High-voltage gerotor motor with high-low speed conversion function

Abstract

The present invention relates to the field of cycloidal motor technology, and in particular to a high-pressure cycloidal motor with a high-low speed conversion function; it includes a front flange assembly and a cycloidal stator-rotor mechanism for providing multiple high- and low-pressure volume chambers, and is characterized in that it also includes a rear baffle valve body assembly and a rear shell flow distribution assembly for controlling the alternating flow of high- and low-pressure hydraulic oils to achieve the switching of the high-pressure cycloidal motor between low speed and high speed, and the front flange assembly, the cycloidal stator-rotor mechanism, the rear baffle valve body assembly and the rear shell flow distribution assembly are connected and fixed by bolts; since the present invention designs the rear baffle valve body assembly and the rear shell flow distribution assembly inside the high-pressure cycloidal motor, the high-pressure cycloidal motor can be switched between low speed and high speed by controlling the alternating flow of high- and low-pressure hydraulic oils, thereby solving the problem that the prior art configures multiple conveying and receiving interfaces or different density media to perform high- and low-pressure conversion, and there is obvious conversion hysteresis and a large structural volume.

Description

Technical Field

[0001] The present invention relates to the technical field of cycloidal motors, and in particular to a high-voltage cycloidal motor with a high-to-low speed conversion function. Background Art

[0002] In recent years, more and more gerotor motors have been applied to vehicle drive wheels. When the vehicle is working at a work site, the motor works in a low-speed, high-torque mode; when the vehicle is traveling between work sites, the motor works in a high-speed, low-torque mode. However, the gerotor motor mechanism of the prior art is not stable enough when achieving high- and low-speed conversion, resulting in sudden acceleration or deceleration of the vehicle. In vehicle driving, two gerotor motors are often used in parallel to drive a pair of wheels. When performing high- and low-speed conversions on such a vehicle, it is difficult for the two gerotor motors to perform conversion operations at the same time. If there is a time difference in the conversion of the two gerotor motors, the rotation speeds of the two wheels will be different, thereby forcing the vehicle to make an unexpected turn and affecting driving safety.

[0003] In order to achieve the function of high-speed and low-speed conversion, the gerotor motor in the prior art is often complex in structure, with a large number of parts, and has high requirements for the processing and assembly accuracy of the parts. In order to seal between the distribution valve of the gerotor motor and the matching hole of the valve housing, it is necessary to install multiple seals at several different outer diameter positions of the gerotor motor to ensure the sealing effect. This multi-radial seal greatly increases the difficulty and cost of motor processing and assembly. Moreover, the working pressure of this type of gerotor motor is relatively low, and can only reach a maximum of 20MPa.

[0004] In the prior art, CN112178001A discloses a hydraulic cycloidal motor, and its technical solution is as follows: it includes a stator, a rotor, and a variable control component, wherein a rotating hole penetrating from left to right is provided in the stator, and a left end cover is fixedly installed at the left end of the rotating hole and a connecting block is fixedly installed at the right end of the stator; an axial hole and a valve hole which are connected to the rotating hole and coaxial are provided in the connecting block from left to right; a right end cover is fixedly installed at the right end of the valve hole in the connecting block; a distribution shaft is rotatably connected in the valve hole, and an output shaft extending out of the right end cover is provided at the right end of the distribution shaft; an A port and a B port are provided on the outer side of the connecting block; a first annular groove which is connected to the A port and a second annular groove which is connected to the B port are provided on the circumferential outer side of the distribution shaft; a plurality of needle teeth are evenly spaced along the circumferential direction on the inner side wall of the rotating hole, and the rotor is eccentrically arranged The rotor is in contact with a plurality of needle teeth in the rotary hole, and is synchronously rotated and connected with the distribution shaft; a needle tooth ring is slidably connected at the left end of the rotor in the rotary hole, and a plurality of needle tooth grooves for accommodating the needle teeth are evenly distributed along the circumferential direction on the side wall of the needle tooth ring; a rotor ring is sleeved on the outer side of the rotor in the axial hole, and the rotor is slidably connected in the rotor ring along the axial direction of the axial hole; a plurality of meshing cavities located between the needle tooth ring and the rotor ring are formed in the rotary hole between the rotor and the plurality of needle teeth; the first ring groove and the second ring groove are kept in communication with the plurality of meshing cavities and are sequentially communicated with the plurality of meshing cavities as the rotor rotates; when the oil pressure at port A or port B is greater than the set pressure of the variable control component, the meshing cavity increases; when the oil pressure at port A and port B is less than the set pressure of the variable control component, the meshing cavity decreases;

