ELECTRIC OIL PUMP

Abstract

An electric oil pump, including a pump housing, a fixed shaft in the pump housing, an inner gear eccentrically and rotatably connected to the fixed shaft, an outer gear coaxially connected to the fixed shaft and rotatably arranged in the pump housing, the outer gear is located at an outer periphery of the inner gear and engaged with the inner gear, a motor rotor fixedly connected to an outer periphery of the outer gear, and a motor stator at an outer periphery of the motor rotor, the motor stator is fixedly connected to the pump housing. A projection area of the motor stator, a projection area of the motor rotor, a projection area of the outer gear, a projection area of the inner gear and a projection area of the fixed shaft on a plane through an axis of the fixed shaft at least partially overlap.

Claims

1. An electric oil pump, comprising: a pump housing, a fixed shaft, provided in the pump housing, an inner gear, eccentrically and rotatably connected to the fixed shaft, an outer gear, coaxially connected to the fixed shaft and rotatably arranged in the pump housing, wherein the outer gear is positioned at an outer periphery of the inner gear and engaged with the inner gear, a motor rotor, fixedly connected to an outer periphery of the outer gear, and a motor stator, positioned at an outer periphery of the motor rotor and fixedly connected to the pump housing, wherein a projection area of the motor stator, a projection area of the motor rotor, a projection area of the outer gear, a projection area of the inner gear and a projection area of the fixed shaft on a plane through an axis of the fixed shaft at least partially overlap with each other.

2. The electric oil pump according to claim 1, further comprising a first bearing, wherein the outer gear is rotatably connected to a first end of the fixed shaft via the first bearing, and a second end of the fixed shaft is connected to the pump housing.

3. The electric oil pump according to claim 1, further comprising a second bearing, a first end of the fixed shaft is rotatably connected to the pump housing via the second bearing, a second end of the fixed shaft is coaxially connected to the outer gear.

4. The electric oil pump according to claim 1, further comprising an eccentric calibrator provided between the fixed shaft and the inner gear, wherein the eccentric calibrator is configured as a crescent sleeve provided on an outer circumference wall of the fixed shaft, the crescent sleeve is provided with a curved notch for insertion fitting with the fixed shaft, and the crescent sleeve is configured to allow the inner gear to be eccentrically and rotatably connected to the fixed shaft.

5. The electric oil pump according to claim 4, further comprising a bushing, wherein the inner gear is rotatably connected to the crescent sleeve and the fixed shaft via the bushing.

6. The electric oil pump according to claim 1, wherein the fixed shaft or the outer gear is fixedly connected with a sensor configured for cold start.

7. The electric oil pump according to claim 1, wherein a plurality of intake-expulsion chambers are formed between the outer gear and the inner gear, a volume of the plurality of intake-expulsion chambers first increases gradually and then decreases gradually along a rotation direction of the outer gear, the pump housing is defined with an inlet and an outlet, when the plurality of intake-expulsion chambers increase gradually, an open end of the plurality of intake-expulsion chambers is aligned with the inlet, and when the plurality of intake-expulsion chambers decrease gradually, the open end of the plurality of intake-expulsion chambers is aligned with the outlet.

8. The electric oil pump according to claim 7, wherein when the volume of the plurality of intake-expulsion chambers increases gradually, cooling oil flows into the plurality of intake-expulsion chambers via the inlet, and when the volume of the plurality of intake-expulsion chambers decreases gradually, the cooling oil in the plurality of intake-expulsion chambers is pressed out of the outlet.

9. The electric oil pump according to claim 1, further comprising a circuit control module, wherein the circuit control module comprises a controller and a busbar hub, the controller and the busbar hub are arranged in the pump housing, the motor stator is arranged on the busbar hub, the motor stator is provided with a plurality of stator coils along a circumferential direction of the motor stator, the motor rotor is sleeved on an outer circumference of the outer gear, and an outer circumference wall of the motor rotor corresponds to an inner circumference wall of the motor stator.

