Wear-resistant structure for electronic oil pump and electronic oil pump

Abstract

The invention relates to the technical field of oil pump assemblies, and discloses a wear-resistant structure for an electronic oil pump and the electronic oil pump, the wear-resistant structure comprises a pump head module and a motor module, the pump head module comprises a pump cover, the pump cover is provided with a first oil guide structure, the first oil guide structure is used for introducing high-pressure oil and acting the high-pressure oil on the upper end face of an inner rotor, and the motor module comprises a machine shell. The machine shell is provided with a second oil guide structure, the second oil guide structure is used for introducing high-pressure oil and acting on the lower end face of the inner rotor, and axial load balance is achieved by arranging the oil guide structures on the upper end face and the lower end face of the inner rotor correspondingly; meanwhile, the pump cover is further provided with a first sliding bearing, the machine shell is further provided with a sliding bearing set distributed in the axial direction of the motor shaft, the first sliding bearing and the sliding bearing set form a lever structure with the sliding bearing, farthest from a load point, in the sliding bearing set as a fulcrum, and lateral loads are scientifically dispersed to the multiple bearings by means of the lever principle. The bearing pressure of a single bearing is greatly reduced, and the problem of eccentric wear of the shaft and the bearing chamber is effectively solved.

Description

Technical Field

[0001] This invention relates to the field of oil pump assembly technology, and more specifically to a wear-resistant structure for an electronic oil pump and the electronic oil pump itself. Background Technology

[0002] As a key component in the powertrain of new energy vehicles, the electronic oil pump's performance, operational reliability, NVH (noise, vibration, and harshness) performance, and manufacturing cost directly impact the overall performance of the powertrain system, thus attracting significant attention within the industry. Under high-pressure conditions, if the electronic oil pump cannot achieve effective oil pressure distribution, the inner and outer rotors and motor will bear the axial load generated by the high-pressure oil, leading to abnormal wear on the pump cover and housing end faces. Simultaneously, due to the oil supply principle of the cycloidal gear pump, a half-high-pressure area and a half-low-pressure area will naturally form inside the pump, causing the inner rotor and motor bearings to be subjected to the load of high-pressure oil on one side, resulting in uneven wear between the shaft and bearing housing, ultimately severely affecting the electronic oil pump's performance, operational reliability, and NVH performance.

[0003] To address the aforementioned lateral load issues, existing industry solutions have several drawbacks: commonly used ball bearings exhibit poor NVH performance under high-speed, high-load conditions and are costly to manufacture; some solutions add sliding bearings to the pump cover to share the load of the housing bearings, but due to installation space limitations, the pump cover bearing chamber is small, resulting in a high PV value (pressure-velocity value) for the bearings, which easily leads to severe wear after prolonged operation; another solution uses Al-Si-Zn-Sb casting alloys or powder metallurgy as pump cover materials, which can improve the wear resistance of the pump cover bearing chamber, but significantly increases the difficulty and cost of machining; yet another solution achieves decoupling between the motor shaft and the inner rotor through a flat fit to reduce the effect of the inner rotor's lateral force on the motor shaft, thereby reducing the lateral load on the shaft, but this flat fit solution requires an additional axial limiting structure for the motor, which not only increases assembly complexity but also raises component costs.

[0004] To address the axial load problem, the current common practice is to set symmetrical planes on the upper and lower end faces of the inner rotor in an attempt to make the pressure-bearing areas of the inner and outer rotors consistent. However, due to the small gap between the upper end faces, the oil pressure cannot be effectively distributed on the upper end face. The lower end face needs to be guided by an oil guide groove to introduce high-pressure oil into the bearing chamber of the housing, so that the pressure can only be effectively distributed on the lower end face. This cannot fundamentally solve the pressure difference problem between the upper and lower end faces, and the wear problem caused by axial load has not been effectively solved. Summary of the Invention

[0005] The purpose of this invention is to provide a wear-resistant structure for an electronic oil pump and an electronic oil pump in general. By setting oil guiding structures on the upper and lower end faces of the inner rotor, axial load balance is achieved. Furthermore, the first sliding bearing on the pump cover and the sliding bearing group distributed along the motor shaft axis of the housing form a lever structure. By using the lever principle, lateral loads are distributed, ultimately achieving the technical effect of low wear and high reliability. This solves the problem of wear on the pump cover and housing end faces caused by uneven axial pressure under high-pressure conditions of electronic oil pumps, as well as the problem of uneven wear between the shaft and bearing chamber caused by lateral loads.