[0005] The advantages of the technical solution are as follows: by setting a variable ring and a variable spring, the high-pressure oil of port A or port B acts on the variable ring. The higher the working pressure, the greater the displacement of the variable ring to the left, thereby making the length of the meshing cavity longer and the displacement of the motor larger, thereby achieving the variable requirements of low speed and high torque and high speed and small torque;

[0006] The disadvantages of this technical solution are: it is impossible to directly modify the existing cycloid motor, resulting in a high manufacturing cost, and the displacement change of the variable ring depends on the variable spring, and the variable spring, due to its own characteristics (hysteresis during deformation), cannot achieve effective proportional control when switching between high and low speeds, and the speed (increase or decrease) cannot change in a curve;

[0007] In the prior art, CN112240323A discloses a hydraulic cycloidal motor, and its technical solution is as follows: the hydraulic cycloidal motor includes a housing, an output shaft, a first distributor, a first rotor, a first needle tooth, a first stator, a second distributor, a second rotor, a second needle tooth, a second stator and a variable control component; the housing is provided with a P port and a T port, the P port is connected to a high-pressure medium, and the T port is connected to a low-pressure medium; the first stator is fixedly connected to the housing, a plurality of the first needle teeth are uniformly distributed inside the first stator along the circumferential direction, the first rotor is eccentrically placed inside the first stator and forms contact with the plurality of the first needle teeth, and the first stator is provided with a plurality of the first needle teeth. , a plurality of first working cavities are formed between the first rotor and the plurality of first needle teeth; the first distributor is synchronously rotatably connected with the first rotor, and a first high-pressure oil groove and a first low-pressure oil groove are provided at the distribution end of the first distributor, the first high-pressure oil groove and the first low-pressure oil groove are connected with the plurality of first working cavities and are sequentially connected with the plurality of first working cavities as the first rotor rotates; the second stator is fixedly connected with the housing, a plurality of second needle teeth are uniformly distributed inside the second stator along the circumferential direction, the second rotor is eccentrically placed inside the second stator and contacts with the plurality of second needle teeth, and in the second stator, the A plurality of second working cavities are formed between the second rotor and the plurality of second needle teeth; the second distributor is connected to the second rotor in synchronous rotation, and a second high-pressure oil groove and a second low-pressure oil groove are provided at the distribution end of the second distributor, and the second high-pressure oil groove and the second low-pressure oil groove are selectively connected to the plurality of second working cavities, and when the second high-pressure oil groove and the second low-pressure oil groove are connected to the plurality of second working cavities, they are sequentially connected to the plurality of second working cavities as the second rotor rotates; the connection end of the first distributor and the connection end of the second distributor form a synchronously rotating selective connection through the variable control component; the P port is simultaneously connected to the The first high-pressure oil tank is connected to the second high-pressure oil tank, and the T port is connected to the first low-pressure oil tank and the second low-pressure oil tank at the same time; one end of the output shaft is connected to the first rotor in synchronous rotation, and the other end extends to the outside of the shell; when the second high-pressure oil tank and the second low-pressure oil tank are disconnected from the second working chambers, the connection end of the first distributor is disconnected from the connection end of the second distributor; when the second high-pressure oil tank and the second low-pressure oil tank are connected to the second working chambers, the connection end of the first distributor and the connection end of the second distributor are connected in synchronous rotation through the variable control component;

[0008] The advantages of the technical solution are as follows: two interfaces, port P and port D, are designed. Port P is used to transport high-pressure media, and port D is used to transport low-pressure media. The first and second distributors are disconnected and connected to achieve the conversion between low-speed heavy load and high-speed light load.

