven by the flywheel any more before the rotation speed of the flywheel rises to an intermediate rotation speed limit value of 9655.2 r/min.

(234) When the vehicle runs, the speed is always switched between two stages, that is, an overall flywheel speed increasing stage (occasionally speed decreasing) and an overall flywheel speed decreasing stage (occasionally speed increasing). Uninterrupted continuity of the vehicle driving/braking torque is maintained during switch of a current stage and a next stage, that is, the wheel-side torque Mhe12 is kept invariable, and the engine-side and flywheel-side torque and power are in smooth balanced transition.

(235) At the overall flywheel speed increasing stage: the flywheel runs in a range from the running rotation speed lower limit value to the load rotation speed upper limit value; the engine always outputs the power, even if the vehicle is braked by the flywheel; the engine runs in the maximal power condition in an area between the running rotation speed lower limit value and the intermediate rotation speed limit value; the engine operating condition is preferably the maximum efficiency condition for loading the flywheel and driving the vehicle in an area between the intermediate rotation speed limit value and the load rotation speed upper limit value; when power Pmaxe of the engine under the maximum efficiency condition is totally used for driving the vehicle and is still insufficient, the flywheel outputs power to assist driving; and when driving power of the flywheel reaches the current maximum value and is still insufficient, the power of the engine is increased, that is, transition from the power Pmaxe to the maximal power Pmax is performed until the maximal driving power of the flywheel and the maximal power of the engine are totally used for driving the vehicle.

(236) At the overall flywheel speed decreasing stage: the flywheel runs in a range from the load rotation speed upper limit value to the running rotation speed lower limit value; the engine occasionally outputs power; when the vehicle is braked by the flywheel, the engine does not run; the vehicle is driven by the flywheel mainly, and when the driving power of the flywheel reaches the current maximal value and is still insufficient, the power Pmaxe of the engine is added, and the power of the flywheel is correspondingly decreased; and when a sum of the maximal power of the flywheel and the Pmaxe is still insufficient, the power of the engine is increased, that is, transition from the power Pmaxe to the maximal power Pmax is performed.

(237) Power control units are arranged on a vehicle driving seat as follows: a drive pedal, a brake pedal, and initial setting operating levers of aheading gear 1, aheading gear 2, aheading gear 3 and reversing gear 1.

(238) Instructions for driving torque relative values ranging from zero to a maximal value are correspondingly output in a drive pedal travel. The torque and the travel adopt a non-linear relation. The torque at an initial stage is increased slowly, so as to easily control a low running speed of the vehicle. The maximal value of the driving torque is a currently available maximal value and is calculated by a power control system according to current state measurement parameters.

(239) Travel of the brake pedal is divided into a front travel and a rear travel. The front travel corresponds to kinetic energy recovery braking torque relative values ranging from zero to a maximal value. The rear travel corresponds to friction braking torque relative values ranging from zero to a maximal value. The maximal value of the kinetic energy recovery braking torque is simultaneously maintained in the rear travel. Kinetic energy recovery braking is to recover kinetic energy of the vehicle to the flywheels by virtue of reverse power flow transfer of the HET. Friction braking is to convert the kinetic energy of the vehicle into heat energy by adopting four vehicle friction braking discs. The maximal value of the kinetic energy recovery braking torque is a currently available maximal value and is calculated by the power control system according to current state measurement parameters.

(240) The initial setting operating levers of the aheading gear 1, aheading gear 2, aheading gear 3 and reversing gear 1 give consideration to aheading and reversing settings and initial speed ratio gear settings. A transmission ratio at the gear 1 is larger, the transmission ratio at the gear 2 is intermediate, and the transmission ratio at the gear 3 is smaller. Initial setting of aheading at gear 1 is as follows: a three-stage speed ratio gear reducer is located in a gear-1 transmission ratio state at an aheading speed of the vehicle ranging from zero to a first intermediate switching speed, located in a gear-2 transmission ratio state in a range from the first intermediate switching speed to a second intermediate switching speed, and located in a gear-3 transmission ratio state in a range from the second intermediate switching speed to the highest vehicle speed. Initial setting of aheading at gear 3 is as follows: the three-stage speed ratio gear reducer is always located in the gear-3 transmission ratio state. Initial setting of reversing at gear 1 is as follows: the three-stage speed ratio gear reducer is located in the gear-1 transmission ratio state at a vehicle reversing running speed ranging from zero to an intermediate speed, and a speed limit does not exceed the intermediate speed. During reversing, the HETh12 output shaft and a rear axle system thereof are reversed, and a special reverse gear block does not exist.

(241) A gear-shifting operation while running is automatically controlled by the power control system. When a preset gear shifting speed is reached, the transferred torque is controlled to be decreased to zero, an original gear is released, two synchronous to-be-engaged parts are rubbed by a synchronizer, a new gear is engaged, and the needed torque is transferred according to the current driving torque command.

(242) (e) Mechanical Connection and Load Charging System for Energy Storage Flywheel of Vehicle Including HET

(243) A mechanical connection and load charging system for flywheel of vehicle adopts components as follows: a load joint, a load-end vertical separated half-coupled member HETho (FIG. 30) and a manipulator system, an energy supply end vertical separated half-coupled member HEThi (FIG. 31), a bevel gear speed increaser and a horizontal synchronous motor. A rated load power is 2000 kW.

(244) The HETho rotation shaft serves as a load rotation shaft. The load joint is assembled at the upper end of the load rotation shaft. The load joint and a loading disc (69) at the lower end of a vehicle flywheel rotation shaft adopt an external-contacting rubber tube hydraulic connecting structure. The load joint has a hydraulic connecting disc (80) and a spline disc (81). The spline disc and an involute spline of the load rotation shaft are in matched connection and torque transfer. The hydraulic connecting disc and the spline disc are located by adopting a seam allowance and subjected to torque transfer by using four circumferentially uniformly distributed cylindrical pins (87). A central end surface of the hydraulic connecting disc and a shaft end surface of the load rotation shaft are fixedly attached by adopting four screws (88). An outer edge of the hydraulic connecting disc is of a cylinder type extending upwards. A peripheral groove is formed in an inner wall of the cylindrical part. A rubber ring (82) made of polyurethane is arranged in the groove. An outer surface of the rubber ring has a longer inner cylindrical surface and a longer outer cylindrical surface. Three axially arranged circular round holes are included in the rubber ring. Two circumferentially uniformly distributed radial through holes towards the outer side are formed corresponding to each of the circular round holes. Corresponding to an orientation of the two rows of radial through holes, two hydraulic circuits (83) communicated with the radial through holes are formed inside the hydraulic connecting disc. The two hydraulic circuits are converged at an axis oil hole of the hydraulic connecting disc. The axis oil hole is butted and communicated with an axis through hole (84) in the load rotation shaft (that is, the HETho rotation shaft). Hydraulic oil is supplied by a hydraulic pressure station of an auxiliary system, and input into the axis through hole (84) and an oil circuit communicated thereby by virtue of a pipeline and a sealed joint at a shaft end at the lower end of the HETho rotation shaft. The outer cylindrical surface of the rubber ring and an outer round-corner surface are adhered and sealed with the surface of the groove in the hydraulic connecting disc, thereby ensuring docking seal between the two rows of radial through holes and the hydraulic circuit. When the hydraulic circuit is subjected to emptied oil filling and is not pressurized, the rubber ring retains an initial shape, a radius of the inner cylindrical surface of the rubber ring is 0.5 mm larger than a radius of the outer cylindrical surface of the flywheel loading disc, and then the load joint may be controlled to axially move (approaching or deviating). When a pressure of the hydraulic oil is increased, a pressure in an inner hole chamber of the rubber ring is increased, the rubber ring expands, and a radius of the inner cylindrical surface of the rubber ring is shrunk, thereby achieving an effect of holding the outer cylindrical surface of the flywheel loading disc; and after the pressure of the hydraulic oil is decreased, the rubber ring restores to the initial shape. When the load rotation shaft rotates, the hydraulic oil in the inner hole chamber of the rubber ring is increased by virtue of a generated centrifugal force effect, and centrifugal force of the rubber ring is increased to cause an outward displacement of the inner cylindrical surface of the rubber ring. In order to avoid uncertainty of the centrifugal force effect and action effects thereof, before the load rotation shaft reaches a load operating position and when the load rotation shaft deviates from the load operating position, the load rotation shaft is positioned in a zero rotation speed state. In order to prevent residual air existing in an engagement area when the rubber ring externally contracts the loading disc, two annular grooves (85) are formed in the outer cylindrical surface of the loading disc. Axial positions of the grooves correspond to a centrally parting point of axial positions of two annular round holes of the rubber ring, and two groups of circumferentially uniformly distributed vent holes (86) are formed in the loading disc, thereby communicating the grooves with outside.

(245) The load-end vertical separated half-coupled member HETho (FIG. 30) and the energy supply end vertical separated half-coupled member HEThi (FIG. 31) are arranged on the same axis, and are electromagnetic structure types of two-stage external series, each-stage double-magnetic flux, near-axis magnet exciting coils and half-height rotor electric conductors (4). Main parameters of each of the half-coupled members include: rated electromagnetic power of 2000 kW, a rated rotation speed of 10000 r/min, a rated main current value of 65644 A, a rated electromotive force value of 30.5V, an axial surface radius 85.285 mm of the rotation shaft, a maximal rotor radius of 145.8 mm, a stator body radius of 232.8 mm, an external terminal radius of 342.8 mm, a stator axial length of 600.5 mm, and rotor mass of 175 kg.

(246) The half-coupled member HETho (FIG. 30) and the half-coupled member HEThi (FIG. 31) have most of the same structural details as those of the separated HET half-coupled members (FIG. 19) adopted in specific embodiments of the above power system. Since the separated HET half-coupled members (FIG. 19) are described above, only main differences between the half-coupled members HETho and HEThi and the separated HET half-coupled members shown in FIG. 19 are described below.

(247) The HETho and HEThi have a series two-stage structure. The series two-stage structure is basically formed in combining single-stage structures shown in FIG. 19 in series. Four magnet exciting coils (9) of the two single-stage structures are reduced to three magnet exciting coils (9) (corresponding to exciting current I1, I2 and I3 in FIG. 12, FIG. 30 and FIG. 31), that is, two coils at intermediate positions of the original four magnet exciting coils with consistent exciting current directions are merged into a coil (I3), original two main magnetic circuits are merged into a main magnetic circuit, and original two stator magnetic conductors (10) are canceled. Coils at both ends with exciting current of I1 and I2 have the same structure and number of turns. Since the magnetic circuit structures are symmetrical, magnetic flux passing through rotor magnetic and electric conductors generated when I1 and I2 are equal to each other also has the same size. An intermediate coil with exciting current of the I3 has a large number of turns. The arranged number of turns ensures that magnetic flux generated by the rated value of I3 is the same as magnetic flux generated by rated values of the I1 and I2, that is, an effect of combining the two single-stage structures is achieved. In an actual application, wires of the three magnet exciting coils are connected in series, the I1 and the I2 are always equal to each other and have the same direction, the I3 and the I1 have opposite directions, and a ratio of numerical values of the I3 and the I1 is always equal to a ratio of the number of turns thereof, so that functional relations between the total rotor magnetic flux and influencing factor changes thereof are simplified, and electromagnetic law formulas and adjustment and control methods of the separated HET half-coupled members shown in FIG. 19 can be adopted in reference.