[0006] This invention is achieved through the following technical solution: A wear-resistant structure for an electronic oil pump, comprising: A pump head module includes a pump cover, the pump cover being provided with a first oil guiding structure, the first oil guiding structure being used to introduce high-pressure oil and act on the upper end face of the inner rotor. A motor module includes a housing, the housing being provided with a second oil guiding structure, the second oil guiding structure being used to introduce high-pressure oil and act on the lower end face of the inner rotor; The pump cover is also provided with a first sliding bearing, and the housing is also provided with a sliding bearing group distributed along the motor shaft axis. The first sliding bearing and the sliding bearing group form a lever structure with the sliding bearing farthest from the load point in the sliding bearing group as the fulcrum, which is used to distribute the lateral load.

[0007] In this solution, the first oil guiding structure of the pump cover and the second oil guiding structure of the housing respectively introduce high-pressure oil into the upper and lower end faces of the inner rotor and form reverse axial pressure, effectively balancing the axial load generated under high-pressure conditions and solving the problem of abnormal wear on the pump cover and housing end faces caused by uneven pressure distribution in traditional structures. At the same time, by using the first sliding bearing of the pump cover and the sliding bearing group distributed along the motor shaft axis of the housing, a lever structure is constructed with the bearing farthest from the load point in the sliding bearing group as the fulcrum, realizing the scientific distribution of lateral load, greatly reducing the load pressure borne by a single bearing, avoiding the risk of uneven wear between the shaft and the bearing chamber, and the selection and layout design of the sliding bearings do not need to rely on high-cost ball bearings or special wear-resistant materials, taking into account both excellent NVH performance and cost economy.

[0008] As a further embodiment of the wear-resistant structure, the oil guiding path of the first oil guiding structure is larger than that of the second oil guiding structure, so that the pressure-bearing area of ​​the upper end face of the inner rotor is larger than that of its lower end face. This can compensate for the oil pressure drop caused by the difference in the oil guiding path, and ensure that when the high-pressure oil acts on the upper and lower end faces of the inner rotor, a balanced reverse axial pressure is formed, thereby offsetting the axial load caused by the uneven oil pressure distribution of the electronic oil pump under high-pressure conditions.

[0009] As a further embodiment of the wear-resistant structure, the first oil guiding structure includes an oil guiding groove on the high-pressure side of the pump cover end face. The pump cover has a protruding central boss at its center, which cooperates with the groove at the center of the inner rotor to form an oil storage cavity. The outlet of the oil guiding groove is connected to the oil storage cavity, which can quickly and stably introduce high-pressure oil from the high-pressure area of ​​the pump head into the oil storage cavity, thereby uniformly acting on the upper end face of the inner rotor, ensuring a balanced axial pressure distribution, and effectively compensating for the pressure drop caused by differences in the oil guiding path. At the same time, the oil storage cavity can realize temporary storage and buffering of oil, avoiding direct impact of high-pressure oil on the end face of the inner rotor and causing local wear, and can provide continuous and sufficient lubrication for the first sliding bearing, reducing frictional losses between the bearing and the motor shaft.

[0010] As a further embodiment of the wear-resistant structure, the pump cover has a central boss forming a pump cover bearing chamber. The first sliding bearing is connected to the pump cover bearing chamber by an interference fit. The pump cover bearing chamber protrudes from the end face of the pump cover and maintains radial and end face clearances with the groove of the inner rotor, providing continuous lubrication for the mating surfaces of the first sliding bearing and the inner rotor, and significantly reducing friction loss.