[0009] The disadvantages of this technical solution are: it is necessary to design two interfaces on the upper part of the rear shell, it is necessary to select two media with different densities, and it is necessary to rely on the opening and closing of the first distributor and the second distributor to realize the load conversion, which causes serious hysteresis during conversion and the valve body structure volume is also larger. Summary of the invention

[0010] The problem to be solved by the present invention is that the prior art configures multiple conveying and receiving interfaces or different density media to perform high and low pressure conversion, which results in obvious conversion delay and a relatively large structure volume.

[0011] In order to solve the above technical problems, the present invention provides a front flange assembly and a cycloid stator-rotor mechanism for providing multiple high- and low-pressure volume chambers, characterized in that it also includes a rear baffle valve body assembly and a rear housing distribution assembly for controlling the alternating flow of high- and low-pressure hydraulic oils to achieve switching of the high-pressure cycloid motor between low speed and high speed, and the front flange assembly, the cycloid stator-rotor mechanism, the rear baffle valve body assembly and the rear housing distribution assembly are connected and fixed by bolts.

[0012] Since the present invention designs a rear baffle valve body assembly and a rear housing distribution assembly inside the high-pressure gerotor motor, the high-pressure gerotor motor can switch between low speed and high speed by controlling the alternating flow of high- and low-pressure hydraulic oils, thereby solving the problems of obvious conversion hysteresis and large structural volume in the prior art of configuring multiple conveying and receiving interfaces or media of different densities for high- and low-pressure conversion. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] Figure 1 The overall structural cross-section diagram of a high-voltage cycloidal motor with high- and low-speed conversion functions.

[0014] Figure 2 The figure is a cross-sectional view of the valve body of a high-pressure gerotor motor with high-low speed conversion function.

[0015] Figure 3 This is a top structural diagram of the valve body of a high-pressure gerotor motor with high- and low-speed conversion functions.

[0016] Figure 4 Schematic diagram of the rear diaphragm valve body assembly of a high-pressure gerotor motor with high-low speed conversion function.

[0017] Figure 5 This is a schematic diagram of the structure of one side of the distribution plate of a high-voltage cycloidal motor with high-low speed conversion function.

[0018] Figure 6 It is a schematic diagram of the side structure of the distribution plate of a high-voltage cycloidal motor with high-low speed conversion function.

[0019] Figure 7 This is a schematic diagram of the structure on the other side of the distribution plate of a high-voltage cycloid motor with high-to-low speed conversion function.

[0020] Figure 8 It is a schematic diagram of the rear partition body structure of a high-voltage cycloidal motor with high-to-low speed conversion function.

[0021] Fig. 9 It is a schematic diagram of the bottom structure of the valve body of a high-pressure cycloidal motor with high-low speed conversion function.

[0022] Fig.10 It is a schematic diagram of the connection between the valve body and the distribution plate of a high-pressure gerotor motor with high-low speed conversion function.

[0023] In the figure: 1, front flange body; 2, front baffle; 3, output shaft; 11, bolt; 13, front flange assembly; 17, cycloid stator and rotor mechanism; 21, rear housing body; 23, stator ring; 25, pin teeth; 27, outer cycloid rotor; 28, distribution shaft; 31, linkage shaft; 35-36, annular hole; 45, valve body; 47, distribution plate; 48, rear baffle body; 49, center ring; 50, screw; 51, oil inlet; 53, oil outlet; 55 / 65, fan-shaped sink channel; 57 / 71, annular fluid chamber; 67, compensation plate ;77, axial flow channel hole;79, rear housing distribution assembly;81 / 83, seal;87, rear partition valve body assembly;89, transverse hole;91-92, joint;93-101, annular cavity;107, slide valve;109 / 111 / 113 / 115, step surface;117, pilot control chamber;119, compression spring;192, through hole;193-201, channel hole;211 / 213 / 215 / 217 / 219 / 221, connecting hole;231-239, flow channel hole;241-249, annular groove. DETAILED DESCRIPTION

[0024] The present invention relates to a high-voltage cycloid motor with high-low speed conversion function, such as Figure 1-10 The high-pressure gerotor motor shown in the figure includes a front flange assembly 13, a gerotor stator and rotor mechanism 17, a rear partition valve body assembly 87 and a rear housing flow distribution assembly 79; the above-mentioned components are connected by a plurality of bolts 11 ( Figure 1 Only one of them is shown in the figure) for connection and fixation.

