Rotor mechanism

Abstract

A rotor mechanism for use in moving fluid. The rotor mechanism has six rotor units spherically arranged, with at least one rotor unit including a port through it's body. Each rotor has the form of a truncated cone with two symmetric spiral recesses provided on the lateral surface of the rotor which acts to cooperate with the adjacent rotors. Rotation of at least one rotor unit causes rotation of adjacent rotor units which thereby moves fluid without compression between the outside of the mechanism and the port via a central substantially spherical free space cavity formed by the cooperation of inner surfaces of the rotor units. The rotor mechanism is fully submersible.

Claims

1. A rotor mechanism for use in moving fluid, the rotor mechanism comprising: a plurality of rotor units spherically arranged to form a rotor mechanism body; each rotor unit including an outer surface and an inner surface and at least one rotor unit having a first opening on the outer surface and a second opening on the inner surface such that an elongate aperture extends between the first and second openings to create a port through the rotor unit; wherein the rotor mechanism body is supported by an external frame comprising a plurality of apertures which allow fluid to flow therethrough and contact an outer surface of the rotor mechanism body; and wherein rotation of at least one rotor unit causes rotation of adjacent rotor units which thereby moves fluid without compression between the outer surface of the rotor mechanism body and the port via a central substantially spherical uninterrupted free space cavity formed by the cooperation of the inner surfaces of the rotor units.

2. A rotor mechanism according to claim 1 wherein the external frame comprises a plurality of arcs.

3. A rotor mechanism according to claim 1 wherein the external frame supports the rotor mechanism body on a plurality of bearings.

4. A rotor mechanism according to claim 1 wherein at least two rotor units have a port through the rotor unit.

5. A rotor mechanism according to claim 1 wherein each rotor unit is operable to co-operate with adjacent rotor units such that during rotation plural channels are created in which fluid is carried in one direction between the outer surface of the rotor mechanism body and the central substantially spherical uninterrupted free space cavity.

6. A rotor mechanism according to claim 5 wherein each rotation fills each one of the plural channels and seals each end thereof to create a temporary chamber.

7. A rotor mechanism according to claim 1 wherein each rotor unit has at least two lateral surfaces which are arranged to provide the rotor unit with a truncated double helix form.

8. A rotor mechanism according to claim 1 wherein the rotor mechanism is provided with six rotor units, the rotor units having the same dimensions.

9. A rotor mechanism according to claim 8 wherein each rotor unit comprises a conical screw rotor, having an axis at right angles to adjacent rotor units and which is twisted at an angle over a length of a truncated cone.

10. A rotor mechanism according to claim 9 wherein a radius of the central substantially spherical uninterrupted free space cavity is greater than half the radius of the rotor mechanism body.

11. A rotor mechanism according to claim 10 wherein the rotor units have dimensions such that the rotor mechanism pumps up to around half the volume of the rotor mechanism body on a single rotation of the rotor units.

12. A rotor mechanism according to claim 11 wherein the radius of the rotor mechanism body, the length and twist angle of the rotor units and dimension of the port are selected to substantially equalize the volume of fluid travelling through the rotor mechanism.

13. A rotor mechanism according to claim 1 wherein a spiral edge of each rotor unit making up the central substantially spherical uninterrupted free space cavity, has a coil of just equal to 180 degrees in order to completely isolate the central substantially spherical uninterrupted free space cavity from the environment.

14. A rotor mechanism according to claim 1 wherein in use, a first rotor unit is held stationary and the remaining rotor units rotate synchronously around three mutually perpendicular axis which converge at a central point of the central substantially spherical uninterrupted free space cavity of the rotor mechanism.

15. A rotor mechanism according to claim 1, the rotor mechanism further comprising a drive unit which in use, acts upon one of said rotor units operable to rotate in order to actuate and drive the rotatable rotor units.

16. A rotor mechanism according to claim 1, the rotor mechanism further comprising a drive unit which operates in the rotor mechanism by means of an electromagnetically induced rotation.

17. A rotor mechanism according to claim 16 wherein one or more rotor units include windings coupled with a magnetic source of opposing pole, and an induced rotational force is delivered by electrical supply to the windings.

18. A rotor mechanism according to claim 1, wherein one or more rotor units include windings coupled with a magnetic source of opposing pole and wherein rotation of the rotor units is carried out by an external force and electricity is generated by moving the windings across the magnetic field.