(248) Connection of main current circuits adopts solutions of mixed flexible cables arranged between external terminals (16) (FIG. 29, FIG. 30 and FIG. 31) between the two stages of each of the half-coupled members and between the HETho and HEThi. The mixed flexible cables adopt circular flexible wire bundles (91) with an outer contour diameter of 6 mm which are made of red copper wire materials with a wire diameter of a fraction of a millimeter and composed of fine wires. The flexible cables are connected between two-stage external terminals of each of the half-coupled members and between external terminals of the HETho and HEThi according to the solutions shown in FIG. 29, FIG. 30 and FIG. 31. The wire bundles in the same path and same current direction are arranged in a row. Various rows of the wire bundles in different paths and different current directions are alternatively arranged into fan-shaped blocks. Eight fan-shaped blocks are circumferentially and uniformly distributed. Spaces through which other pipelines and leads pass are reserved among the fan-shaped blocks. The wire bundles and red copper external terminals are in brazed connection, or red copper intermediate transition terminals are in brazed connection with the wire bundles and the red copper external terminals. Lengths of the wire bundles between the HETho and HEThi external terminals should meet as follows: upward and left-and-right movements of the HETho and the load rotation shaft meet limit requirements of the operating positions, that is, the HETho and the load rotation shaft have full stretching flexibility.

(249) The manipulator system is provided with three spherical hinge fulcrums (fulcrums P1, P2 and P3) on the outer surface of the HETho. In an attached rectangular coordinate system by taking an axial lead of the HETho rotation shaft as a vertical axis Zb, the three fulcrums have the same Zb coordinates (the Zb value is set as zero). A distance between each of the three supports and the Zb axis is the same (the distance is R=340 mm). The three fulcrums are circumferentially and uniformly distributed. The point P1 is located on an Xb axis. Six linear stepping actuators are adopted to control absolute coordinates of the three supports. A ground absolute rectangular coordinate system (X, Y, Z) and an attached rectangular coordinate system (Xb, Yb, Zb) at an initial position are coincided. Z-axis coordinates of the three supports are directly controlled. A Y-axis coordinate of the point P1 is directly controlled. X-axis coordinates of the points P2 and P3 are directly controlled. An X-axis coordinate of the point P1 and Y-axis coordinates of the points P2 and P3 are indirectly controlled by a rigid connection relation of the three points. Z-axis control of each of the supports is as follows: a prismatic kinematic pair of upper and lower members (specifically a cylindrical kinematic pair with a guide sliding key, the same below) is adopted, a lower-end member is rigidly connected to a stationally frame and a foundation, a cylindrical hole seat with a key groove is formed in the upper end of the lower-end member, a shaft extension with a key is arranged at the lower end of an upper-end member, the lower-end member and the upper-end member are assembled into the prismatic kinematic pair, an output shaft of a linear stepping actuator (specifically a stepping motor and leadscrew nut transmission mechanism, the same below) is connected below the shaft extension end, and machine legs of the linear stepping actuator are fixed on the lower-end member. Y-axis control of the point P1 is as follows: a prismatic kinematic pair is adopted, wherein one member is an upper-end member of a Z-axis control kinematic pair of the point P1, and a pair of cylindrical hole seats with key grooves of which axes are parallel to the axis Y is arranged on the member; and shaft extensions with keys are arranged at both ends of the other member, a cylindrical hole seat without a key groove of which the axis is parallel to the axis Z is arranged in the middle of the member, the shaft extensions at the both ends and the pair of hole seats are assembled into the prismatic kinematic pair, the shaft extension at one end is connected with the output shaft of the linear stepping actuator, and machine legs of the linear stepping actuator are fixed on the upper-end member. X-axis control of the point P2 (point P3) is as follows: a prismatic kinematic pair is adopted, wherein one member is an upper-end member of a Z-axis control kinematic pair of the point P2 (point P3), and a pair of cylindrical hole seats with key grooves of which axes are parallel to the axis Y is arranged on the member; and shaft extensions with keys are arranged at both ends of the other member, a cylindrical hole seat without a key groove of which the axis is parallel to the axis Y is arranged in the middle of the member, the shaft extensions at the both ends and the pair of hole seats are assembled into the prismatic kinematic pair, the shaft extension at one end is connected with the output shaft of the linear stepping actuator, and machine legs of the linear stepping actuator are fixed on the upper-end member. A cylindrical piston is respectively assembled in each of the three cylindrical hole seats without the key grooves. A spherical plain bearing block is installed in the center of an end surface, which is close to the axis Z, of the piston. The spherical plain bearing block and a matched spherical bar head are combined into a spherical hinge. Centers of spheres of the three spherical hinges are the points P1, P2 and P3. Three supporting rods with the spherical bar heads are fixedly connected above a support ring (92) added at a flange at the upper end of the HETho stator.

(250) A system for detecting the orientation of the vertical flywheel rotation shaft of the vehicle in the manipulator system is also applied. A non-contact distance measuring instrument is adopted. Nine distance data between three measuring mark points on a symmetrical fixing piece coaxial with the rotation shaft at the flywheel rotation shaft end and three fixed datum points of the detection system are measured, and three-dimensional spatial absolute coordinates of the three measuring mark points are calculated and determined, thereby determining the spatial positions and direction angles of the flywheel shaft end (that is, three spatial coordinates and two direction angles). Working procedures performed before loading include steps: opening a protective cover at the flywheel shaft end, measuring and determining the spatial positions and direction angles of the flywheel shaft end, adjusting and moving the HETho in a ready position and a posture that the axis is coincided with the flywheel by utilizing the manipulator system, and linearly translating the HETho to a load operating position. In order to ensure smooth engagement and alignment before loading, guiding measures are added: a guide sleeve ring (90) is attached to a flywheel shaft end shell, a guide sleeve (89) is attached to a bearing block at the upper end of the HETho, and the guide sleeve ring and the guide sleeve are matched to achieve an auxiliary guiding effect during engagement and alignment. The guiding measures may also be applied to manual engagement and alignment.

(251) The horizontal synchronous motor has a rated power of 2000 kW, runs at a synchronous rotation speed of 3000 r/min after started, and can reversely run to serve as a synchronous generator when stored energy of the flywheel of the vehicle should be unloaded to the power grid. The bevel gear speed increaser has a pair of spiral bevel gears subjected to gear grinding, two axes are perpendicular to each other, and a speed-up transmission ratio is 3.333.

(252) A fixing and supporting device for the vehicle frame is arranged and adopts a three-point supporting structure, that is, two front supporting points and a rear supporting point of the vehicle are arranged. Three hydraulic jacks are arranged between a standard setting supporting bottom surface of the frame and a ground support. The vehicle is controlled to be jacked by the system after entry, tires are overhead, and the frame is fixed, so that the positions of the flywheels located on the frames are stabilized.

(253) (f) Wind Power Generation System Including HET

(254) A specific embodiment of a 1.5 MW wind power generation system (FIG. 40) with HET is as follows.

(255) The system includes: a horizontal axis type variable pitch blade wind wheel, a horizontal speed-up gear box connected with a wind wheel shaft, a homopolar DC electromagnetic transmission (HET) connected with a gear box output shaft and a generator shaft, a horizontal synchronous generator, a mechanical brake apparatus arranged at the wind wheel shaft, a yawing driven active yawing mechanism, a cabin, a tower and a control and attached system.

(256) The wind wheel adopts three aerofoil profile blades. A maximum value of a wind-power utilization coefficient Cp is 0.47, a corresponding optimal tip speed ratio is 7, and the optimal tip speed ratio and the maximum value Cp are used at a rated design point. A rated wind speed 12 m/s of lower wind energy with a wide applicable wind field range is selected. A rated rotation speed of the wind wheel is 24.31 r/min, a rated tip linear speed is 84 m/s, and the rated power is 1670 kW. A diameter of the wind wheel is 66 m.

(257) The speed-up gear box increases the rotation speed from 24.31 r/min to 1500 r/min under a rated working condition, so that the two rotors of the HET have the same rated rotation speed. A speed-up ratio is 61.7. A three-stage transmission manner is adopted. The forward two stages are planet gears, and the backward stage is a parallel shaft cylindrical gear.

(258) The synchronous generator has a rated output power of 1.5 MW, runs at a constant speed of 1500 r/min, outputs alternating current of 50 Hz and is connected to the power grid by virtue of a boosting transformer.

(259) The HET is a horizontal separated type, has a pair of HET half-coupled members (FIG. 38) of the same specification, and has a rated power of 1612 kW, a rated rotation speed of 1500 r/min, rated main current of 107873 A and rated efficiency of 97%. Each of the HET half-coupled members has a single-stage, solid-shaft, double-magnetic flux and near-axis coil structural form. Geometry and weight parameters of each of the HET half-coupled members include: a maximum rotor outer diameter of 701.8 mm, a maximum stator body outer diameter of 928.9 mm, an external terminal outer diameter of 1239.5 mm, an overall length of 804.7 mm, a rotor weight of 927 kg and a total weight of 2604 kg.

(260) Embodiments of the HET half-coupled members (FIG. 38) are as follows. Only parts different from explanations in embodiments of “(a) homopolar DC electromagnetic transmission (HET)” are described.

(261) The rotation shaft is a hollow shaft. A middle section is provided with hollow 20-steel magnetic conductors (2). Both ends are provided with 40Cr steel end shafts (180, 182) and a 20-steel steel lantern ring (181). The lantern ring (181) is used for magnetic conduction of a magnetic fluid sealing element (37). Interference fitting is formed between the magnetic conductors (2) and the end shafts and between the end shafts and the lantern ring, and sealants are applied to contact end surfaces. A rolling bearing (a deep groove ball radial bearing, grease lubricating, with contact-type sealing rings on two sides) is respectively arranged on each of the end shafts. The bearing on one side of a shaft extension end is an axial positioning end and can bear a bidirectional axial load, and the bearing on one side without the shaft extension end is a free end capable of producing an axial displacement. An axial bearing load generated by gravity of the rotor is larger than a minimum load thereof, and additional pre-loading measures do not need to be increased for the two bearings. An external spline is arranged at the shaft extension end and is used for installing a coupling to be connected the generator rotation shaft and the gearbox output shaft.

(262) Connection of main current circuits between the two separated HET half-coupled members adopts solutions of external terminals (16) and mixed flexible cables (FIG. 39). The mixed flexible cables adopt circular flexible wire bundles (91) which are made of red copper wire materials with a wire diameter of a fraction of a millimeter and composed of fine wires. The wire bundles in the same current direction are arranged in a row. Various rows of the wire bundles in different current directions are alternatively arranged into fan-shaped blocks. 16 fan-shaped blocks are circumferentially and uniformly distributed. Spaces through which other pipelines and leads pass are reserved among the fan-shaped blocks. The wire bundles and red copper external terminals are in brazed connection, or red copper intermediate transition terminals are in brazed connection with the wire bundles and the red copper external terminals.

(263) The second type of adjustment and control method of the HET above can be adopted for electromagnetic torque control of the HET.