[0025] like Figure 1-10 As shown, the front flange assembly 13 includes a front flange body 1, a front partition plate 2, an output shaft 3, a linkage shaft 31, and a distribution shaft 28.

[0026] like Figure 1-10As shown, the cycloid stator-rotor mechanism 17 is composed of a stator ring 23 with multiple semi-cylindrical holes, an epicycloid rotor 27 generated by a short-amplitude epicycloid, and multiple cylindrical needle teeth 25 in the semi-cylindrical holes of the stator ring 23; the epicycloid rotor 27 is eccentrically arranged in the stator ring 23, and the number of teeth of the outer teeth of the epicycloid rotor 27 is one less than that of the needle teeth 25, thereby allowing the epicycloid rotor 27 to rotate while revolving around the central orbit of the stator ring 23; the outer teeth of the epicycloid rotor 27 are in contact with the cylindrical needle teeth 25, thereby forming a plurality of expansion (high-pressure) volume chambers and contraction (low-pressure) volume chambers.

[0027] like Figure 1-10 As shown, the linkage shaft 31 is arranged inside the front flange body 1, and drum splines are respectively provided at both ends of the linkage shaft 31. The spline at one end of the linkage shaft 31 is connected to the inner spline of the outer cycloid rotor 27 of the cycloid stator-rotor mechanism 17, and the spline at the other end of the linkage shaft 31 is connected to the inner spline of the output shaft 3.

[0028] like Figure 1-10 As shown, the rear diaphragm valve body assembly 87 includes the rear diaphragm body 48 , the center ring 49 , the valve body 45 , the sliding valve 107 and the distribution shaft 28 .

[0029] like Figure 1-10 As shown, the distribution shaft 28 is arranged inside the rear partition valve body assembly 87, and drum splines are respectively provided at both ends of the distribution shaft 28. The spline at one end of the distribution shaft 28 is connected to the inner spline of the outer cycloid rotor 27.

[0030] like Figure 1-10 As shown, one end of the rear baffle body 48 is provided with flow channel holes (231, 232, 233, 234, 235, 236, 237, 238, 239), and the other end of the rear baffle body 48 is provided with an annular groove (241, 242, 243, 244, 245, 246, 247, 248, 249), the flow channel holes and the annular grooves are connected in sequence (for example: the flow channel hole 231 is connected with the annular groove 241, the flow channel hole 232 is connected with the annular groove 242, ...), and the interior of the rear baffle body 48 is provided with annular holes (35, 36) side by side.

[0031] like Figure 1-10As shown, the valve body 45 is fixed to the rear partition body 48 by a plurality of screws 50, and a transverse hole 89 and a through hole 192 are provided in the valve body 45, and both ends of the transverse hole 89 are sealed by joints (91, 92); a plurality of annular cavities (93, 94, 95, 96, 97, 98, 99, 100, 101) are formed inside the transverse hole 89; a slide valve 107 is arranged inside the transverse hole 89, and the slide valve 107 has a plurality of step surfaces (109, 111, 113, 115); a pilot control chamber 117 is formed between the step surface 115 and the joint 91, and is used to receive a pilot pressure signal to directly control the movement of the slide valve 107 between two operating positions; a spring chamber is formed between the step surface 109 and the joint 92, and a compression spring 119 is provided inside the spring chamber.

[0032] like Figure 1-10 As shown, a plurality of channel holes (193, 194, 195, 196, 197, 198, 199, 200, 201) are provided in the valve body 45, and the channel holes are connected to the annular cavities in sequence (for example: the channel hole 193 is connected to the annular cavity 93, the channel hole 194 is connected to the annular cavity 94, ...), and the channel holes (193, 196, 199) are connected through the through hole 192.