19. A rotor mechanism according to claim 1 wherein the application of a fluid through the port induces rotation of at least one rotor unit which thereby operates the rotor mechanism.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Embodiments of the present invention will now be described, by way of example only, with reference to the accompanying drawing of which:

(2) FIG. 1 is a schematic diagram of a known volumetric rotor mechanism;

(3) FIGS. 2 to 6 are cross sections of details of features of the volumetric rotor mechanism of FIG. 1;

(4) FIGS. 7 to 10 are cross sections of the volumetric rotor mechanism of FIG. 1 through different planes;

(5) FIG. 11 is a cross-sectional view through a schematic illustration of a rotor mechanism according to a first embodiment of the present invention;

(6) FIG. 12 is a schematic illustration of the rotor mechanism of FIG. 11;

(7) FIG. 13 is a schematic illustration of a frame arrangement of a rotor mechanism according to an embodiment of the present invention;

(8) FIGS. 14A to 14F are different views of an embodiment of a rotor of the rotor mechanism of the present invention;

(9) FIGS. 15A to 15D are schematic diagrams of a section of an embodiment of a driving mechanism of the rotor mechanism of the present invention;

(10) FIGS. 16A to 16F are graphical representations of fluid progression in a rotor mechanism according to a further embodiment of the invention;

(11) FIGS. 17A and 17B are schematic illustration of pumps according to embodiments of the present invention; and

(12) FIG. 18 is a schematic illustration of a rotor mechanism arranged for a motor or turbine according to an embodiment of the present invention.

DETAILED DESCRIPTION OF THE PRESENT INVENTION

(13) Reference is initially made to FIG. 11 of the drawings which shows a rotor mechanism, generally indicated by reference numeral 20, in cross-section exposing four of six rotor units 30a-30f, arranged spherically to form a rotor mechanism body 21, with each rotor unit 30 having an outer surface 32a-32f and inner surface 38a-38f respectively, and a port 40c providing an aperture 41c between the outer surface 32c and the inner surface 38c of a rotor unit 30c, leading to a free space cavity 26 in the centre of the rotor mechanism 20.

(14) The rotor units 30 are solid elements in the form of a conical spiral arranged on an axis 31. The rotor units 30 are positioned such that the axis 31a-31f of each rotor unit 30 is at right angles to the axis 31a-31f of the adjacent rotor units. Each rotor unit 30 is arranged so as to cooperate with one another such that the petal shaped outer surface 32 of each rotor unit 30 is curved concavely out from the rotor mechanism 20 and contributes to the outer surface 22 of the rotor mechanism body 21. This is best seen in FIG. 12. The petal shape outer surface 32 of each rotor unit 30 is defined by an outer edge 33. Each rotor unit 30 is further provided with lateral surfaces 34 and 36, in this case lateral surfaces 34b, 34c and 34d can be seen between the outer edges 33b, 33c and 33d wherein the lateral surfaces 34b, 34c and 34d cooperate for form an outer surface recess 24a which may be considered as a temporary port. It can also be seen that for rotor units 30b, 30a and 30c, rotor tips 37a, 37b and 37c of outer surfaces 32a, 32b and 32c all meet, thus closing the outer surface 22 at these points, which may be considered as closed points. This is also the case at the rotor tips 37c, 37d and 37e and so on around the rotor mechanism 20. For the six rotor units 30, there will be four outer surface recesses 24, or temporary ports, and four closed points at a time. In addition, it can be seen that between these closed points formed by rotor tips 37a, b and c, and so on, a chamber is formed 42 which is closed to both the central cavity 26 of the rotor mechanism 20 and the outside environment 28 surrounding the rotor mechanism 20. This is best seen in FIG. 11.

(15) Without an internal gearing structure 7, as in the prior art, the rotor units 30 are held together by use of a frame 50, illustrated in FIG. 13. In FIG. 13, like parts to those of FIGS. 11 and 12 have been given the same reference numerals to aid clarity. Frame 50 comprises four arc sections 52a-d. Only two 52a,b are shown, but 52c,d would be arranged to form a circle which would lie perpendicularly to arc sections 52a,b to provide a spherical cage as the frame 50. At the port 40c, and for this illustration the opposite rotor unit 30d also has a port 40d connecting to the central cavity 26, a tubular section 54 is inserted into the port 40 to extend the port 40 out of the frame 50. Between the arc sections 52 and the tubular section 54 is a bearing unit 56. Each port 40 has a tubular section 54 and a bearing unit 56. Each bearing unit 56 connects to the four arc sections 52 at screw threads 58. Each bearing unit 56 houses two bearing rings 60 arranged along the tubular section 54, so that the tubular section 54 and with it the rotor unit 30c can rotate independently of the frame 50. The bearing unit 56 also provides an exit port 62, for connection to a pipe or tubing as required.