10. The electric oil pump according to claim 9, wherein an O-ring is provided at an outer periphery of the pump housing.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0028] FIG. 1 is a schematic diagram showing the appearance structure of an electric oil pump according to a first embodiment of the present application;

[0029] FIG. 2 is a schematic three-dimensional section view of the electric oil pump according to the first embodiment of the present application;

[0030] FIG. 3 is a section view showing the internal structure of the electric oil pump according to the first embodiment of the present application;

[0031] FIG. 4 is a schematic structural diagram of a motor stator in the electric oil pump according to the first embodiment of the present application;

[0032] FIG. 5 is a schematic structural diagram of a pump housing in the electric oil pump according to the first embodiment of the present application;

[0033] FIG. 6 is a schematic three-dimensional cross section of an electric oil pump according to a second embodiment of the present application;

[0034] FIG. 7 is a schematic structural diagram showing the circuit control module, the outer gear and the inner gear in the electric oil pump according to the second embodiment of the present application;

[0035] FIG. 8 is a schematic structural diagram showing the assembly of the motor stator, the inner gear and the outer gear in the electric oil pump according to the second embodiment of the present application;

[0036] FIG. 9 is a schematic structural diagram of the bottom of the pump housing of the electric oil pump according to the second embodiment of the present application;

[0037] FIG. 10 is a schematic structural diagram of the outer gear and the inner gear in the electric oil pump according to the second embodiment of the present application;

[0038] FIG. 11 is a schematic diagram showing an eccentric calibrator in an integrated electric oil pump according to the second embodiment of the present application; and

[0039] FIG. 12 is a schematic three-dimensional section view of the electric oil pump according to the third embodiment of the present application.

DETAILED DESCRIPTION

[0040] In order to make the object, technical solutions and advantages of the present application more clear, it will be described in detail below with reference to the accompanying drawings. The assemblies in embodiments of the present application, which are typically described and illustrated in the drawings herein, may be arranged and designed in a variety of different configurations. All other embodiments obtained by a person of ordinary skilled in the art based on the embodiments of the present disclosure without creative efforts shall fall within the protection scope of the present disclosure.

[0041] It should be noted that similar reference numerals and letters denote similar items in the following accompanying drawings, and therefore, once an item is defined in a drawing, it is not necessary to further define and explain it in the following accompanying drawings.

[0042] In the description of the present disclosure, it should be noted that, unless otherwise clearly specified and defined, the terms install, connecting, and connected should be understood in a broad sense, for example, it may be a fixed connection, a detachable connection, or an integral connection, it may be a mechanical connection or an electrical connection, and it may be a direct connection, an indirect connection through an intermediate medium, or an inner connection of two elements. For those skilled in the art, the specific meanings of the above terms in the present disclosure could be understood according to a specific condition.

[0043] In the description of the present disclosure, it should be understood that the orientation or position relationship indicated by the terms upper, lower, left, right, etc. are based on the orientation or position relationship shown in the accompanying drawings and are intended to facilitate the description of the present disclosure and simplify the description only, rather than indicating or implying that the apparatus or element referred to must have a particular orientation or be constructed and operated in a particular orientation, and therefore are not to be interpreted as limiting the present disclosure.

[0044] The embodiments of the present application will be described below in further detail with reference to the accompanying drawings. In the case of no conflict, the features in the following embodiments may be combined with each other

The First Embodiment

[0045] Referring to FIGS. 1-5, this embodiment discloses an electric oil pump. Referring to FIG. 1, the electric oil pump includes a pump housing 1. In some embodiments, the pump housing 1 is made of aluminum. An outlet 12 is defined in a side wall of the pump housing 1, an inlet 11 is defined at the bottom of the pump housing 1. The bottom of the pump housing 1 is provided with a filter screen 14, which is located at the inlet 11 to cover the inlet 11.

[0046] Referring to FIGS. 2-4, a fixed shaft 4, a motor, a circuit control module 9 and a gear set are installed in the pump housing 1. The motor includes a motor rotor 8, a motor stator 93 and a stator winding 94. The motor stator 93 is fixed in the pump housing 1, the motor rotor 8 is arranged in the motor stator 93, and a plurality of stator coils 94 are wound around the motor stator 93 circumferentially, located between the motor rotor 8 and the motor stator 93.

[0047] The gear set includes an outer gear 2 that is integrated in and fixed to the motor rotor 8 and an inner gear 3 that is located in the outer gear 2 and engaged with the inner teeth of the outer gear 2. The inner gear 3 is eccentrically and rotatably connected to the fixed shaft 4, in which eccentrically means that the rotation axes do not coincide. The outer gear 2 is coaxially connected to the fixed shaft 4 and rotatably arranged in the pump housing 1. In the present disclosure, the outer gear 2 is integrated into the motor rotor 8, which are pressed into a whole. On the one hand, this design significantly reduces the volume of the system, reduces the weight of the system, and reduces the material and production costs of the system obviously. On the other hand, this design effectively reduces the friction of the chamber of gerotor, which is conducive to improving the efficiency of the system.