[0033] like Figure 1-10 As shown, the bottom of the valve body 45 is provided with connecting holes (211, 213, 215, 217, 219, 221), the annular groove 242 is connected with the connecting hole 211, the annular groove 245 is connected with the connecting hole 213 through the annular hole 36, the annular groove 248 is connected with the connecting hole 215, the flow channel hole 232 is connected with the connecting hole 217, the flow channel hole 235 is connected with the connecting hole 219 through the annular hole 35, and the flow channel hole 238 is connected with the connecting hole 221.

[0034] like Figure 1-10 As shown, the rear housing distribution assembly 79 includes the rear housing body 21, the distribution plate 47, and the compensation plate 67; the distribution plate 47 is evenly provided with eight spaced fan-shaped sink groove flow channels (55, 65) on the circumference, and the internal spline of the distribution plate 47 is connected to the other end of the distribution shaft 28.

[0035] like Figure 1-10 As shown, a hydraulic oil inlet 51 and a hydraulic oil return port 53 are provided at the upper end of the rear housing body 21, and the distribution plate 47 is arranged inside the rear housing body 21 and forms an annular fluid chamber 57 therewith, and the annular fluid chamber 57 is connected to the eight fan-shaped sink channels 55 on the distribution plate 47.

[0036] like Figure 1-10As shown, the compensation plate 67 is fixed inside a hole inside the rear shell body 21 and is arranged adjacent to the distribution plate 47, and is supported by multiple springs inside the hole; an annular fluid chamber 71 is formed between the compensation plate 67 and the rear shell body 21; a plurality of axial flow channel holes 77 are provided in the compensation plate 67, and the axial flow channel holes 77 are connected to the fan-shaped sink groove flow channel 65 of the distribution plate 47.

[0037] like Figure 1-10 As shown, a seal (81, 83) is provided on the compensation disk 67 to prevent the annular fluid chambers (57, 71) from being connected; the annular fluid chamber 57 is connected to the oil inlet, and the annular fluid chamber 71 is connected to the oil return port.

[0038] like Figure 1-10 As shown, each flow channel hole is connected to the expansion (high pressure) volume chamber or the contraction (low pressure) volume chamber. When the epicycloid rotor 27 rotates and revolves around the center of the stator ring 23, the distribution shaft 28 simultaneously drives the distribution plate 47 to rotate. Each flow channel hole will alternately connect the high-pressure oil to the expansion (high pressure) volume chamber, and then the contraction (low pressure) volume chamber is connected to the flow channel hole to discharge the hydraulic oil back to the oil tank.

[0039] like Figure 1-10 As shown, the high-pressure gerotor motor is driven to switch between low speed (large torque) and high speed (small torque) by controlling the movement of the rear diaphragm valve body assembly 87 .

[0040] When using the high-voltage gerotor motor manufactured by the present invention:

[0041] Low-speed and high-torque working state: high-pressure oil enters the motor annular fluid chamber 57 through the oil inlet 51 on the rear housing 21, and enters the annular groove (242, 243, 244, 245) of the rear partition body 48 through the fan-shaped sink channel 55 on the distribution plate 47. At this time, there is no control signal in the pilot control chamber 117 of the valve body 45, and the slide valve 107 is in the initial position, such as Figure 2 As shown;