(264) A wind power system start-up process is as follows: when a start-up wind speed is reached, a pitch angle of the blades of the wind wheel ranges from a decreased angle at a “feathering” position to a pitch angle with a larger starting torque, an impeller is driven to be self-started by the wind power, the synchronous generator rotor is driven to speed up from a zero rotation speed to a synchronous rotation speed of 1500 r/min by virtue of HET transmission, and then connected to the power grid by virtue of synchronous grid-connected operating procedures; and after the starting process is completed, the blade pitch angle rotates to a rated design pitch angle, and the rotation speed of the impeller is adjusted to a rotation speed value meeting the optimal tip speed ratio of 7.

(265) A conventional operating control solution in a range from a cut-in wind speed to a rated wind speed is as follows: the wind wheel blades maintain a control objective that the design pitch angle linearly changes along with a direct wind speed ratio according to the wind wheel rotation speed (that is, a ratio of the tip linear speed to the wind speed is equal to 7), a local mean wind speed (outside the cabin), the wind wheel rotation speed and the generator rotation speed are measured in real time, a proportional relation between the wind wheel torque and second power of the wind speed is taken as a mater control rule, an instruction for the torque Me1 of the rotation shaft of the wind-wheel-side HET half-coupled member HETh1 is given, and operations of the HET and power transfer thereof are adjusted and controlled. When the rotation speed of the wind wheel is lower than a constant value of a target rotation speed, the Me1 instruction is appropriately decreased so as to lighten an output load of the wind wheel, thereby speeding up the wind wheel. When the rotation speed of the wind wheel is higher than the constant value of the target rotation speed, the Me1 instruction is appropriately increased so as to increase the output load of the wind wheel, thereby reducing the speed of the wind wheel.

(266) A power limitation control solution in a range from the rated wind speed to the cut-in wind speed is as follows: by taking measures that the variable pitch angle changes towards aspects of decreasing a stall trend, decreasing an airflow angle of attack and increasing the pitch angle of the blades, the power and the impeller rotation speed are kept constant in principle (equal to the rated value), that is, the wind-power utilization coefficient Cp of the impeller and third power of the wind speed are in inversely proportional change, and a tip speed ratio λ and the wind speed are in inversely proportional change. A moving track that the value Cp and third power of the λ are proportional is shown in a Cp-λ diagram, and is a steep curve. An intersection set of a set of curves and the steep curve is solved by utilizing a set of Cp-λ curves under different pitch angles in an adjustable pitch angle range, and a corresponding law that the pitch angle changes along the wind speed is determined from the intersection set. The local mean wind speed, the wind wheel rotation speed and the generator rotation speed are measured in real time, the pitch angle is adjusted according to the corresponding law, a torque Me1 instruction for the rotation shaft of the HETh1 is given according to a master control rule that the wind wheel torque is equal to a rated torque, and the operations of the HET and the power transfer thereof are adjusted and controlled. When the rotation speed of the wind wheel is lower than a constant value of a rated rotation speed, the Me1 instruction is appropriately decreased so as to lighten the output load of the wind wheel, thereby speeding up the wind wheel. When the rotation speed of the wind wheel is higher than the constant value of the rated rotation speed, the Me1 instruction is appropriately increased so as to increase the output load of the wind wheel, thereby speeding down the wind wheel.

(267) An impeller brake and stop process is as follows: when the cut-out wind speed is reached, or other braking instructions are transmitted, the pitch angle of the wind wheel blades is rotated to the “feathering” position, aerodynamic braking is implemented, and mechanical braking of a brake disc arranged at the wind wheel shaft is performed until the wind wheel stops rotating.

(268) (g) Wind Power Generation System Including HET and Flywheels

(269) A specific embodiment of a 1.5 MW wind power generation system (FIG. 41) with HET and flywheels is as follows.

(270) The system includes: a horizontal axis type variable pitch blade wind wheel, a horizontal speed-up gear box connected with a wind wheel shaft, a homopolar DC electromagnetic transmission (HETw) connected with a gear box output shaft and indirectly connected a generator shaft, a horizontal synchronous generator, a suspended flexible flywheel device, a homopolar DC electromagnetic transmission (HETf) connected with flywheel rotation shafts and the generator shaft, a mechanical brake apparatus arranged at the wind wheel shaft, a yawing driven active yawing mechanism, a cabin, a tower and a control and auxiliary system.

(271) The wind wheel adopts three aerofoil profile blades. A maximum value of a wind-power utilization coefficient Cp is 0.47, a corresponding optimal tip speed ratio is 7, and the optimal tip speed ratio and the maximum value Cp are used at a rated design point. A rated wind speed 12 m/s of lower wind energy with a wide applicable wind field range is selected. A rated rotation speed of the wind wheel is 24.31 r/min, a rated tip linear speed is 84 m/s, and the rated power is 1670 kW. A diameter of the wind wheel is 66 m.

(272) The speed-up gear box increases the rotation speed from 24.31 r/min to 1500 r/min under a rated working condition, so that the two rotors of the HET have the same rated rotation speed. A speed-up ratio is 61.7. A rated input power is 1670 kW. A three-stage transmission manner is adopted. The forward two stages are planet gears, and the backward stage is a parallel shaft cylindrical gear.

(273) The synchronous generator has a rated output power of 750 kW (power halved design), runs at a constant speed of 1500 r/min, outputs alternating current of 50 Hz and is connected to the power grid by virtue of a boosting transformer.

(274) The HETw is a horizontal separated type, has a pair of HET half-coupled members (FIG. 38) of the same specification, and has a rated power of 1612 kW, a rated rotation speed of 1500 r/min, rated main current of 107873 A and rated efficiency of 97%. Each of the HET half-coupled members has a single-stage, solid-shaft, double-magnetic flux and near-axis coil structural form. Geometry and weight parameters of each of the HET half-coupled members include: a maximum rotor outer diameter of 701.8 mm, a maximum stator body outer diameter of 928.9 mm, an external terminal outer diameter of 1239.5 mm, an overall length of 804.7 mm, a rotor weight of 927 kg and a total weight of 2604 kg.

(275) The HETf is a horizontal separated type, and has a horizontal half-coupled member HETfhe (FIG. 66) connected with the generator shaft and a vertical half-coupled member HETfhf (FIG. 67) connected with the flywheel rotation shaft, as well as a rated output power of 750 kW (power halved design), and rated main current of 60959 A. The half-coupled member HETfhe has a rated rotation speed of 1500 r/min, has a single-stage, solid-shaft, double-magnetic flux and near-axis coil structural form, and includes parameters: a maximum rotor outer diameter of 571.1 mm, a maximum stator body outer diameter of 806.6 mm, an external terminal outer diameter of 1133 mm, an overall length of 945 mm, a rotor weight of 821 kg and a total weight of 2481 kg. The half-coupled member HETfhf has a rated rotation speed of 3796.25 r/min, has a design power of 3×750 kW (may reach a rated power of 750 kW at ⅓ of the rated rotation speed), has a single-stage, solid-shaft, double-magnetic flux and near-axis coil structural form, and includes parameters: a maximum rotor outer diameter of 527.7 mm, a maximum stator body outer diameter of 756.5 mm, an external terminal outer diameter of 1080.4 mm, an overall length of 820 mm, a rotor weight of 871 kg and a total weight of 2356 kg. Mean rated efficiency of the HETf is 97% under conditions as follows: the power is the rated value of 750 kW, the rotation speed of the half-coupled member HETfhe is the rated value of 1500 r/min, the rotation speed of the half-coupled member HETfhf is a whole-process rotation speed from the ⅓ of the rated rotation speed to 100% of the rated rotation speed (whole process of corresponding flywheels from ⅓ of the rated rotation speed and 1/9 of stored energy to the 100% of the rated rotation speed and 100% of stored energy).

(276) The HETf is connected to a generator rotation shaft end that faces the wind wheel side. Connection of various devices between the speed-up gear box and the generator is as follows: a coupling is connected with the gear box output shaft and a front half-coupled member end shaft of the HETw, a set of external cable is connected with a main current circuit of the two half-coupled member of the HETw, a coupling is connected with a rear half-coupled member end shaft of the HETw and a front end shaft of the horizontal half-coupled member HETfhe, and a coupling is connected with a rear end shaft of the horizontal half-coupled member HETfhe and the generator rotation shaft. The HETfhe rotation shaft has an effect of transferring power to the rear generator rotation shaft. A rated value of the power transferred at the front end of the rotation shaft is 1563 kW, and a rated value of the power transferred at the rear end of the rotation shaft is 782 kW.

(277) Main parameters of the suspended flexible flywheel device (FIG. 64) include: a rated rotation speed of 3796.25 r/min, a rated transmission power of 750 kW (power halved design), a maximum transmission torque of 5660 Nm (capable of transmitting the rated power of 750 kW under the ⅓ of the rated rotation speed and higher), a maximum flywheel outer diameter of 3360 mm, a maximum device outer diameter of 3727 mm, a total device height of 4675 mm, an overall device weight of 51581 kg, a total rotor weight of 42837 kg and rated stored energy of 1567 kWh.

(278) Embodiments of the suspended flexible flywheel device (FIG. 64) are as follows.

(279) Flywheel rotors have 7 sets of upper and lower tandem wheel bodies. Each set of the wheel bodies has two mass block bodies (53) and two supporting bodies (54) (FIG. 59). Each set of the wheel bodies is connected with a section of cylindrical center shaft (102). Upper and lower adjacent center shafts are connected by virtue of flanges and threaded fasteners. 6 sections of center shafts located on the lower side have the same structure. One section of center shaft on the uppermost side has a flange plate (FIG. 59) connected with a flange plate (131) at the lower end of a circular chain. During installation and assembly, one set of wheel bodies at the bottommost end and the center shaft assembly are supported and installed from the bottom, and the rest wheel bodies and center shaft assemblies are assembled and connected one by one from bottom to top.

(280) The mass block body on the outer ring is made of high-strength glass fiber roving reinforced epoxy resin subjected to filament winding. The mass block body on the inner ring is made of E-type glass fiber roving reinforced epoxy resin subjected to filament winding. Each of the supporting bodies is made of E-type glass fiber roving reinforced unsaturated polyester resin subjected to filament winding. The cylindrical center shaft is made of nodular cast iron.

(281) A bearing end surface pair (56) is adopted between the mass block body on the outer ring and the mass block body on the inner ring. A bearing end surface pair (56) and an upward displacement-limiting end surface pair (64) are adopted between the mass block body on the inner ring and the supporting body on the outer ring, between the supporting body on the outer ring and the supporting body on the inner ring and between the supporting body on the inner ring and the cylindrical center shaft. The two end surface pairs are designed in a centralized manner. Two opposite end surfaces of the bearing end surface pair (56) remain a margin on a radial height so as to compensate radial displacement dislocation generated during rotation, so that the end surface pairs always keep an effective action area in a range from a static state to the maximal rotation speed. In order to achieve the purposes of increasing wear resistance of a contact surface of the end surface pairs, increasing an effective contact area, protecting a fiber reinforced plastic surface, realizing reliability, durability, vibration absorption and the like, the two opposite end surfaces of the end surface pairs (56) are made of polyurethane rubber. An end-surface thin plate (65) and an end-surface thick block (66) made of the polyurethane rubber material are adhered with a matrix together. The end-face thick block (66) has high elasticity and deformation adaptability, but high centrifugal load, and is installed on an outer ring matrix. The centrifugal load is borne by an inner hole surface of the matrix. Since a load of the bearing end surface pair (56) is higher, the selected matrix adhered and a main body of a wheel body structure are made into an integral structure, thereby ensuring that a load transfer path has full strength reserve. However, a matrix at one end of the non-bearing end surface pair (57) adopts an accessory structure, and the accessory is fixedly connected with a main matrix by virtue of an adhesive and is made of a material identical to that of the main matrix.