[0048] The pump housing 1 is provided with an enclosure 15 for separating the controller 91 from the busbar hub 92. With the enclosure 15, the oil paths may be separated from the electric control part, thereby improving the sealing effect and ensuring the work of the controller 91 at a suitable temperature. A PTC temperature sensor (not shown) for detecting and feeding back the temperature of the cooling oil is installed on the enclosure 15 and electrically connected to the controller 91. In some embodiments, the detection of the PTC temperature sensor may be accurate to 0.1 C.

[0049] The outer gear is integrated in the motor rotor and the thermal expansion coefficients of the motor stator 93 and the pump body are identical, which greatly reduces the influence of temperature on the clearances of the oil pump, so as to precisely ensure the end clearance of the pump, such that the influence of temperature on the flow efficiency of the system is effectively reduced or avoided.

[0050] During operation, the circuit control module 9 controls a plurality of stator windings 94 to be powered on to generate a magnetic field, which interacts with the permanent magnetic field of a magnet of the motor rotor 8, to drive the motor rotor 8 to rotate. The motor rotor 8 is fixed to the outer gear 2, that is, the motor stator 93 and the magnet of the motor rotor 8 interact with each other to drive the outer gear 2 to rotate, and the outer gear 2 in turn drives the inner gear 3 to rotate, thus realizing the relative rotation of the inner gear 3 relative to the outer gear 2.

[0051] In particular, projection areas of the motor stator 93, of the motor rotor 8, of the outer gear 2, of the inner gear 3 and of the fixed shaft 4 on a plane through the axis of the fixed shaft 4 at least partially overlap with each other. With the present structure, the axial height of the electric oil pump may be reduced, so as to attain a compact structure and a small size.

[0052] A sealing ring is further provided at an outer periphery of the pump housing 1. In some embodiments, the sealing ring is an O-ring and made of rubber. The O-ring 17 is configured for horizontal and axial deformation, which is conductive to sealing to reduce oil leakage and to form high pressure. This design is cost-effective and efficient, easy to assemble, has a long service life and is easy to maintain.

[0053] In some embodiments, the electric oil pump further includes an upper cover 25 fixedly connected to the outer gear 2. One end of the fixed shaft 4 is rotatably connected to the pump housing 1 via a bearing 6, and the other end of the fixed shaft 4 is coaxially and fixedly connected to the outer gear 2 through the upper cover 25. The inner gear 3 is eccentrically connected to the fixed shaft 4 through the pump housing 1, and the inner gear 3 is rotatably connected to the pump housing 1.

[0054] For the cold start of the high-power electric oil pump, the top of the fixed shaft 4 is also fixedly connected with a sensor 26 in this embodiment, for example, a magnetic transformer. In other embodiments, the sensor 26 may also be fixedly connected to the upper cover 25 fixedly connected to the outer gear 2.

[0055] The circuit control module 9 includes a busbar hub 92 above the motor in the pump housing 1 and a controller 91 above the busbar hub 92. The function of the busbar hub 92 is to collect the incoming and outgoing lines of the stator winding 94, so that the line ends are distributed orderly and clearly, and the line ends are welded on the busbar hub 92 by a simple and clean process. Another function of the busbar hub 92 is to separate the controller 91 from the motor part, so that the oil only circulates in the motor part to form a cooling and lubrication loop, thereby preventing the oil from entering the controller 91.

[0056] The busbar hub 92 is arranged above the stator assembly. Pins of the stator windings 94 are inserted in the busbar hub 92, thereby simplifying the design of the electric control module and thus the traditional winding structure.

[0057] The controller 91 may allow a fast response, which is characterized in a circuit reverse connection protection, prevention of signal interference, monitoring of oil temperature, prevention of overheating, independent communication channels, detection of the angular position of the motor, reception and calculation of the motor speed, and rational comparison and adjustment of the actual rotor speed.

[0058] Since the height of the whole electric oil pump is reduced, compared with a traditional electric oil pump, a short time for the pressurized cooling oil to flow to the stator assembly is required by the electric oil pump in this embodiment, thereby achieving a better cooling effect.