[0042] The annular cavity 94 is connected with the annular cavity 95, the annular cavity 97 is connected with the annular cavity 98, the channel hole 195 of the valve body 45 is connected with the annular cavity 95, the annular cavity 94 is connected with the channel hole 194, the channel hole 198 is connected with the annular cavity 98, the annular cavity 97 is connected with the channel hole 197, the high-pressure oil in the annular groove 242 on the rear partition body 48 flows into the channel hole 195 of the valve body 45 through the connecting hole 211, passes through the annular cavities 95, 94, and the channel hole 194, and flows into the connecting hole 217 of the rear partition body 48, the connecting hole 217 is connected with the flow channel hole 232, and the high-pressure oil enters the high-pressure volume chamber 29B of the cycloid stator-rotor mechanism 17; the annular groove 242 of the rear partition body 48 flows into the channel hole 195 of the valve body 45 through the connecting hole 211, passes through the annular cavities 95, 94, and the channel hole 194, and flows into the connecting hole 217 of the rear partition body 48, and the connecting hole 217 is connected with the flow channel hole 232, and the high-pressure oil enters the high-pressure volume chamber 29B of the cycloid stator-rotor mechanism 17; The high-pressure oil in the annular groove 241 enters the high-pressure volume chamber 29A of the cycloid stator-rotor mechanism 17 through the flow channel hole 231; the high-pressure oil in the annular groove 243 enters the high-pressure volume chamber 29C of the cycloid stator-rotor mechanism 17 through the flow channel hole 233; the high-pressure oil in the annular groove 244 enters the high-pressure volume chamber 29D of the cycloid stator-rotor mechanism 17 through the flow channel hole 234; the high-pressure oil entering the annular groove 245 passes through the annular hole 36 of the rear partition, the connecting hole 213, enters the channel hole 198 of the valve body, the annular cavity 98, 97, enters the channel hole 197, enters the connecting hole 219 of the rear partition body 48, the flow channel hole 235, and enters the high-pressure volume chamber 29E of the cycloid stator-rotor mechanism 17. 29F, 29G, 29H, 29J are low-pressure volume chambers (hydraulic oil is discharged from the motor housing). The low-pressure oil in the low-pressure volume chamber 29F flows through the flow channel hole 236 on the rear partition body 48 into the annular groove 246, the low-pressure oil in the low-pressure volume chamber 29G flows through the flow channel hole 237 on the rear partition body 48 into the annular groove 247, the low-pressure oil in the low-pressure volume chamber 29J flows through the flow channel hole 239 on the rear partition body 48 into the annular groove 249, and the low-pressure oil in the low-pressure volume chamber 29H flows through the flow channel hole 238 on the rear partition body 48 into the annular groove 249. The oil flows into the connecting hole 221, passes through the annular cavity 101 and the annular cavity 100 of the valve body 45, flows into the channel hole 200, enters the connecting hole 215 of the rear partition body 48, enters the annular groove 248, enters the low-pressure oil in the annular grooves 246, 247, 248, 249, flows into the fan-shaped sink groove flow channel 65 of the distribution plate 47, flows into the axial flow channel hole 77 of the compensation plate, flows into the annular fluid chamber 71, and flows into the oil outlet 53, forming a hydraulic cycle. The outer cycloid rotor 27 of the cycloid stator-rotor mechanism 17 rotates under the lateral force of the high-pressure oil, and drives the oil distribution shaft 28 through the inner spline of the outer cycloid rotor 27, and the distribution plate 47 rotates synchronously, so that the fan-shaped sink groove flow channel 65 on the distribution plate 47 and the annular groove on the rear partition body 48 form an alternating distribution, so that the high and low pressure oil chambers entering the volume chamber of the cycloid stator-rotor mechanism 17 change alternately;

[0043] High-speed and low-torque working state: When the motor needs to switch to high-speed and low-torque working state, the pilot control chamber 117 of the valve body 45 introduces a control signal, and the slide valve 107 moves to the left, such as Figure 3 At this time, the annular cavity 93 is connected with the annular cavity 94, the annular cavity 96 is connected with the annular cavity 97, and the annular cavity 99 is connected with the annular cavity 100. The high-pressure oil in the annular groove 242 on the rear partition body 48 is enclosed in the annular cavity 95 of the valve body 45, and the high-pressure oil in the annular groove 245 is enclosed in the annular cavity 98 of the valve body 45. Since the number of volume cavities involved in the work of the cycloid stator-rotor mechanism 17 is reduced, the motor displacement is reduced, the working speed is increased, and the torque is reduced.

[0044] It is to be understood that the present invention is described by some embodiments, and it is known to those skilled in the art that various changes or equivalent substitutions may be made to these features and embodiments without departing from the spirit and scope of the present invention. In addition, under the teachings of the present invention, these features and embodiments may be modified to adapt to specific circumstances and materials without departing from the spirit and scope of the present invention. Therefore, the present invention is not limited by the specific embodiments disclosed herein, and all embodiments falling within the scope of the claims of this application are within the scope of protection of the present invention.