(282) A single flexible membrane ring (58) is respectively arranged between the mass block on the outer ring and the mass block on the inner ring, between the mass block on the inner ring and the supporting body on the outer ring, between the supporting body on the outer ring and the supporting body on the inner ring and between the supporting body on the inner ring and the cylindrical center shaft. Each of the flexible membrane rings is adhered to the accessory structure, and then the accessory structure is adhered to the main matrix. The accessory is made of the same material as the main matrix. The flexible membrane ring adopts a polyurethane rubber material. A free state of film ring parts before installation is of a uniform thickness flat washer shape. During installation, the film ring is forced to deform into a shape bending to one side surface, and a film ring farther away from the center shaft has a larger bending degree. The film ring is basically straightened while rotating at the maximum rotation speed. The flexible membrane ring is circumferentially stretched during installation, and an inner hole diameter of the film ring is increased to a fit dimension.

(283) A pulling torque transfer flexible transmission part between the flywheel rotation shaft (101) and the wheel body center shaft (102) adopts a circular chain (FIG. 49). A half circular ring (FIG. 46) with a flange plate is respectively adopted at each of upper and lower ends of the circular chain, and a circular ring with a horizontal connecting beam (FIG. 48) is adopted in the middle of the chain. Fastened “hole shafts” of the two rings are in close fit, and a radius of the hole is 70 mm and only slightly larger than a radius 69.6 mm of the shaft, thereby decreasing bearing stress. Nodular cast iron casting and processing is adopted, two end semicircular rings (FIG. 46) are cast and processed, and casting of an intermediate circular ring and subsequent processing may be performed under a condition in which the two end semicircular rings are joined.

(284) A flange structure (FIG. 58, FIG. 59) is adopted for connection between the upper end of the center shaft and the lower end of the circular chain.

(285) A spline, thread and flange connecting structure shown in FIG. 55 is adopted for connection between the lower shaft end of the rotation shaft and the upper end of the circular chain. An internal spline of a connecting piece (127) and an external spline of the lower shaft end of the rotation shaft (101) are in matched connection to transfer the torque. An external flange plate of the connecting piece (127) is matched with an external flange plate (129) at an upper end of the circular chain through a seam allowance and fastened by a bolt. A nut (128) is fastened at a tail end of the rotation shaft and bears gravity transferred by the connecting piece (127). A ring groove structure of the nut (128) is favorable for thread load uniformity.

(286) Axial supporting permanent magnetic bearings are composed of 5 serial force attraction type axial supporting permanent magnetic bearings. Each bearing has a rotary disc (59) and a stationary disc (60) (FIG. 61 and FIG. 63). The rotary disc is located below the stationary disc. A clearance is formed between end surfaces on adjacent sides of the two discs. The rotary discs adopt 5 soft magnetic material 45# steel cone discs with the same size structure. Each of the rotary discs is fastened with the rotation shaft (101) by virtue of an adapter sleeve (147) (with an outer conical surface and an inner cylindrical surface, with a gap formed in a longitudinal direction) and a nut (146). An intermediate spacer bush (148) is arranged between two adjacent rotary discs. A spacer bush (152) is arranged between the rotary disc at the uppermost end and a shoulder on the spindle. These spacer bushes achieve the effects of axially positioning and ensuring reliable axial transfer force. The stationary discs (FIG. 65) are composed of axisymmetric non-magnetic material aluminum alloy matrixes (151), soft magnetic material electromagnetic pure iron rings (149) and permanent magnet material Nd—Fe—B rings (150), and the three kinds of materials are connected by adhesives. The Nd—Fe—B rings (150) are magnetized along a radial direction. Adjacent Nd—Fe—B rings have opposite magnetizing directions. Main magnetic flux circuits pass through the Nd—Fe—B rings, two adjacent electromagnetic pure iron rings and opposite rotary discs thereof. A strong air-gap field is generated between the electromagnetic pure iron rings and the rotary discs, and upward magnetic attraction is formed relative to the rotary discs and designed to be used for offsetting gravity of the rotors. Connecting structures of the stationary discs (60) and other members and assembling steps are as follows: after the bearing block and adjacent parts thereof at the upper end of the rotation shaft and a steel bearing block (153) are assembled, installing the stationary disc at the uppermost end and an upper-end steel bushing (154); installing the rotary disc (59) at the uppermost end, the spacer bush (152), the adapter sleeve (147), the nut (146) and locking accessories thereof; installing the stationary disc in the middle, a rubber elastic cushion cover (155) and an intermediate steel bushing as well as the rotary disc in the middle, the intermediate spacer bush (148), the adapter sleeve (147), the nut (146) and locking accessories thereof one by one according to a sequence of installing stationary members and rotary members in sequence; and finally, installing the stationary disc at the bottommost end, the rubber elastic cushion cover (155) and a lower-end steel bushing (157), and finally accommodating and sleeving various sections of serial steel bushings (154, 156 and 157) by virtue of a through-long outer steel bushing (139).

(287) Radial rolling bearing supports are adopted at the upper and lower ends of the rotation shaft (101). The rotary discs of the axial supporting permanent magnetic bearings are positioned in the middle of the rotation shaft. The rotation shaft is designed as a rigid rotor, and a first-order bending critical rotation speed of the rotor is higher than the rated rotation speed.

(288) A deep groove ball bearing (FIG. 61) is adopted at the lower end of the rotation shaft, and lubricating grease is used. Magnetic fluid sealing components (Nd—Fe—B rings and electromagnetic pure iron rings with three teeth respectively on two sides thereof, as well as magnetic fluid at tooth tips) are arranged on both sides of the bearing, so that the bearing is isolated from a surrounding vacuum environment, and a bearing chamber is communicated with atmosphere. Centrifugal isolating discs (159) that prevent the lubricating grease from moving to both sides are arranged on the two sides of the bearing. Spacer bushes (160, 161) are installed on the rotation shaft at positions relative to the magnetic fluid sealing components. The spacer bushes are made of 45# steel of which magnetic conductivity is higher than that of the material of the rotation shaft, thereby ensuring sealed magnetic flux. Meanwhile, the spacer bushes have axial positioning effects of related parts. Rubber sealing rings and vacuum sealing grease are arranged between the spacer bushes (160, 161) and the rotation shaft (101). The spacer bush (160) and the rotation shaft may also be fixedly connected and sealed by a brazing method. The two sets of upper and lower magnetic fluid sealing components are respectively fixed on the bearing block (140) and the end cover (158), connection surfaces are adhered and sealed by adhesives, the end cover and the bearing block are fastened by screws, and rubber sealing rings and vacuum sealing grease are arranged. The bearing block (140), the end cover (158) and the centrifugal isolating discs (159) are made of non-magnetic material aluminium alloys, thereby meeting magnetic fluid sealing requirements.

(289) The deep groove ball bearing (FIG. 61) at the lower end of the rotation shaft is a free end bearing in a non-axial positioning manner. An axial free displacement of an outer ring of the bearing should be ensured. In addition, a load of the bearing should not be lower than the minimum load, so as to avoid severe sliding friction. In order to meet the above two requirements, structure measures are taken as follows: the bearing block (140) is contacted with an upper end surface of the outer ring of the bearing, an outer cylindrical surface of the bearing block allows the axial free displacement, an axial load formed by total weight of the bearing block, the end cover (158), the two sets of magnetic fluid sealing components and the outer ring of the bearing acts on a bearing ball. An equivalent load of the bearing generated by the axial load is not lower than the required minimum load.

(290) The bearing at the lower end of the rotation shaft adopts the solution (FIG. 61) transferring force to the support by virtue of the outer steel bushing (139). The outer cylindrical surface of the bearing block (140) is directly contacted with an inner cylindrical hole of the outer steel bushing. In order to ensure coaxiality of bearing block holes in the upper and lower ends, the related parts (139, 153 and 154) including the outer steel bushing are combined and machined with upper and lower end seat holes.

(291) A pair of deep groove ball bearings (FIG. 63) is adopted at the upper end of the rotation shaft. A space ring is arranged between inner rings of the two bearings. A supporting space ring with more than ten circumferentially and uniformly distributed axial through holes and built-in spiral compression springs thereof is respectively arranged above an upper end surface of an outer ring of the upper bearing and below a lower end surface of an outer ring of the lower bearing, so that a face-to-face bearing combination is formed by the two bearings. The two bearings bear the radial load and the bidirectional axial load and serve as axial positioning ends. The more than ten built-in spiral compression springs in the supporting space ring are used for ensuring that the equivalent load of each of the bearings is not lower than the required minimum load. The supporting space ring at the lower end is limited and supported by an aluminium-alloy end base (162). The supporting space ring at the upper end is limited and supported by an aluminium-alloy end cover (165). The aluminium-alloy end base (162) and the steel bearing block (153) are positioned by a seam allowance and fixed and sealed by brazing. An adjusting washer is arranged between the aluminium-alloy end cover (165) and the steel bearing block. During assembly, a thickness of the adjusting washer is ground according to related dimension measurement results when the bearing reaches a required pre-rightening load by virtue of a special tool. The bearings are lubricated by the lubricating grease. Centrifugal isolating discs preventing the lubricating grease from moving to the two sides are arranged on both sides of the bearing pack. A magnetic fluid sealing element with six sealing teeth is arranged on the lower side of the bearing pack, so that the bearings are isolated from a vacuum environment in which the rotors are located, and the bearing chamber is communicated with an atmospheric gas circuit. A magnetic fluid sealing element with two sealing teeth is arranged on the upper side of the bearing pack. The magnetic fluid sealing elements are respectively fixed on the aluminium-alloy end base (162) and the aluminium-alloy end cover (165), and connection surfaces are adhered and sealed by adhesives. Spacer bushes (163, 164) are installed on the rotation shaft at positions relative to the magnetic fluid sealing components. The spacer bushes are made of 45# steel of which the magnetic conductivity is higher than that of the material of the rotation shaft, thereby ensuring sealed magnetic flux. Meanwhile, the spacer bushes have axial positioning and force transferring effects of the related parts. Rubber sealing rings and vacuum sealing grease are arranged between the spacer bush (163) and the rotation shaft (101). The spacer bush (163) and the rotation shaft may also be fixedly connected and sealed by a brazing method. An upper end surface of the spacer bush (164) is fastened by a shaft-end nut. An external spline is arranged at the upper shaft end of the rotation shaft (101) and connected with a rotation shaft of peripheral equipment. An internal thread at a central hole is used in an installation process.