[0011] As a further embodiment of the wear-resistant structure, the second oil guiding structure includes a housing oil guiding groove located on the high-pressure side of the housing end face. The groove on the lower end face of the inner rotor mates with the groove on the upper end face of the housing to form a housing end oil storage cavity. The outlet of the housing oil guiding groove is connected to the housing end oil storage cavity, and the housing end oil storage cavity is connected to the front bearing chamber of the housing where the second sliding bearing is located. This enables the high-pressure oil to be introduced and stably stored from the high-pressure area of ​​the pump head to the lower end face of the inner rotor. This allows the high-pressure oil to act evenly on the lower end face of the inner rotor, forming a balanced reverse axial pressure in conjunction with the first oil guiding structure, effectively balancing the axial load to reduce end face wear. Furthermore, the connection between the housing end oil storage cavity and the front bearing chamber of the housing allows for the continuous supply of lubricating grease to the second sliding bearing, significantly reducing the frictional loss between the bearing and the motor shaft.

[0012] As a further embodiment of the wear-resistant structure, the inner wall of the front bearing chamber of the housing is provided with a spiral oil guide groove. The pitch of the spiral oil guide groove is consistent with the axial length of the front bearing chamber of the housing and covers the inner circumference of the front bearing chamber. With the driving force of the motor shaft rotation, the high-pressure oil in the oil storage chamber at the end of the housing can be evenly and continuously transported to the entire bearing chamber along the spiral path, ensuring that the entire circle of the second sliding bearing can be fully lubricated, avoiding the problem of aggravated wear caused by insufficient local lubrication. At the same time, the structural design of the spiral oil guide groove can also form a stable oil flow channel, which can not only remove the heat generated by the bearing operation and play a role in cooling and heat dissipation, but also flush impurities on the bearing surface through the oil flow, reducing the risk of abrasive wear.

[0013] As a further improvement to the wear-resistant structure, an enlarged bearing chamber oil reservoir is provided below the front bearing chamber of the housing. The spiral oil guide groove guides high-pressure oil into the bearing chamber oil reservoir, avoiding insufficient lubrication and aggravated wear caused by untimely oil supply under high-pressure conditions. At the same time, in conjunction with the directional oil guiding effect of the spiral oil guide groove, a stable oil circulation path can be formed, which not only improves lubrication efficiency but also helps to remove the heat generated by the bearing operation, achieving a cooling and heat dissipation effect.

[0014] As a further embodiment of the wear-resistant structure, the lower part of the bearing housing oil reservoir is also connected to the rear bearing housing of the housing. The rear bearing housing of the housing is clearance-fitted with the motor shaft. The clearance fit limits the oil flow rate, avoids excessive oil loss leading to a decrease in the overall pump output flow rate, and ensures that the oil forms a reasonable pressure distribution inside the bearing housing to help balance the axial load.

[0015] As a further embodiment of the wear-resistant structure, the housing is provided with a housing pressure relief hole, which is connected to the high-pressure area and the low-pressure area of ​​the housing respectively. After the high-pressure oil enters the motor cavity through the bearing chamber gap of the housing, it is discharged through the housing pressure relief hole, forming an oil circulation for motor cooling. In this way, the heat generated during motor operation can be carried away in time by the flowing oil, avoiding the problem of performance degradation or component damage of the motor due to high temperature. At the same time, the oil circulation can continuously flush out impurities inside the bearing chamber and motor cavity, reducing the risk of abrasive wear.

[0016] An electronic oil pump includes a controller module and a wear-resistant structure, wherein the controller module is connected to the housing of the wear-resistant structure and is located at one end away from the pump head module; The controller module includes a PCBA, a heat sink, and a mounting plate. The mounting plate is connected to the housing and isolates and seals the motor module from the PCBA. The heat sink is located between the mounting plate and the PCBA.