[0059] Referring to FIG. 2, the working process of the electric oil pump is as follows: the controller 91 controls the busbar hub 92 to power the plurality of stator windings 94 on the motor stator 93, the plurality of stator windings 94 after being powered on generate a magnetic field, to drive the motor rotor 8 to rotate, the motor stator 93 drives the outer gear 2 to rotate, thus realizing the relative rotation of the outer gear 2 relative to the inner gear 3.

[0060] When the inner gear 3 rotates relative to the outer gear 2, the volume of the intake-expulsion chamber 21 increases gradually, the oil is taken in through the inlet 11, so the amount of oil in the intake-expulsion chamber 21 increases as the volume increases. In this case, the oil with a low temperature comes into contact with the teeth of the inner gear 3 and the outer gear 2 during the intake of the oil, such that the oil absorbs the heat of the teeth. Then, the oil is discharged through the outlet 12 as the volume of the intake-expulsion chamber 21 decreases gradually, such that the amount of oil in the intake-expulsion chamber 21 decreases as the volume decreases. In this case, the oil with a high temperature after absorbing heat during the intake of the oil is discharged out of the pump body from the outlet 12, thereby realizing the cooling and lubrication of the inner gear 3 and the outer gear 2 while cooling the pump body.

[0061] Referring to FIG. 5, the bottom of the pump housing 1 is integrally formed with a housing bottom 13 configured to cover the inlet 11 and the outlet 12. The housing bottom is configured with a pressing hole 131, and the pressing hole 131 is eccentrically arranged relative to the pump housing 1. The fixed shaft 4 is arranged in the pressing hole 131, and an outer circumference wall of the fixed shaft 4 is in tight fit with a hole wall of the pressing hole 131. A sliding bearing may be arranged between the inner gear 3 and the pump housing 1 to reduce the rotation resistance and increase the service life. The end surface of the housing bottom 13 is configured with an intake mouth 132 in communication with the inlet 11 and an expulsion mouth 133 in communication with the outlet 12. A partition 134 for separating the intake mouth 132 from the expulsion mouth 133 is provided at the housing bottom 13, and one side of the partition 134 abuts against one side of the inner gear 3, which improves the sealing effect between the intake mouth 132 and the expulsion mouth 133.

[0062] In this embodiment, the eccentric fit between the inner gear 3 and the outer gear 2 is achieved via the eccentric pressing hole 131 of the pump housing without any redundant accessories. The advantages of this design lie in that the structure of the gerotor is simplified and the assembly difficulty of the rotary shaft and the pump housing is lowered. The concentricity of the motor, the housing and the gear set is improved, which is conducive to ensuring the structure concentricity of the pump system. With this design, the accuracy of the air gap between the motor stator and the motor rotor may be improved, so that the motor always works in a precise and uniform magnetic field distribution. The motor works more stably and more precisely, the magnetic field of the motor is unitized more efficiently, so as to ultimately ensure the efficient operation of the electric oil pump. The accumulation of assembly deviations caused by multiple contact interfaces is reduced, which effectively reduces the friction resistance generated when the pump structure rotates. The large eccentricity caused by the rotation of a large-sized bearing is reduced, which improves the efficiency and stability of the electric oil pump. This design has a small size, light weight and is cost-efficient.

The Second Embodiment

[0063] Referring to FIGS. 6-11, this embodiment differs from the first embodiment in the eccentric connection structure of the fixed shaft 4.

[0064] Referring to FIGS. 6-8, the outer gear 2 in this embodiment includes an inner circumference of outer gear 23, which is engaged with the inner gear 3, and the inner circumference of the motor rotor is fixedly sleeved on the outer circumference of the outer gear. A permanent magnet of the motor rotor 8 is fixed at an outer periphery of the outer circumference of motor rotor 24, and an air gap 16 is formed between the permanent magnet of the motor rotor 8 and the stator windings 94. For the purpose of research and development process, the influence of various factors on the stability of the clear width of the air gap 16 shall be minimized. A rotor neck 22 is integrally formed at the top of the outer circumference of motor rotor 24, and a bearing 6 is installed in the rotor neck 22. The bearing 6 is configured to support the motor rotor 8, to ensure the rotation of the outer gear 2 in the gerotor. The bearing 6 is installed at an end of the gerotor, so that there is no chamber between the motor and the gerotor, thereby reducing the height of the electric oil pump, which significantly reduces the weight and size of the gerotor. In this embodiment, the bearing 6 and the pump housing 1 are machined by a same mechanical fixture, so that the bearing 6 and the pump housing 1 have very precise coaxiality and concentricity, so as to precisely control the air gap eccentricity.