(292) In order to locate a center line of the flywheel rotation shaft (101) at a vertical position, installation levelness of the support plate (133) and the base (134) is adjusted by adopting a structure shown in FIG. 63, so that levelness of the installed reference plane (135) of the flywheel rotation shaft meets strict requirements. Meanwhile, related machining form and position accuracy of the bearing block (153), the outer steel bushing (139), fan-shaped cushion blocks (166) and fan-shaped adjusting base plates (167) is strictly controlled. The fan-shaped cushion blocks (166) are circumferentially and uniformly distributed and temporarily not used at the beginning of installation. After connection with the circular chain is completed at the lower end of the rotation shaft and connection between the circular chain and the flywheel bodies and the center shaft located at the bottom is completed, the whole rotor (total stator members including the bearing block (153) and the outer steel bushing (139)) is lifted by a lifting tool installed at the internal thread of the upper shaft end of the rotation shaft; or the heaviest flywheel body is jacked up at the bottom of the center shaft of the flywheel body by adopting a hydraulic jack, the total rotors are lifted and straightened, and then the fan-shaped cushion blocks (166) are installed from side surfaces. The fan-shaped adjusting base plates (167) which are circumferentially and uniformly distributed and installed from the side surfaces are used for clearances between the rotary discs and the stationary discs of the axial supporting permanent magnetic bearings, thereby adjusting the magnetic attraction. When the stationary discs and the rotary discs of the permanent magnetic bearings are assembled one by one, the stationary discs are sucked onto the rotary discs. Since limiting flanges with smaller clearances are formed in inner edges and outer edges of opposite end surfaces of the stationary discs and the rotary discs, about one half of rated air-gap distance is still remained in the air gap formed when the two discs are attracted with each other. Therefore, the magnetic attraction at the moment is not too high, and a debugging operation of the magnetic attraction is facilitated.

(293) A vacuum container shell which is fixedly installed on the base (134) is in the shape of a bottle (FIG. 64) which is fine in top and thick in bottom, and has three parts, i.e., an upper part, a middle part and a lower part. The lower part is composed of a bottom elliptical head and a lower cylindrical section, the middle part is an elliptical closing port, and the upper part is composed of a cylindrical section and the support plate (133). The bearing block (153) is also a seal head of the vacuum container. The middle part is connected with a flange arranged on a lower shell, and the upper part is connected with a flange arranged on a middle shell. An installation sequence is as follows: the lower shell, the wheel body and the center shaft assembly, the middle shell, the base (134), the upper shell and the rest parts. A brazing ring cavity wall structure is formed in an outer ring at a flange connection joint (FIG. 64, an enlarged drawing) between the middle part and the lower shell and between the upper part and the middle shell respectively. Thin-walled ring units (168, 170) at both ends are fixedly welded with a thick-walled shell. After field installation and flange connection fastening, an intermediate thin-walled ring unit (169) and the thin-walled ring units (168, 170) are welded by adopting a field soldering method, thereby ensuring a reliable vacuum seal. Meanwhile, semi-detachable seal and connection can be realized. The thin-walled units and transition structures at both ends are mainly used for preventing heat from dissipating too fast during field soldering. A brazing ring cavity wall structure (FIG. 63) accommodating total connection surfaces between the support plate (133) and the bearing block (153) is formed between the support plate (133) and the bearing block (153). Thin-walled ring units (171, 173) at both ends are fixedly welded with the bearing block and the support plate first. After thicknesses of the fan-shaped adjusting base plates (167) are determined under conditions that the container is not vacuumized and the rotors are static and fastening between the bearing block (153) and the outer steel busing is completed, an intermediate thin-walled ring unit (172) and the thin-walled ring units (171, 173) at both ends are welded by adopting the field soldering method, thereby ensuring a reliable seal of the accommodating members. Moreover, when the thicknesses of the fan-shaped adjusting base plates (167) should be further adjusted, the thin-walled ring units may be removed and reused.

(294) The two horizontal half-coupled members (FIG. 38) of the HETw with the same design and the horizontal half-coupled member HETfhe (FIG. 66) and the vertical half-coupled member HETfhf (FIG. 67) of the HETf are in single-stage, double-magnetic flux and near-axis coil forms, and adopt the mixed flexible external cables. General description of the common part of the embodiments of the three half-coupled members is the same as description explained in specific embodiments of “(f) Wind Power Generation System Including HET”.

(295) The half-coupled members (FIG. 38) of the HETw and the half-coupled member HETfhe (FIG. 66) of the HETf are of horizontal hollow-shaft structures. Intermediate sections of rotation shafts of the half-coupled members are provided with hollow 20-steel magnetic conductors (2); both ends are provided with 40Cr-steel end shafts (180, 182) and 20-steel lantern rings (181); and the lantern rings (181) are used for magnetizing the magnetic fluid sealing elements (37). Interference fitting is respectively formed between the magnetic conductors (2) and the end shafts and between the end shafts and the lantern rings, and sealants are applied to the contact end surfaces. A rolling bearing (a deep groove ball radial bearing, grease lubricating, with contact-type sealing rings on two sides) is respectively arranged on each of the end shafts. The bearing on one side of the end shaft (180) is an axial positioning end and can bear a bidirectional axial load, and the bearing on one side of the end shaft (182) is a free end capable of producing an axial displacement. An axial bearing load generated by gravity of the rotor is larger than a minimum load thereof, and additional pre-loading measures do not need to be increased for the two bearings. The half-coupled members (FIG. 38) of the HETw have a shaft extension end with an external spline. The half-coupled member HETfhe (FIG. 66) of the HETf has two shaft extension ends with external splines.

(296) The half-coupled member HETfhf (FIG. 67) of the HETf is of a vertical and solid-shaft structure. The rotation shaft (2) is composed of two parts, i.e., a central fine shaft and an outer ring annular shaft which are in interference fit. The central fine shaft is made of 45 steel. The outer-ring annular shaft is made of 20 steel. The half-coupled member HETfhf has a shaft extension end having an external spline and facing the lower side.

(297) A stator of the HETfhf (FIG. 67) is connected with the bearing block (153) (FIG. 68, FIG. 69) at the upper end of the flywheel rotation shaft by virtue of a bracket (175), i.e., a small-diameter seam allowance ring body at the upper end of the bracket (175) is connected and fastened with a seam allowance of a flange plate at the lower end of the stator of the HETfhf, and a large-diameter seam allowance ring body at the lower end of the bracket is connected and fastened with a seam allowance of a boss on an outer edge of the bearing block (153) at the upper end of the flywheel rotation shaft, so that a support of the stator of the HETfhf and the flywheel device are integrated. Due to form and position tolerance machining control of related connecting parts, the rotation shaft of the HETfhf is coincided with the axis of the flywheel rotation shaft. The bracket (175) is composed of the small-diameter seam allowance ring body at the upper end, the large-diameter seam allowance ring body at the lower end, and circumferenally and uniformly distributed rectangular-section radial spokes connecting the both ends, and is cast by nodular cast iron and manufactured by a machining process. The lower end surface of the rotation shaft of the HETfhf is pressed on the upper end surface of the flywheel rotation shaft (FIG. 68). Gravity of the rotor of the HETfhf is transferred onto the flywheel rotation shaft and borne by the axial supporting permanent magnetic bearings of the flywheels in a unified manner, so that the HETfhf is not equipped with an axial supporting bearing with an extremely high load, and also not equipped with an axial positioning dead point. External splines with the same specification and size are machined in shaft ends of the two shafts. Torque between the two shafts is transferred by an internal spline sleeve (174) (FIG. 68) assembled at the two shaft ends. A coupling between two devices (one of the devices does not have the axial positioning dead point) may not generate an extra undesired axial load to the only one axial positioning bearing during operation. However, on a general occasion that the two devices have the axial positioning dead point, an elastic coupling between the two devices may generate axial force (caused by the axial displacement, misalignment and other conditions), a rigid fixed coupling between the two devices may generate extremely high thermal expansion axial force, and a toothed coupling between the two devices may generate frictional axial force when an axial displacement between engaging teeth is caused by thermal expansion and shrinkage of the rotation shafts and other parts. The above axial force is action and reaction in a paired manner, and simultaneously transferred to the axial supporting bearings at the axial positioning end of the two devices.

(298) Only one radial rolling bearing (deep groove ball bearing) is respectively arranged at each of both ends of the rotation shaft (the central fine shaft) of the HETfhf (FIG. 67). Outer rings can generate free axial displacements. Any axial positioning bearing capable of bearing the bidirectional axial load is not arranged. Since the bearings of the vertical rotors do not bear the gravity, in order to retain the minimum load of the bearings, the spiral compression springs acting on end surfaces of the bearing outer rings are added on one side of the bearing block end cover, so as to apply the axial pre-tightening load.

(299) The suspended flexible flywheel device and the HETfhf (FIG. 69) are arranged at central positions of the tower. A center line of the flywheel rotation shaft is coincided with a yawing rotation center line. During wind wheel yawing, a flywheel gyroscoopic torque is not generated, and rotation of center of gravity of the flywheel is not caused.

(300) In the half-coupled members of the HETw and the half-coupled members HETfhe and HETfhf of the HETf, currents with the same magnitude and opposite directions (I1 and I2, FIG. 9, FIG. 10) are conducted to two magnet exciting coils (9) of each of the half-coupled members, and generated double-magnetic flux magnetic fields are bilaterally symmetrical. Windings of the two magnet exciting coils are connected in series together and have the same exciting winding current Ic1, I1=Z1×Ic1, I2=Z2×Ic1, the number of turns Z1 and Z2 are equal to each other, and total magnetic flux ΣΦ1 of the rotors of the half-coupled members is equal to Ff1(|I0|, I1, I2)=Ff1(|I0|, Z1×Ic1, Z2×Ic1).

(301) Since the two half-coupled members of the HETw have an identical design, a set of electromagnetic interaction relationship curve formula may be shared by the two half-coupled members, i.e., ΣΦ2=Ff1(|I0|, Z1×Ic2, Z2×Ic2), wherein Ic2 is exciting winding current of the second half-coupled member of the HETw.

(302) Operating control of the HETw and HETf is respectively independently executed. Each set of the HET may be controlled by selecting any one of two adjustment and control methods as follows:

(303) A first type of adjustment and control method:

(304) The total loss is a sum of main current ohmic heat (I0.Math.I0.Math.R0) and each exciting current ohmic heat (ΣPoi), wherein R0 and Ri are constant values.

(305) A relationship curve that varies along with main current I0 and exciting winding current Ic1 and Ic2 is obtained by calculation or test as follows:
ΣΦ1=Ff1(|I0|,Z11×Ic1,Z12×Ic1)  (g16)
ΣΦ2=Ff2(|I0|,Z21×Ic2,Z22×Ic2)  (g17)

(306) wherein the value of I0 ranges from zero to a designed value, and the values of Ic1 and Ic2 range from zero to a designed value, Z11 and Z12 are numbers of turns of the two magnet exciting coils of the first HET half-coupled member, and Z21 and Z22 are numbers of turns of the two magnet exciting coils of the second HET half-coupled member.

(307) An application range of an electromagnetic torque of a specified rotation shaft and an application range of rotation speeds of two shafts are given. By utilizing the electromagnetic law formulas (formulas (a1)-(a4), (a5) or (a6), and R0 is a constant value) and the above formulas (g16) and (g17), a matrix of optimum values Ic1opt and Ic2opt of exciting winding current, which fully covers different rotation speed conditions and torque demands and satisfies a total loss minimum target, is calculated, and all the data are stored in the control system.