[0017] In summary, compared with the prior art, the present invention has the following main advantages and beneficial effects: 1. This invention introduces high-pressure oil to the upper and lower end faces of the inner rotor through the first oil guiding structure of the pump cover and the second oil guiding structure of the housing, respectively. With the matching of the pressure-bearing area of ​​the end face and the oil guiding path, dynamic balance of axial load can be achieved without relying on an additional pressure regulating device, avoiding abnormal wear of pump cover, housing and rotor components caused by uneven end face pressure in traditional structures. At the same time, a lever-type load distribution structure is constructed based on the first sliding bearing of the pump cover and the sliding bearing group distributed along the motor shaft axis of the housing. Using the bearing farthest from the load point in the sliding bearing group as the fulcrum, the lateral load is scientifically distributed to multiple bearings, which greatly reduces the bearing pressure of a single bearing and effectively solves the problem of uneven wear between the shaft and the bearing chamber. Moreover, the selection and layout of the sliding bearings take into account excellent NVH performance, avoiding the defects of high cost and high noise of traditional ball bearing solutions.

[0018] 2. This invention achieves stable delivery and temporary storage of high-pressure oil through the integrated design of the oil guide groove and the oil storage chamber. This provides continuous and sufficient lubrication for the bearings and allows the oil flow to carry away operating heat and flush away impurities, reducing the risk of abrasive wear. The matching design of the bearing chamber with the boss and groove, as well as the control of interference fit and clearance, ensures the stability of component installation and avoids the risk of motion interference, thus improving operational stability. At the same time, the design of the pressure relief hole in the housing relies on the oil pump's own oil pressure to form a cooling oil circulation for the motor, eliminating the need for an additional cooling system and further optimizing the economy and practicality of the overall structure. Attached Figure Description

[0019] The accompanying drawings, which are included to provide a further understanding of embodiments of the invention and form part of this application, do not constitute a limitation thereof. In the drawings: Figure 1 This is a schematic diagram of the overall structure of the present invention; Figure 2 This is a cross-sectional structural diagram of the present invention; Figure 3 This is a schematic diagram of the pump cover mounting surface structure; Figure 4 for Figure 2 A schematic diagram of the structure marked A in the middle; Figure 5 A schematic diagram of the mounting surface structure of the casing and pump body; Figure 6 for Figure 2 A schematic diagram of the structure marked B in the middle; Figure 7 This is a schematic diagram of the bearing housing. Figure 8 for Figure 2 A schematic diagram of the structure marked C.

[0020] The attached diagram shows the markings and corresponding component names: 1-Pump cover, 2-Pump cover bearing, 3-Inner rotor, 4-Outer rotor, 5-Pump body, 6-Rotor assembly, 6-1-Motor shaft, 7-Stator assembly, 8-Housing, 9-Mounting plate, 10-Heat plate, 11-PCBA, 12-Rear cover assembly, 1-1-Pump cover oil guide groove, 1-2-Pump cover oil storage chamber, 1-3-Pump cover center boss, 1-4-Pump cover bearing chamber, 1-5-Pump cover oil outlet, 1-6-Pump cover oil inlet, 1-7-Pump cover low-pressure area, 1-8-Pump cover high-pressure area, 8-1-Housing pressure relief hole, 8-2-Housing high-pressure area, 8-3-Housing low-pressure area, 8-4-Housing oil guide groove, 8-5-Housing front bearing chamber, 8-6-Spiral oil guide groove, 8-7-Bearing chamber oil storage cavity, 8-8-Housing rear bearing chamber, 8-9-Housing end oil storage cavity. Detailed Implementation

[0021] To make the objectives, technical solutions, and advantages of the present invention clearer, the present invention will be further described in detail below with reference to the embodiments and accompanying drawings. The illustrative embodiments and descriptions of the present invention are only used to explain the present invention and are not intended to limit the present invention. Example 1