[0065] Referring to FIGS. 6-9, the bottom of the pump housing 1 is configured with a pressing hole 131, and the pressing hole 131 and the pump housing 1 are arranged concentrically. The fixed shaft 4 is inserted into the pressing hole 131, and the fixed shaft 4 is in tight fit with the bearing 6. The rotor neck 22 that matches the bearing 6 is integrally formed on one side of the outer gear 2. The inner gear includes an inner circumference of inner gear that is in coaxial fit with the fixed shaft 4 and abuts against the eccentric assembly. The inner gear 3 is eccentrically and rotatably connected to the fixed shaft 4 via an eccentric calibrator 5. Eccentrically means that the rotation axes do not coincide. The eccentric calibrator 5 is configured as a crescent sleeve disposed on an outer circumference wall of the fixed shaft 4. The crescent sleeve is configured with a curved notch 51 for the fixed shaft 4 to be embedded. The crescent sleeve is configured to allow the inner gear 3 to be eccentrically and rotatably connected to the fixed shaft 4. The inner circumference of motor rotor is configured to axially abut against the outer circumference of outer gear. The rotor neck 22 that matches the bearing 6 is integrally formed on one side of the outer circumference of motor rotor 24. The rotor neck 22 and one side of the outer circumference of motor rotor 24 form a rabbet for the bearing 6 to be embedded. The outer circumference wall of the bearing 6 is in tight fit with the circumferential groove wall of the rabbet, so as to reduce the working noise.

[0066] Referring to FIGS. 9-11, an inner circumferential wall of the outer gear 23 and an outer circumferential wall of the inner gear 3 are both attached to an inner end face of the outer circumference of the motor rotor 24. A zone between the outer gear 2 and the inner gear 3 is divided by tooth-to-tooth contact to form multiple closed intake-expulsion chambers 21, the volume of which gradually increases and then decreases along a rotation direction of the outer gear 2. A bottom of pump housing 1 is integrally formed with an inlet 11, and an outer circumferential wall of the pump housing 1 is integrally formed with an outlet 12. When the intake-expulsion chamber 21 gradually increases, it is aligned with the inlet 11. When the intake-expulsion chamber 21 gradually decreases, it is aligned with the outlet 12.

[0067] The bottom of pump housing 1 is integrally formed with a housing bottom 13 covering the inlet 11 and the outlet 12. An end face of housing bottom 13 is axially defined with a pressing hole 131 fixedly connected to one end of the fixed shaft 4. The fixed shaft 4 is inserted into the pressing hole 131, and an outer circumferential wall of fixed shaft 4 is tightly fit with the hole wall of the pressing hole 131. An end face of the housing bottom 13 is defined with an intake mouth 132 communicating with the inlet 11 and an expulsion mouth 133 communicating with the outlet 12. At the housing bottom 13, a partition 134 is formed to separate the intake mouth 132 and the expulsion mouth 133 after the intake mouth 132 and the expulsion mouth 133 are defined. One side of the partition 134 is attached to one side of the inner gear 3, improving the sealing between the intake mouth 132 and the expulsion mouth 133.

[0068] A location hole 52 is formed in one side of the crescent sleeve and penetrates through the crescent sleeve, a guide hole for assembly 135 corresponding to the location hole 52 is formed in the housing bottom 13, the guide hole for assembly 135 and the pressing hole 131 are arranged eccentrically. A bushing is provided between the fixed shaft 4 and the inner gear 3, to reduce sliding friction. The inner gear 3 is rotatably connected to the crescent sleeve and the fixed shaft 4 via the bushing 7.

[0069] An opening is formed in the pump housing 1 to match the fixed shaft 4, thereby effectively reducing the machining complexity of the pump housing 1, improving the machining efficiency of the pump housing 1, and improving the matching accuracy between the outer gear 2 and the inner gear 3.

[0070] The implementation principle of the high-precision electric oil pump in this embodiment of the present application is stated as follows.

[0071] A fixed shaft 4 is provided in the pump housing 1, and then an eccentric calibrator 5 is provided on the circumferential side wall of the fixed shaft 4 to form an eccentric assembly 41. In this way, when the outer gear 2 is rotatably connected to the fixed shaft 4, the eccentric assembly 41 may also be rotatably connected to the inner gear 3, thus achieving the relative coaxial and eccentric arrangement of the inner gear 3 relative to the outer gear 2.