(308) When regulation is executed, rotation speeds (ω1 and ω2) of the two rotors are acquired in real time input conditions, a torque instruction of the specified rotation shaft is given as an input condition, related stored data is invoked from the control system, and corresponding optimum values Ic1opt and Ic2opt of each exciting winding current are calculated by adopting a spline interpolating function formula for use in the execution link.

(309) A second type of adjustment and control method:

(310) The total loss is a sum of main current ohmic heat (I0.Math.I0.Math.R0), each exciting current ohmic heat (ΣPoi) and circuit “connecting region clearance” liquid metal friction heat, wherein Ri is a constant value, and R0 is a function of liquid metal state parameters MLS, a variable in the parameters MLS is a NaK liquid capacity parameter, while a liquid center position parameter is fixed as an average value. The parameters MLS may influence the liquid metal friction heat.

(311) A relationship curve that varies along with main current I0 and exciting winding current Ic1 and Ic2 is obtained by calculation or test as follows:
ΣΦ1=Ff1(|I0|,Z11×Ic1,Z12×Ic1)  (g16)
ΣΦ2=Ff2(|I0|,Z21×Ic2,Z22×Ic2)  (g17)

(312) wherein the value of I0 ranges from zero to a designed value, and the values of Ic1 and Ic2 range from zero to a designed value, Z11 and Z12 are numbers of turns of the two magnet exciting coils of the first HET half-coupled member, and Z21 and Z22 are numbers of turns of the two magnet exciting coils of the second HET half-coupled member.

(313) An application range of a torque of a specified rotation shaft, an application range of rotation speeds of two shafts and an application range of the circuit “connecting region clearance” NaK liquid capacity parameter are given. By utilizing the electromagnetic law formulas (formulas (a1)-(a4), (a5) or (a6), and R0 is a function of the NaK liquid capacity parameter) and the above formulas (g16) and (g17), a matrix of optimum values Ic1opt and Ic2opt of exciting winding current, which fully covers different rotation speed conditions and torque demands and satisfies a total loss minimum target, as well as a matrix of optimum values of the NaK liquid capacity parameter are calculated, and all the data are stored in the control system.

(314) When regulation is executed, rotation speeds (ω1 and ω2) of the two rotors are acquired in real time as input conditions, a torque instruction of the specified rotation shaft is given as an input condition, related stored data is invoked from the control system, and corresponding optimum values Ic1opt and Ic2opt of each exciting winding current, as well as the optimum value of the NaK liquid capacity parameter are calculated by adopting the spline interpolating function formula for use in the execution link.

(315) A stable power generation operating method is adopted during a normal operation of the wind power system in the present invention. The generator is operated according to planned average power generation power. When the output power of the wind wheel is higher than an average value under a strong wind condition or under gust of wind, the higher difference is absorbed by the flywheel. When the output power of the wind wheel is lower than the average value under a small wind condition, the insufficient difference is compensated and output by the flywheel.

(316) The wind power system may also realize a peak regulation function of the power grid when necessary. When the power grid needs to store energy and the wind speed is small, the generator serves as a motor, and electric energy from the power grid is absorbed by the flywheel. When the load of the power grid is increased and the wind speed is small, the stored energy is totally output by the flywheel.

(317) A process of starting the wind wheel and the generator by adopting wind power is as follows: when a start-up wind speed is reached, a pitch angle of the blades of the wind wheel ranges from a decreased angle at a “feathering” position to a pitch angle with a larger starting torque, an impeller is driven to be self-started by the wind power, the synchronous generator rotor is driven to speed up from a zero rotation speed to a synchronous rotation speed of 1500 r/min by virtue of HET transmission, and then connected to the power grid by virtue of synchronous grid-connected operating procedures; and after the starting process is completed, the blade pitch angle rotates to a rated design pitch angle, and the rotation speed of the impeller is adjusted to a rotation speed value meeting the optimal tip speed ratio of 7.

(318) The peak regulation function of the power grid is realized in the absence of wind. A process of starting the generator (motor) by adopting the flywheel is as follows: by utilizing kinetic energy of the flywheels, the synchronous generator rotor is driven to speed up from a zero rotation speed to a synchronous rotation speed of 1500 r/min by virtue of the HET transmission, and then connected to the power grid by virtue of synchronous grid-connected operating procedures. Thus, the synchronous motor is operated according to the planned power generation conditions, or operated in an electric working condition. When the flywheel is in a zero rotation speed state and does not have the kinetic energy, the synchronous motor is started under no-load by adopting an own starting winding, and then operated in the electric working condition.

(319) A conventional operating control solution in a range from a cut-in wind speed to a rated wind speed is as follows: the wind wheel blades maintain a control objective that the design pitch angle linearly changes along with a direct wind speed ratio according to the wind wheel rotation speed (that is, a ratio of the tip linear speed to the wind speed is equal to 7), a local mean wind speed (outside the cabin), the wind wheel rotation speed, the generator rotation speed and the flywheel rotation speed are measured in real time, a proportional relation between the wind wheel torque and second power of the wind speed is taken as a mater control rule, an instruction for the torque Mew1 of the rotation shaft of the wind-wheel-side half-coupled member of the HETw is given, a stable operation of the generator according to the planned mean power generation power is taken as an energy allocation principle, and an instruction for the torque Mefhe (positive or negative) of the rotation shaft of the half-coupled member HETfhe is given, so that operations of the HETw and HETf and power transfer thereof are adjusted and controlled. When the rotation speed of the wind wheel is lower than a constant value of a target rotation speed, the Mew1 instruction is appropriately decreased (the instruction Mefhe is correspondingly changed), so as to lighten an output load of the wind wheel, thereby speeding up the wind wheel. When the rotation speed of the wind wheel is higher than the constant value of the target rotation speed, the Mew1 instruction is appropriately increased (the instruction Mefhe is correspondingly changed), so as to increase the output load of the wind wheel, thereby reducing the speed of the wind wheel.

(320) A power limitation control solution in a range from the rated wind speed to the cut-in wind speed is as follows: by taking measures that the variable pitch angle changes towards aspects of decreasing a stall trend, decreasing an airflow angle of attack and increasing the pitch angle of the blades, the power and the impeller rotation speed are kept constant in principle (equal to the rated value), that is, the wind-power utilization coefficient Cp of the impeller and third power of the wind speed are in inversely proportional change, and a tip speed ratio λ and the wind speed are in inversely proportional change. A moving track that the value Cp and third power of the λ are proportional is shown in a Cp-λ diagram, and is a steep curve. An intersection set of a set of curves and the steep curve is solved by utilizing a set of Cp-λ curves under different pitch angles in an adjustable pitch angle range, and a corresponding law that the pitch angle changes along the wind speed is determined from the intersection set. The local mean wind speed, the wind wheel rotation speed, the generator rotation speed and the flywheel rotation speed are measured in real time, the pitch angle is adjusted according to the corresponding law, a torque Mew1 instruction for the rotation shaft of the wind-wheel-side half-coupled member of the HETw is given according to a master control rule that the wind wheel torque is equal to a rated torque, and a torque Mefhe instruction for the rotation shaft of the HETfhe half-coupled member is given by taking the stable operation of the generator according to the planned mean power generation power as the energy allocation principle, so that operations of the HETw and HETf and power transfer thereof are adjusted and controlled. When the rotation speed of the wind wheel is lower than a constant value of a rated rotation speed, the Mew1 instruction is appropriately decreased (the instruction Mefhe is correspondingly changed), so as to lighten the output load of the wind wheel, thereby speeding up the wind wheel. When the rotation speed of the wind wheel is higher than the constant value of the rated rotation speed, the Mew1 instruction is appropriately increased (the instruction Mefhe is correspondingly changed), so as to increase the output load of the wind wheel, thereby reducing the speed of the wind wheel.

(321) An impeller brake and stop process is as follows: when the cut-out wind speed is reached, or other braking instructions are transmitted, the pitch angle of the wind wheel blades is rotated to the “feathering” position, aerodynamic braking is implemented, and mechanical braking of a brake disc arranged at the wind wheel shaft is performed until the wind wheel stops rotating.

(322) (h) Flywheel Energy Storage and Conversion System Including HET

(323) A specific embodiment of the flywheel energy storage and conversion system (FIG. 76) for peak regulation of the power grid is as follows.

(324) The system includes: a suspended flexible flywheel device (176) (FIG. 71), a flywheel-side vertical separated HET half-coupled member (177) (FIG. 73), a motor-side horizontal separated HET half-coupled member (178) (FIG. 72), and a horizontal synchronous motor/generator (179).

(325) The horizontal synchronous motor/generator includes parameters: a rated power generation power of 12 MW, a rotation speed of 3000 r/min, rated capacity of 15 MVA, a rated voltage of 6.3 kV and a total weight of 31.7 tonnages, and adopts an indirect air cooling manner. When the flywheel has energy, a method for driving the motor to the rated rotation speed by the flywheels and HET is preferably adopted for starting the motor.

(326) Main parameters of the suspended flexible flywheel device (FIG. 71) include: a rated rotation speed of 1321.9 r/min, a rated transmission power of 12.8 MW, a maximum transmission torque of 277398 Nm (capable of transmitting the rated power of 12.8 MW under the ⅓ of the rated rotation speed and higher), a maximum flywheel outer diameter of 9648 mm, a maximum device outer diameter of 10697 mm, a total device height of 15894 mm, an overall device weight of 1414587 kg, a total rotor weight of 1181437 kg and rated stored energy of 38465 kWh.

(327) Embodiments of the suspended flexible flywheel device (FIG. 71) are as follows.

(328) Only parts different from the suspended flexible flywheel device (FIG. 64) in the embodiment of “(g) Wind Power Generation System Including HET and Flywheels” are described herein. The same part can be seen in detail above.

(329) Flywheel rotors have 15 sets of upper and lower series wheel bodies. Each set of the wheel bodies has two mass block bodies (53) and two supporting bodies (54) (FIG. 70). Each set of the wheel bodies is connected with a section of cylindrical center shaft (102). Upper and lower adjacent center shafts are connected by virtue of flanges and threaded fasteners. 14 sections of center shafts located on the lower side have the same structure. One section of center shaft on the uppermost side has a flange plate (FIG. 70) connected with the flange plate (131) at the lower end of a circular chain. During installation and assembly, one set of wheel bodies at the bottommost end and the center shaft assembly are supported and installed from the bottom, and the rest wheel bodies and center shaft assemblies are assembled and connected one by one from bottom to top. Fasteners connected with the 14 sections of center shafts with the same structure are double-end studs and nuts. The studs pass through a temporarily-unused through hole space when assembled in place.

(330) A pulling torque transfer flexible transmission part between the flywheel rotation shaft (101) and the wheel body center shaft (102) is a circular chain (FIG. 8). Fastened “hole shafts” of the two rings are in close fit, and a radius of the hole is 201 mm and only slightly larger than a radius 200 mm of the shaft, thereby decreasing bearing stress.

(331) Axial supporting permanent magnetic bearings are composed of 12 serial force attraction type axial supporting permanent magnetic bearings. Rotary discs adopt 12 soft magnetic material 45# steel cone discs with the same size structure.