[0022] This embodiment 1 provides a wear-resistant structure for an electronic oil pump, such as... Figures 2-6 As shown, the system includes a pump head module and a motor module. The pump head module includes a pump cover 1, an inner rotor 3, an outer rotor 4, and a pump body 5. The motor module includes a stator assembly 7, a housing 8, and a rotor assembly 6. The pump cover 1 is fixedly connected to the top of the pump body 5 by pump cover screws. The pump body 5 is positioned and connected to the housing 8 by positioning pins to ensure the relative position of the bearing chambers 1-4 of the pump cover and the bearing chambers of the housing 8. The inner rotor 3 and the outer rotor 4 are set in the sealed cavity formed by the pump cover 1, the pump body 5, and the housing 8, constituting the core pumping unit of the oil pump. The stator assembly 7 is press-fitted and fixed inside the housing 8. The rotor assembly 6 contains a solid motor shaft 6-1, which passes through the bearing chambers 1-4 of the pump cover and the front bearing chamber 8-5 and the rear bearing chamber 8-8 of the housing, achieving radial positioning.

[0023] Specifically, such as Figure 3 and Figure 4 As shown, the pump cover 1 is an integrally formed structure with an upwardly protruding central boss 1-3 at its center. A pump cover bearing chamber 1-4 is located at the center of this central boss 1-3. The pump cover bearing 2 is tightly fitted into the pump cover bearing chamber 1-4 via an interference fit, and the pump cover bearing chamber 1-4 protrudes from the upper end face of the pump cover 1 facing the inner rotor 3. To avoid interference between the pump cover bearing chamber 1-4 and the inner rotor 3, a circular groove is provided at the center of the inner rotor 3. A preset radial clearance and end face clearance are maintained between this groove and the pump cover bearing chamber 1-4. These clearances and the groove together constitute the pump cover oil storage cavity 1-2, used for temporary storage of lubricating and pressure regulating oil.

[0024] Meanwhile, the end face of the pump cover 1 is divided into a high-pressure zone 1-8 and a low-pressure zone 1-7, with corresponding oil outlet 1-5 and oil inlet 1-6. The oil outlet 1-5 is located in the high-pressure zone 1-8, and the oil inlet 1-6 is located in the low-pressure zone 1-7. An oil guide groove 1-1 is provided in the high-pressure zone 1-8 of the pump cover where the pump cover 1 mates with the inner rotor 3. One end of the oil guide groove 1-1 is connected to the oil pressure area of ​​the high-pressure zone 1-8, and the other end directly leads to the oil storage chamber 1-2, forming a complete first oil guide structure. This ensures that high-pressure oil can be quickly and stably introduced from the high-pressure zone 1-8 into the oil storage chamber 1-2 and evenly applied to the upper end face of the inner rotor 3.

[0025] The inner rotor 3 also has a through hole at its center, which is connected to the motor shaft 6-1 by an interference fit. This ensures that the torque of the motor rotor assembly 6 can be efficiently transmitted to the inner rotor 3, driving the inner rotor 3 to mesh and rotate with the outer rotor 4 to achieve the oil pumping function. At the same time, the pressure-bearing area of ​​the upper end face of the inner rotor 3 is designed to be slightly larger than that of the lower end face to compensate for the oil pressure drop caused by the longer oil guide path of the first oil guide structure (pump cover oil guide groove 1-1) compared to the second oil guide structure (machine housing oil guide groove 8-4).

[0026] Specifically, such as Figure 5 , Figure 6 , Figure 7 , Figure 8 As shown, the housing 8 is an integral die-cast structure with a circular groove at the center of its upper end face. This groove aligns with the circular groove on the lower end face of the inner rotor 3, forming a sealed oil storage chamber 8-9 at the housing end. A high-pressure area 8-2 is located on the end face of the housing 8 corresponding to the high-pressure area 1-8 of the pump cover, and a low-pressure area 8-3 is located corresponding to the low-pressure area 1-7 of the pump cover. An oil guide groove 8-4 is located on the high-pressure area 8-2 on the upper end face of the housing 8. One end of the oil guide groove 8-4 connects to the oil pressure area of ​​the high-pressure area 8-2, and the other end leads to the oil storage chamber 8-9 at the housing end, forming the core part of the second oil guiding structure.