The Third Embodiment

[0072] Referring to FIG. 12, this embodiment differs from the first embodiment and the second embodiment in that the bearing is provided between the outer gear and the pump housing, and the fixed shaft 4 has a hollow structure. In this embodiment, a channel for cooling oil to pass through is defined inside the fixed shaft 4. In this embodiment, the fixed shaft 4 is designed to be stationary. Under the drive of the outer gear 2, the inner gear 3 in the pump rotates relative to the fixed shaft 4, and the mutual lubrication therebetween reduces friction, so as to reduce the loss of the gerotor system, and effectively improve the rotation stability of the gerotor.

[0073] The mechanism for cooling the stator assembly by the cooling oil in this embodiment is as follows.

[0074] The motor rotor 8 and the outer gear 2 jointly drive the inner gear 3 to rotate to pressurize the cooling oil from the inlet 11, so that one part of the pressurized cooling oil flows to the stator assembly via the hollow channel of the fixed shaft 4, to cool the stator assembly, and the cooling oil that undergoes heat exchange then flows back to a low-pressure area.

[0075] In addition, the other part of the pressurized cooling oil is directly discharged from the outlet 12 via a high-pressure area.

[0076] In this embodiment, the fixed shaft 4 is further equipped with a radial magnetic steel to monitor the position of the fixed shaft.

[0077] The specific process of cooling the stator assembly of the present application is as follows.

[0078] 1) First, the device is powered on. At this time, the controller 91 is powered on and converts electricity into three-phase electricity to power the stator windings 94. The electromagnetic force drives the motor rotor 8 and the outer gear 2 to rotate. The motor rotor 8 and the outer gear 2 rotate so that the cooling oil from the inlet 11 enters the low-pressure area through the filter screen 14.

[0079] 2) The motor rotor 8 and the outer gear 2 jointly drive the inner gear 3 to rotate around the fixed shaft 4, to pressurize the cooling oil from the inlet 11, so that one part of the pressurized cooling oil flows to the stator assembly through the fixed shaft 4, to cool the stator assembly, the cooling oil that undergoes heat exchange then flows back to the low-pressure area, and the cooling oil is pressurized by a pressure difference caused by the eccentric arrangement of the inner gear relative to the outer gear. In this case, the PTC temperature sensor 82 is configured to detect the current temperature value of the oil and feed the temperature value back to the controller 91, and the controller 91 then feeds the current temperature value of the oil back to an external control system.

[0080] 3) The other part of the pressurized cooling oil is directly discharged from the outlet 12 through the high-pressure area.

[0081] The above shows and describes the basic principles, main features and advantages of the present invention. Those skilled in the industry should understand that the present application is not limited by the embodiments described above. The described embodiments and description only illustrate the principles of the present application. Without departing from the spirit and scope of the present disclosure, the present application may also be subject to various changes, modifications, substitutions and variations, all of which fall within the scope of the present disclosure as claimed.

LIST OF REFERENCE NUMERALS

[0082] 1 Pump Housing [0083] 11 Inlet [0084] 12 Outlet [0085] 13 Bottom Of Pump Housing [0086] 131 Pressing Hole [0087] 132 Intake Mouth [0088] 133 Expulsion Mouth [0089] 134 Partition [0090] 135 Guide Hole For Assembly [0091] 14 Filter Screen [0092] 15 Enclosure [0093] 16 Air Gap [0094] 17 Sealing Ring [0095] 2 Outer Gear [0096] 21 Intake And Outtake Chamber For Oil [0097] 22 Rotor Neck [0098] 23 Inner Circumference Of Outer Gear [0099] 24 Outer Circumference Of Motor Rotor [0100] 25 Upper Cover [0101] 26 Sensor [0102] 3 Inner Gear [0103] 4 Fixed Shaft [0104] 41 Eccentric Assembly [0105] 5 Eccentric Calibrator [0106] 51 curved notch [0107] 52 Location Hole [0108] 6 Bearing [0109] 7 Bushing [0110] 8 Motor Rotor [0111] 9 Circuit Control Module [0112] 91 Controller [0113] 92 busbar hub [0114] 93 Motor Stator [0115] 94 Stator Winding