(332) A vacuum container shell which is fixedly installed on the base (134) is in the shape of a bottle (FIG. 71) which is fine in top and thick in bottom. The vacuum container shell is located in a deep pit under the ground.

(333) Main parameters of the motor-side horizontal separated HET half-coupled member (FIG. 72) include: a rated rotation speed of 3000 r/min, a rated power of 12.3 MW, a rated torque of 39097 Nm, rated main current of 429558 A, a rotor outer diameter of 730 mm, a stator body outer diameter of 1117 mm, a maximum outer diameter (external terminal outer diameter) of 1720 mm, an overall length of 1217.6 mm, a rotor weight of 1561 kg and a total weight of 5498 kg (not including aluminum cables). The motor-side horizontal separated HET half-coupled member adopts the double-magnetic flux, near-axis coil, solid-shaft, axial plane type and single-stage structural form.

(334) Main parameters of the flywheel-side vertical separated HET half-coupled member (FIG. 73) include: a rated rotation speed of 1321.9 r/min, a rated power of 12.8 MW, a design power of 3×12.8 MW (capable of reaching the rated power of 12.8 MW at the ⅓ of the rated rotation speed), a maximum torque of 277398 Nm, rated main current of 429558 A, a rotor outer diameter of 1373.7 mm, a stator body outer diameter of 2193.2 mm, a maximum outer diameter (external terminal outer diameter) of 2818.9 mm, an overall length (height) of 3212 mm, a rotor weight of 18245 kg and a total weight of 68199 kg (not including aluminum cables). The flywheel-side vertical separated HET half-coupled member adopts the double-magnetic flux, near-axis coil, solid-shaft, axial plane type and two-stage external series structural form.

(335) Embodiments of the motor-side horizontal separated HET half-coupled member (FIG. 72) are as follows.

(336) Only parts with different characteristics from the embodiments of “(a) Homopolar DC Electromagnetic Transmission (HET)” are described herein. The parts with the same characteristic can be seen in detail above.

(337) Connection of main current circuits with the flywheel-side vertical separated HET half-coupled member (177) adopts solutions of external terminals (16) and mixed flexible cables (FIG. 39). The mixed flexible cables adopt circular flexible wire bundles (91) which are made of red copper wire materials with a wire diameter of a fraction of a millimeter and composed of fine wires. The mixed flexible cables are connected to the external terminals. The wire bundles in the same current direction are arranged in a row. Various rows of the wire bundles in different current directions are alternatively arranged into fan-shaped blocks. Eight fan-shaped blocks are circumferentially and uniformly distributed. Spaces through which other pipelines and leads pass are reserved among the fan-shaped blocks. The wire bundles and red copper external terminals are in brazed connection, or red copper intermediate transition terminals are in brazed connection with the wire bundles and the red copper external terminals.

(338) Embodiments of the flywheel-side vertical separated HET half-coupled member (FIG. 73) are as follows.

(339) The flywheel-side vertical separated HET half-coupled member and the motor-side horizontal separated HET half-coupled member (FIG. 72) have most of the same structural details. The latter is described above. Only main differences are described below.

(340) The flywheel-side vertical separated HET half-coupled member has a series two-stage structure. The series two-stage structure is basically formed in combining single-stage structures shown in FIG. 72 in series. Four magnet exciting coils (9) of the two single-stage structures are reduced to three magnet exciting coils (9) (corresponding to exciting current I1, I2 and I3 in FIG. 32 and FIG. 73), i.e., two coils at intermediate positions of the original four magnet exciting coils with consistent exciting current directions are merged into a coil (13), original two main magnetic circuits are merged into a main magnetic circuit, and original two stator magnetic conductors (10) are canceled. Coils at both ends with exciting current of I1 and I2 have the same structure and number of turns. Since the magnetic circuit structures are symmetrical, magnetic flux passing through rotor magnetic and electric conductors generated when I1 and I2 are equal to each other also has the same size. An intermediate coil with exciting current of the I3 has a large number of turns. The arranged number of turns ensures that magnetic flux generated by the rated value of I3 is the same as magnetic flux generated by rated values of the I1 and I2, that is, an effect of combining the two single-stage structures is achieved. In an actual application, wires of the three magnet exciting coils are connected in series, the I1 and the I2 are always equal to each other and have the same direction, the I3 and the I1 have opposite directions, and a ratio of numerical values of the I3 and the I1 is always equal to a ratio of the number of turns thereof, that is, the three magnet exciting coils have the same exciting winding current Ic2, I1=Z1×Ic2, 12=Z2×Ic2, 13=Z3×Ic2, the numbers of turns Z1 and Z2 are equal to each other, and the total magnetic flux of the rotors ΣΦ2 is equal to Ff2(|I0|, I1, I2, I3)=Ff2(|I0|, Z1×Ic2, Z2×Ic2, Z3×Ic2).

(341) Connection of main current circuits with the motor-side horizontal separated HET half-coupled member (178) and connection of main current circuits between two stages of the half-coupled member adopt solutions of external terminals (16) and mixed flexible cables (FIG. 74). The mixed flexible cables are connected between the two-stage external terminals according to the solution shown in FIG. 74, and lead to the external terminals of the motor-side horizontal separated HET half-coupled member (178). The wire bundles (91) in the same path and the same current direction are arranged in a row. Various rows of the wire bundles (91) in different paths and different current directions are alternatively arranged into fan-shaped blocks. Eight fan-shaped blocks are circumferentially and uniformly distributed. Spaces through which other pipelines and leads pass are reserved among the fan-shaped blocks. The wire bundles (91) and red copper external terminals are in brazed connection, or red copper intermediate transition terminals are in brazed connection with the wire bundles and the red copper external terminals. Numbers of the wire bundles (91) connected with the external terminals of the flywheel-side and motor-side HET half-coupled members are the same, but distribution shapes of the wire bundles are different. The number of the wire bundles (91) in radial distribution connected to the external terminals of the flywheel-side HET half-coupled member is smaller, while the number of the wire bundles (91) in circumferential distribution is larger, thereby adapting to larger outer diameters of the external terminals of the half-coupled member.

(342) A stator of the flywheel-side vertical separated HET half-coupled member is connected with the bearing block (153) (FIG. 73, FIG. 75 and FIG. 76) at the upper end of the flywheel rotation shaft by virtue of a bracket (175), that is, a small-diameter seam allowance ring body at the upper end of the bracket (175) is connected and fastened with a seam allowance of a flange plate at the lower end of the stator of the HET half-coupled member, and a large-diameter seam allowance ring body at the lower end of the bracket is connected and fastened with a seam allowance of a boss on an outer edge of the bearing block (153) at the upper end of the flywheel rotation shaft, so that a support of the stator of the HETfhf and the flywheel device are integrated. Due to form and position tolerance machining control of related connecting parts, the rotation shaft of the HET half-coupled member is coincided with the axis of the flywheel rotation shaft. The bracket (175) is composed of the small-diameter seam allowance ring body at the upper end, the large-diameter seam allowance ring body at the lower end, and circumferenally and uniformly distributed rectangular-section radial spokes connecting the both ends, and is cast by nodular cast iron and manufactured by a machining process. The lower end surface of the rotation shaft of the HET half-coupled member is pressed on the upper end surface of the flywheel rotation shaft (FIG. 75). Gravity of the rotor of the HET half-coupled member is transferred onto the flywheel rotation shaft and borne by the axial supporting permanent magnetic bearings of the flywheels in a unified manner, so that the HET half-coupled member is not equipped an axial supporting bearing with an extremely high load, and also not equipped with an axial positioning dead point. External splines with the same specification and size are machined in shaft ends of the two shafts. Torque between the two shafts is transferred by an internal spline sleeve (174) (FIG. 75) assembled at the two shaft ends. A coupling between two devices (one of the devices does not have the axial positioning dead point) may not generate an extra undesired axial load to the only one axial positioning bearing during operation. However, on a general occasion that the two devices have the axial positioning dead point, an elastic coupling between the two devices may generate axial force (caused by the axial displacement, misalignment and other conditions), a rigid fixed coupling between the two devices may generate extremely high thermal expansion axial force, and a toothed coupling between the two devices may generate frictional axial force when an axial displacement between engaging teeth is caused by thermal expansion and shrinkage of the rotation shafts and other parts. The above axial force is action and reaction in a paired manner, and simultaneously transferred to the axial supporting bearings at the axial positioning end of the two devices.

(343) Only one radial rolling bearing (deep groove ball bearing) is respectively arranged at each of both ends of the rotation shaft (the central fine shaft) of the flywheel-side vertical separated HET half-coupled member. Outer rings can generate free axial displacements. Any axial positioning bearing capable of bearing the bidirectional axial load is not arranged. Since the bearings of the vertical rotors do not bear the gravity, in order to retain the minimum load of the bearings, the spiral compression springs acting on end surfaces of the bearing outer rings are added on one side of the bearing block end cover, so as to apply the axial pre-tightening load

(344) When operating control of the HET is executed, any one of two adjustment and control methods may be selected as follows:

(345) A first type of adjustment and control method:

(346) The total loss is a sum of main current ohmic heat (I0.Math.I0.Math.R0) and each exciting current ohmic heat (ΣPoi), wherein R0 and Ri are constant values.

(347) A relationship curve changing along with main current I0 and exciting winding current Ic1 and Ic2 is obtained by calculation or test as follows:
ΣΦ1=Ff1(|I0|,Z11×Ic1,Z12×Ic1)  (h1)
ΣΦ2=Ff2(|I0|,Z21×Ic2,Z22×Ic2,Z23×Ic2)  (h2)

(348) wherein the value of I0 ranges from zero to a designed value, the values of Ic1 and Ic2 range from zero to a designed value, Z11 and Z12 are numbers of turns of the two magnet exciting coils of the motor-side HET half-coupled member, and Z21, Z22 and Z23 are numbers of turns of the three magnet exciting coils of the flywheel-side HET half-coupled member.

(349) An application range of an electromagnetic torque of a specified rotation shaft and an application range of rotation speeds of two shafts are given. By utilizing the electromagnetic law formulas (formulas (a1)-(a4), (a5) or (a6), and R0 is a constant value) and the above formulas (h1) and (h2), a matrix of optimum values Ic1opt and Ic2opt of exciting winding current, which fully covers different rotation speed conditions and torque demands and satisfies a total loss minimum target, is calculated, and all the data are stored in the control system.

(350) When regulation is executed, rotation speeds (ω1 and ω2) of the two rotors are acquired in real time as input conditions, a torque instruction of the specified rotation shaft is given as an input condition, related stored data is invoked from the control system, and corresponding optimum values Ic1opt and Ic2opt of each exciting winding current are calculated by adopting a spline interpolating function formula to be used in execution.

(351) A second type of adjustment and control method:

(352) The total loss is a sum of main current ohmic heat (I0.Math.I0.Math.R0), each exciting current ohmic heat (ΣPoi) and circuit “connecting region clearance” liquid metal friction heat, wherein Ri is a constant value, and R0 is a function of liquid metal state parameters MLS, a variable in the parameters MLS is a NaK liquid capacity parameter, while a liquid center position parameter is fixed as a mean. The parameters MLS may influence the liquid metal friction heat.