[0027] Meanwhile, inside the housing 8, along the axial direction of the motor shaft 6-1, are sequentially arranged a front bearing chamber 8-5, a bearing chamber oil reservoir 8-7, and a rear bearing chamber 8-8. These three components are integrally formed, constituting the bearing support system of the housing. The front bearing chamber 8-5 houses a second sliding bearing, and its inner wall is provided with a spiral oil guide groove 8-6. The pitch of this spiral oil guide groove 8-6 is exactly the same as the axial length of the front bearing chamber 8-5, and it continuously covers the entire inner circumference of the front bearing chamber 8-5, ensuring that a complete oil film can be established through the oil guiding action of the spiral oil guide groove 8-6 when the motor shaft 6-1 rotates. The bearing chamber oil reservoir 8-7 is located below the front bearing chamber 8-5, and its diameter is larger than that of the front and rear bearing chambers 8-5 and 8-8, forming an expanded oil storage space. The lower end of the spiral oil guide groove 8-6 communicates with the bearing chamber oil reservoir 8-7, allowing high-pressure oil to be introduced into it for storage and buffering.

[0028] A third sliding bearing is installed in the rear bearing chamber 8-8 of the housing. Its inner wall lacks an oil guide groove, and it is assembled with the motor shaft 6-1 using a clearance fit. This design effectively limits the oil flow within the bearing chamber, preventing excessive oil loss. Furthermore, the side wall of the housing 8 in this embodiment is equipped with a housing pressure relief hole 8-1. One end of this hole connects to the high-pressure zone 8-2 of the housing, and the other end connects to the low-pressure zone 8-3. High-pressure oil seeps into the motor cavity through the gaps between the front bearing chamber 8-5, the bearing chamber oil reservoir 8-7, and the rear bearing chamber 8-8, and then flows back to the low-pressure zone 8-3 through the pressure relief hole 8-1, forming a complete oil circulation.

[0029] In this embodiment, when the electronic oil pump is working, high-pressure oil forms a stable high pressure in the high-pressure zone 1-8 of the pump cover and the high-pressure zone 8-2 of the housing. Through the pump cover oil guide groove 1-1 of the first oil guide structure, the high-pressure oil enters the pump cover oil storage chamber 1-2, acting evenly on the upper end face of the inner rotor 3, generating downward axial pressure. Simultaneously, through the housing oil guide groove 8-4 of the second oil guide structure, the high-pressure oil enters the housing end oil storage chamber 8-9, acting evenly on the lower end face of the inner rotor 3, generating upward axial pressure. Since the pressure-bearing area of ​​the upper end face of the inner rotor 3 is slightly larger than that of the lower end face, it precisely compensates for the pressure drop loss caused by the longer oil guide path of the first oil guide structure, making the axial pressure on the upper and lower end faces equal in magnitude and opposite in direction, achieving complete balance of axial load, and fundamentally eliminating abnormal wear caused by uneven axial pressure on the pump cover 1 and housing 8 end faces.

[0030] Meanwhile, due to the working principle of the cycloidal gear pump, the inner rotor 3 and motor shaft 6-1 in this embodiment will be subjected to lateral loads generated by high-pressure oil on one side. In this invention, the pump cover bearing 2 (first sliding bearing) is located above the inner rotor 3, and the front bearing chamber 8-5 (second sliding bearing) and the rear bearing chamber 8-8 (third sliding bearing) of the housing are distributed axially along the motor shaft 6-1 below the inner rotor 3, with the third sliding bearing being the bearing farthest from the inner rotor 3 (load point) in the sliding bearing group. When the lateral load acts on the motor shaft 6-1, the motor shaft 6-1 will slightly oscillate with the rear bearing chamber 8-8 of the housing as the fulcrum, forming a lever structure: the lever arm length of the pump cover bearing 2 is greater than the lever arm length from the inner rotor 3 to the fulcrum, and it can bear a larger proportion of the lateral load. At the same time, the front bearing chamber 8-5 and the rear bearing chamber 8-8 of the housing share the remaining lateral load. This design significantly reduces the load on a single bearing. Even though the housing 8 is made of conventional ADC12 aluminum alloy, the PV value of its bearing chamber can still meet the requirements for long-term operation, effectively avoiding the problem of uneven wear between the shaft and the bearing chamber.