Claims

1. A high-pressure cycloid motor with high-low speed conversion function, comprising a front flange assembly and a cycloid stator-rotor mechanism for providing a plurality of high- and low-pressure volume cavities, characterized in that: It also includes a rear baffle valve body assembly and a rear housing flow distribution assembly for controlling the alternating flow of high and low pressure hydraulic oils to achieve switching between low speed and high speed of the high pressure cycloidal motor. The front flange assembly, the cycloidal stator-rotor mechanism, the rear baffle valve body assembly and the rear housing flow distribution assembly are connected and fixed by bolts; the cycloidal stator-rotor mechanism consists of a stator ring, an outer cycloidal rotor and a plurality of pin teeth inside the stator ring; the outer cycloidal rotor is eccentrically arranged inside the stator ring, and the outer teeth of the outer cycloidal rotor have one less tooth than the pin teeth, thereby allowing the outer cycloidal rotor to revolve in an orbit around the center of the stator ring The front flange assembly includes a front flange body, a front baffle, an output shaft, a linkage shaft and a distribution shaft arranged in sequence; the linkage shaft is arranged inside the front flange body, and drum splines are respectively provided at both ends of the linkage shaft, the spline at one end of the linkage shaft is connected to the inner spline of the outer cycloid rotor of the cycloid stator and rotor mechanism, and the spline at the other end of the linkage shaft is connected to the inner spline of the output shaft; the rear baffle valve body assembly includes a rear baffle body, a center ring, a valve body, a sliding valve and a distribution shaft; the distribution shaft is arranged inside the rear baffle valve body assembly, and drum splines are respectively provided at both ends of the distribution shaft , one end of the distribution shaft is splined to the inner spline of the outer cycloid rotor; a flow channel hole is opened at one end of the rear partition body, and an annular groove is opened at the other end of the rear partition body. The flow channel hole and the annular groove are connected in sequence, and annular holes are opened side by side inside the rear partition body; the valve body is fixed to the rear partition body by multiple screws, and there is a transverse hole and a through hole in the valve body, and the two ends of the transverse hole are sealed by joints; multiple annular cavities are formed inside the transverse hole; the slide valve is arranged inside the transverse hole, and the slide valve has multiple step surfaces; a pilot control is formed between the step surface and the joint A control chamber is used to receive a pilot pressure signal to directly control the movement of the slide valve between two operating positions; a spring chamber is formed between the step surface and the joint, and a compression spring is arranged inside the spring chamber; a plurality of channel holes are arranged in the valve body, and the channel holes are connected with the annular chambers in sequence, and the channel holes are connected through through holes; a connecting hole is opened at the bottom of the valve body, the annular groove is connected with the connecting hole, the annular groove is connected with the connecting hole through the annular hole, the annular groove is connected with the connecting hole, the flow hole is connected with the connecting hole, the flow hole is connected with the connecting hole through the annular hole, and the flow hole is connected with the connecting hole.

2. The high-voltage cycloid motor with high-speed and low-speed conversion function according to claim 1 is characterized in that: The rear housing distribution assembly includes a rear housing body, a distribution plate, and a compensation plate; eight fan-shaped sink groove flow channels are evenly arranged at intervals on the circumference of the distribution plate, and the spline inside the distribution plate is connected to the other end of the distribution shaft; a hydraulic oil inlet and a hydraulic oil return port are provided at the upper end of the rear housing body, the distribution plate is arranged inside the rear housing body and forms an annular fluid chamber therewith, and the annular fluid chamber is connected to the eight fan-shaped sink groove flow channels on the distribution plate.

3. The high-voltage cycloid motor with high-speed and low-speed conversion function according to claim 2 is characterized in that: The compensation disk is fixed inside a hole inside the rear housing body and is arranged adjacent to the distribution disk. It is supported by multiple springs inside the hole. An annular fluid chamber is formed between the compensation disk and the rear housing body. A plurality of axial flow channel holes are arranged in the compensation plate, and the axial flow channel holes are communicated with the fan-shaped sink groove flow channels of the distribution plate.

4. The high-voltage cycloid motor with high-speed and low-speed conversion function according to claim 3 is characterized in that: The compensation disc is provided with a sealing member to prevent the annular fluid chambers from being connected; the annular fluid chamber is connected with the oil inlet, and the annular fluid chamber is connected with the oil return port.

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