(353) A relationship curve that varies along with main current I0 and exciting winding current Ic1 and Ic2 is obtained by calculation or test as follows:
ΣΦ1=Ff1(|I0|,Z11×Ic1,Z12×Ic1)  (h1)
ΣΦ2=Ff2(|I0|,Z21×Ic2,Z22×Ic2,Z23×Ic2)  (h2)

(354) wherein the value of I0 ranges from zero to a designed value, the values of Ic1 and Ic2 range from zero to a designed value, Z11 and Z12 are numbers of turns of the two magnet exciting coils of the motor-side HET half-coupled member, and Z21, Z22 and Z23 are numbers of turns of the three magnet exciting coils of the flywheel-side HET half-coupled member.

(355) An application range of a torque of a specified rotation shaft, an application range of rotation speeds of two shafts and an application range of the circuit “connecting region clearance” NaK liquid capacity parameter are given. By utilizing the electromagnetic law formulas (formulas (a1)-(a4), (a5) or (a6), and R0 is a function of the NaK liquid capacity parameter) and the above formulas (h1) and (h2), a matrix of optimum values Ic1opt and Ic2opt of exciting winding current that fully cover different rotation speed conditions and torque demands and satisfies a total loss minimum target, as well as a matrix of optimum values of the NaK liquid capacity parameter are calculated, and all the data are stored in the control system.

(356) When regulation is executed, rotation speeds (ω1 and ω2) of the two rotors are acquired in real time as input conditions, a torque instruction of the specified rotation shaft is given as an input condition, related stored data is invoked from the control system, and corresponding optimum values Ic1opt and Ic2opt of each exciting winding current, as well as the optimum value of the NaK liquid capacity parameter are calculated by adopting the spline interpolating function formula for use in the execution link. [amended according to detailed rule 26 22.12.2015]

LIST OF REFERENCE NUMERALS

(357) I0: marked main current, I0_1, I0_2: marked current of a parallel circuit on a main current circuit. I1, I2, . . . : current of each of DC magnet exciting coils. Φ: magnetic flux of a main magnetic circuit; Φ1, Φ2, Φ3, etc.: magnetix flux of each of main magnetic circuits. ω, ω1, ω2 and arrows: angular velocity vectors of HET rotor, HET rotor 1 and HET rotor 2. 1: central axis of HET rotation shaft. 2: HET rotation shaft. 3: rotor magnetic conductor. 4: rotor electric conductor. 5: dynamic/static circuit connecting medium (“connecting region clearance”) 6: stator electric conductor (independent), 6a, 6b, 6c, 6d: 4 split bodies of conductors (6) sleeved in sequence. 7: stator magnetic and electric conductors. 8: stator intermediate electric conductor. 9: DC magnet exciting coil. 10: stator magnetic conductor. 11: stator electric conductor (shared). 12: stator magnetic conductor. 13: permanent magnet. 14: rotor magnetic conductor. 15: liquid metal transfer switch (liquid metal filled end-surface gaps). 16: stator outer electric conductor (external terminal). 17: stator magnetic and electric conductor. 18: stator magnetic and electric conductor. 19: rotor electric conductor. 20: stator magnetic conductor. 21: stator magnetic conductor. 22: main magnetic circuit. 23: main current circuit. 25: branch clearance (located in liquid metal outlet channel). 26: second branch clearance (located in liquid metal inlet channel). 27: uniform-delivery buffer region clearance (located in liquid metal outlet channel). 28: round pipe (located in liquid metal outlet channel). 29: uniform-delivery buffer region clearance (located in liquid metal inlet channel). 30: round pipe (located in liquid metal inlet channel). 31: thermal insulating clearance for gas. 32: groove (sealed rubber tube (33) located therein). 33: sealing hose. 34: ventilating pipe (communicated with sealed rubber tube (33)). 35: vent hole. 36: supporting end cover. 37: magnetic fluid sealing element. 38: small hole (transporting metal liquid). 39: elastic taper washer. 40: spindle for coaxial external conductor. 41: pipe wall for coaxial external conductor. 42: sealing ring for coaxial external conductor. 43: sealing ring for coaxial external conductor. 44: small hole (transporting metal liquid). 51: flywheel rotation shaft. 52: flywheel vacuum container shell. 53: mass block for flywheel body. 54: support body for flywheel body. 55: flexible membrane ring for flywheel body (without pre-bending deformation in an installation state). 56: bearing end surface pair for flywheel body. 57: upward displacement-limiting end surface pair for flywheel body (a gap does not exist between two opposite end surfaces). 58: flexible membrane ring for flywheel body (with pre-bending deformation in an installation state). 59: rotary disc for axial permanent magnet attraction bearings for flywheels. 60: stationary disc for axial permanent magnet attraction bearings for flywheels (independent). 61: stationary disc for axial permanent magnet attraction bearings for flywheels (installed on vacuum container shell). 62: support disc for flywheel body. 63: elastic material ring (connecting support disc and supporting body). 64: upward displacement-limiting end surface pair for flywheel body (a gap exists between two opposite end surfaces). 65: rubber end surface thin plate for flywheel end surface pair. 66: rubber end surface thick block for flywheel end surface pair. 67: flange for flywheel vacuum container shell. 68: protective sleeve in flywheel vacuum container. 69: loading disc at lower end of flywheel rotation shaft (used for mechanical direct connection load). 71: vertical axis type flexible flywheel device on vehicle chassis. 72: HET half-coupled member on vehicle chassis. 73: vehicle frame. 74: ear flange for flywheel vacuum container shell. 75: flywheel supporting assembly on vehicle chassis. 76: fuel engine on vehicle chassis. 77: three-stage speed ratio gear reducer on vehicle chassis. 80: hydraulic connecting disc for mechanical load joint of flywheels for vehicle. 81: spline disc for mechanical load joint of flywheels for vehicle. 82: special-shaped rubber ring on hydraulic connecting disc. 83: hydraulic circuit on hydraulic connecting disc. 84: axis through hole on load rotation shaft. 85: annular groove on outer cylindrical surface of loading disc. 86: vent hole on loading disc. 87: cylindrical pin. 88: screw. 89: guide sleeve. 90: guide sleeve ring. 91: flexible wire bundle. 92: support ring plate. 101: flywheel rotation shaft. 102: flywheel body center shaft. 103: intersected cross shaft of universal joints. 104: yoke hole members of intersected cross shaft of universal joints. 105: roller pin for universal joint revolute pair. 106: bearing inner race for universal joint revolute pair. 107: bearing steel bowl for universal joint revolute pair. 108: center top rubber ball for universal joint revolute pair. 109: snap ring for universal joint revolute pair. 110: sealing sleeve for universal joint revolute pair. 111: nut for universal joint revolute pair. 112: spherical outer ring for universal joint revolute pair. 113: spherical inner ring for universal joint revolute pair. 114: rubber ring for universal joint revolute pair. 115: aluminum sheath for universal joint revolute pair. 116: aluminum bowl cover for universal joint revolute pair. 117: tapered rolling bearing for universal joint revolute pair. 118: oblique nut for universal joint revolute pair. 119: horizontal axis for staggered cross shaft for universal joints. 120: vertical axis for staggered cross shaft for universal joints. 121: yoke hole member (whole-circle yoke rings) for staggered cross shaft universal joints. 122: bearing bush for universal joint revolute pair. 123: flat rubber ring for universal joint revolute pair. 124: oblique nut for universal joint revolute pair. 125: shaft washer for universal joint revolute pair. 126: thrust bearing roller needle for universal joint revolute pair. 127: connecting piece at lower shaft end of flywheel rotation shaft. 128: nut with ring groove. 129: external flange plate at upper end of pulling torque transfer flexible transmission part. 130: connecting piece with internal thread at lower shaft end of flywheel rotation shaft. 131: external flange plate at lower end of pulling torque transfer flexible transmission part. 132: external flange plate at upper end of flywheel center shaft. 133: support plate of suspended flexible flywheel device. 134: base for suspended flexible flywheel device (connected with site foundation). 135: installed reference plane for suspended flexible flywheel rotation shaft (contact surface). 136: spherical surface (contact surface) for suspended flexible flywheel device support. 137: spherical cone for suspended flexible flywheel device support. 138: vacuum chamber shell for suspended flexible flywheel device. 139: outer steel bushing accommodating each section of steel bushing of permanent magnetic bearing stationary disc. 140: bearing block at lower end of flywheel rotation shaft. 141: sleeve with outer spherical surface. 142: support disc with inner spherical surface. 143: outer ring support disc. 144: set screw. 145: adjusting washer. 146: nut for fixing permanent magnetic bearing rotary disc. 147: adapter sleeve for fixing permanent magnetic bearing rotary disc. 148: intermediate spacer bush between permanent magnetic bearing rotary discs. 149: soft magnetic material electromagnetic pure iron ring for permanent magnetic bearing stationary disc. 150: permanent magnet material Nd—Fe—B ring for permanent magnetic bearing stationary disc. 151: non-magnetic material aluminium alloy matrix for permanent magnetic bearing stationary disc. 152: spacer bush at uppermost end of permanent magnetic bearing rotary disc. 153: steel bearing block at upper end of flywheel rotation shaft. 154: upper-end steel bushing accommodating permanent magnetic bearing stationary disc. 155: rubber elastic cushion cover. 156: intermediate steel bushing accommodating permanent magnetic bearing stationary disc. 157: lower-end steel bushing accommodating permanent magnetic bearing stationary disc. 158: end cover of bearing block at lower end of flywheel rotation shaft. 159: centrifugal isolating disc for bearing chamber at lower end of flywheel rotation shaft. 160: bearing spacer at lower end of flywheel rotation shaft. 161: bearing spacer at lower end of flywheel rotation shaft. 162: bearing aluminium-alloy end base at upper end of flywheel rotation shaft. 163: bearing spacer at upper end of flywheel rotation shaft. 164: bearing spacer at upper end of flywheel rotation shaft. 165: bearing aluminium-alloy end cover at upper end of flywheel rotation shaft. 166: fan-shaped cushion block for suspended flexible flywheel device support. 167: fan-shaped adjusting base plate (adjusting clearance between permanent magnetic bearing rotary disc and stationary disc). 168: end thin-walled ring unit for brazing ring cavity wall structure of vacuum container shell. 169: intermediate thin-walled ring unit for brazing ring cavity wall structure of vacuum container shell. 170: end thin-walled ring unit for brazing ring cavity wall structure of vacuum container shell. 171: end thin-walled ring unit for brazing ring cavity wall structure between support plate and upper bearing block. 172: intermediate thin-walled ring unit for brazing ring cavity wall structure between support plate and upper bearing block. 173: end thin-walled ring unit for brazing ring cavity wall structure between support plate and upper bearing block. 174: internal spline sleeve connecting HET rotation shaft and flywheel rotation shaft. 175: bracket connecting HET stator and flywheel bearing block. 176: suspended flexible flywheel device. 177: flywheel-side vertical separated HET half-coupled member. 178: motor-side horizontal separated HET half-coupled member. 179: horizontal synchronous motor/generator. 180: end shaft of HET hollow rotation shaft. 181: lantern ring of HET hollow rotation shaft. 182: end shaft of HET hollow rotation shaft.