(16) On the rotor units 30 which do not include ports 40, a bearing axle 44 is fixed into the outer surface 32 of the rotor unit 30. The axle 44 does not extend through the rotor unit 30 and is only embedded sufficiently to turn with the rotor unit 30. Preferentially ports 40 face each other, when more than one is present. In this embodiment two are shown, but there may be up to six in i.e. one per rotor unit 30, if desired. Each arc section 52 has a twin set of bearing rings 64 arranged centrally and axially on the arc. The bearing rings 64 slide over the axles 44 and allow the axles 44 together with their attached rotor unit 30 to rotate independently of the frame 50.

(17) By using pairs of bearing rings 60,64 at each of the six axes 31 of the rotor mechanism 20, the axes are cantilevered for support.

(18) Each of the rotor units 30 is now considered in greater detail with FIGS. 14A to 14 F illustrating a variety of perspective and plan views of a rotor unit 30.

(19) With reference first to FIG. 14A, there is shown a plan view of a rotor unit 30 in which can be seen inner surface 38 which has a petal shape. The inner surface 38 is located between first lateral surface 34 and second lateral surface 36.

(20) As can be seen from FIG. 14B in which a side view of rotor 30 is shown, lateral surface 34 has a tapering helical form with lateral surface having an opposing tapering helical form such that together lateral surface 34 and 36 form a truncated double helix. The form of the rotor unit can be understood as being a conical screw which is twisted at an angle over length L of a truncated cone. Inner surface 38 is curved concavely into the body of the rotor unit 30 and outer surface 32 curves concavely away from the body of the rotor unit 30. Axle 44 is located in the centre of outer surface 32. Note than the axle 44 is a protrusion which does not pass through the rotor 30.

(21) With reference to FIG. 14C there is shown a plan view of a rotor unit 30 with section lines A-A; B-B and C-C detailed. As can be seen the outer edge 33 defines outer surface 32 and lateral surfaces 34 and 36 having driving edges 34 and 36 which extend slightly beyond outer edge 33 at diametrically opposite positions on the outer edge 33. In FIGS. 14D, 14E and 14F cross sectional views of the rotor unit 30 are shown through section lines A-A, B-B and C-C respectively.

(22) In use, the six rotor units 30 are located within the frame 50. In an embodiment of a submersible or bilge pump, a single port 40 is present and the connection 62 will be made to tubing to be routed overboard. On one axle 44, there will be located a DC motor to turn the axle into a drive shaft and cause rotation of the rotor unit 30 to which the axle 44 is affixed. A low rpm is all that is required as the motor is only turning the single rotor unit. The rotor mechanism body 21 in it's frame 50 is submerged in water.

(23) The rotation of a single rotor unit 30 by the motor impels the other rotor units to turn synchronously about their axis 31. With reference now to FIGS. 15A to 15D there is shown two rotor units combined to better illustrate the interlinking of rotor units 30 in rotor mechanism 20 and the progression of the driving mechanism which results from the cooperation of the rotor units. As can be seen in FIG. 15A, rotor unit 30a is arranged so that it is cooperating with, and at right angles to rotor unit 30b. Inner surface points 39a and 39b are arranged so as to be touching one another and driving edge 34a of lateral surface 34a is arrange so that upon rotation, it will act upon lateral surface 36b by imparting a force. The incident angle between the driving edge 34a and driven surface, in this case lateral surface 36b contributes, along with other factors such as the distance from the extremity of contact to the central axis of the driving edge, to determining the torque required to drive the rotors units 30 of the rotor mechanism 20.

(24) It will be appreciated that when three or more rotor units 30 are interlinked perpendicular to one another the driving functionality of the arrangement will act continuously with a driving edge 34 acting on one rotor unit 30 for a 180 turn after which it will act on another adjacent rotor unit 30. As there are two driving edges 34, 36 per rotor unit 30 a continuous driving process through a rotation of 360 is achieved.

(25) The interlocking helical form of rotor units 30a-f, when arranged to form the rotor mechanism 20 of FIGS. 11 to 13 are such that when a driving force is applied to one rotor, for example, rotor 30a, the form of the driving rotor unit 30a as described with reference to FIGS. 14A to 14F will act upon adjacent rotor units 30b, 30c, 30e and 30f (not shown) imparting a force which will cause these driven rotor units 30b, 30c, 30e and 30f to rotate on an axis at 90 to the driving rotor 30a. Each of these rotor units 30b, 30c, 30e and 30f will impart a force to drive the sixth rotor unit 30d in the same manner as described for the other rotor units.

(26) Referring back to FIG. 12, we can consider this as a start position. There will be four recesses 24 exposed on the spherical body 21. Equally there will be four closed points where three rotor tips meet. In this configuration, behind each closed point there is a closed chamber 42 formed from the lateral surfaces of the rotor units 30. As the rotor units 30 begin to rotate, the closed point is opened, thereby drawing fluid in which the rotor mechanism 20 is immersed, into the body 21. A contrasting motion occurs at the recesses 24. Each rotor tip travels along the edge 33 of another rotor unit 30 so that each closed point becomes a recess 24 in a 180 degrees rotation of the rotor units. As the driving and driven rotors 30a-f rotate, the interlocking edges 33, 34, 36 and surfaces 34, 36 temporally create closed chambers 42 which capture fluid, either from the external environment 28 or the central cavity 26, propelling it in to, or out of the mechanism 20 depending on the direction of rotation of the rotor units 30. Following 360 degrees rotation of the rotor units 30, the body 21 will have returned to the start position. The progression of fluid is illustrated in FIGS. 16A-F which shows the creation of the recesses 24, movement of fluid into a closed chamber 42 and the movement of fluid into the free space central cavity 26. Four paths are shown in FIG. 16A-F, but a further four paths will exist on the cross-axis of the body 21. For our bilge pump water is drawn in from the outer surface 22 into the free space cavity 26 and out of the exhaust port 40.

(27) If each of the rotor units 30 are formed in such a manner that the spiral edge of each rotor unit 30 provides a coil at equal to 180 degrees at the closed point, then the internal cavity 42 is completely isolated from the environment 28. Such a design is referred to as not blown, which provides for the possibility of pumping at high pressure. This is in contrast to known designs of turbine and centrifugal pumps in braked conditions which are blown or have permeability. Preferentially, the radii of the central cavity 26 and body 21 is selected together with the length of rotor, angle of rotation and volume of outlet to provide near constant volume of fluid through the rotor mechanism so that back pressure is avoided. In particular, the radius of the central cavity 26 is made greater than half the radius body 21. This also reduces the pressure differential through the rotor mechanism so that the fluid is never compressed and prevents damage to the rotor units.

(28) As detailed above with reference to a submersible or bilge pump, the rotor mechanism 20 can be driven by any external motor. FIG. 17A illustrates the rotor mechanism 20 within the frame 50 being driven by an electric motor 70. The drive shaft of the motor 70 is connected to an axle 44 on one of the rotor units 30. Operating the motor 70, will turn the rotor unit 30 at the drave shaft, this in turn will compel the other rotor units to turn as described hereinbefore. If the frame 50 is immersed in fluid, the fluid will be drawn into the rotor unit unit and be expelled through the ports 40. In this arrangement two ports 40 are shown, but up to five exit ports could be provided. If the drive is reversed, fluid can be drawn in at the ports 40, and expelled through the temporary ports 24. Alternative drive arrangements can be used such as a diesel engine, petrol engine (2 stroke/4 stroke) Wankel engine, steam, wind turbine and a reciprocal engine. A hydraulic motor 72 is illustrated in FIG. 17B. Those skilled in the art will recognize that any external motor system can be used to drive the rotor mechanism 20.

(29) Further embodiments of the present invention are provided by incorporating a magnet and coil arrangement at the axes 44. An example of this embodiment is shown in FIG. 18. In this arrangement the axle 44 includes a circumferentially arranged set of magnets 80. Around each axle 44, at the location of the magnets 80, is a set of winding coils 82. Equally, the magnets could be arranged around the coil.

(30) By applying an electric current to the windings 82, a magnetic field is generated which imparts a rotational force on the accompanying rotor unit 30. The corollary is also useful, in that if the rotors 30 are moved by any means of propulsion, the magnets 80 will rotate and the coils 82 will move through the magnetic fields of the magnets 80, establishing a current in the windings and thus creating electricity.

(31) The principle advantage of the present invention is that it provides a rotor mechanism which does not require an enclosed waterproof housing.

(32) A further advantage of the present invention is that it provides a rotor mechanism which does not compress the fluid as it moves through the mechanism.

(33) A yet further advantage of the present invention is that it provides a pump achievable at very low values of RPM.

(34) Further advantages of the present invention are realized in that it has a high compactness of design (low weight and small dimensions); low number of elements to give a simplicity in design and construction; low level noise; low level of vibration; constancy of stream of a pumped over product; small friction losses and small power consumption compared with pumps of similar productivity.

(35) Modifications may be made to the invention herein described without departing from the scope thereof.