[0031] In addition, the aforementioned high-pressure oil, while achieving axial pressure balance and lateral load distribution, constructs an efficient lubrication and cooling circulation system: the oil in the pump cover oil reservoir 1-2 continuously provides lubrication for the pump cover bearing 2, reducing frictional losses between the bearing and the motor shaft 6-1; the oil in the housing end oil reservoir 8-9 is guided into the bearing chamber oil reservoir 8-7 through the spiral oil guide groove 8-6, and then continuously supplied to the front bearing chamber 8-5 and the rear bearing chamber 8-8 of the housing, ensuring that all sliding bearings receive sufficient lubrication. Furthermore, the structural design of the spiral oil guide groove 8-6 allows for forced oil supply through the rotation of the motor shaft 6-1, ensuring uniform lubrication throughout the bearing. Simultaneously, the high-pressure oil penetrating the motor cavity carries away the heat generated by the stator assembly 7 and rotor assembly 6 during circulation, and is then discharged through the housing pressure relief hole 8-1, achieving efficient cooling of the motor and improving its operating efficiency and service life. Example 2

[0032] This embodiment provides an electronic oil pump, such as Figure 1 and Figure 2 As shown, the device includes a controller module and the wear-resistant structure described in Embodiment 1. The controller module is connected to the housing of the wear-resistant structure and is located at the end away from the pump head module. Specifically, the mounting plate 9 of the controller module is pressed into the middle of the housing 8 and is provided with a sealing structure, which together with the housing 8 isolates and seals the motor module and the controller module. The PCBA11 of the controller module is electrically connected to the motor module. The heat sink 10 is located between the mounting plate 9 and the PCBA11. The rear cover assembly 12 is fixedly connected to the end of the housing 8 away from the pump head module, forming protection for the controller module.

[0033] The specific embodiments described above further illustrate the purpose, technical solution, and beneficial effects of the present invention. It should be understood that the above description is only a specific embodiment of the present invention and is not intended to limit the scope of protection of the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A wear resistant structure for an electric oil pump, characterized by, The application relates to a pump head module and a motor module. The pump head module comprises a pump cover (1) provided with a first oil guide structure for introducing high-pressure oil liquid to the upper end surface of an inner rotor (3) and applying the high-pressure oil liquid to the upper end surface of the inner rotor (3). The motor module comprises a motor shell (8) provided with a second oil guide structure for introducing high-pressure oil liquid to the lower end surface of the inner rotor (3) and applying the high-pressure oil liquid to the lower end surface of the inner rotor (3). The pump cover (1) is further provided with a first sliding bearing, and the motor shell (8) is further provided with a sliding bearing group distributed along the motor shaft (6-1) in the axial direction; the first sliding bearing and the sliding bearing group form a lever structure with the sliding bearing farthest from a load point in the sliding bearing group as a fulcrum, and the lever structure is used for distributing lateral load.

2. A wear resistant structure for an electronic oil pump according to claim 1, wherein The oil guide path of the first oil guide structure is larger than the oil guide path of the second oil guide structure, so that the pressure receiving area of the upper end surface of the inner rotor (3) is larger than the pressure receiving area of the lower end surface of the inner rotor (3).

3. A wear resistant structure for an electronic oil pump according to claim 1, wherein The first oil guide structure comprises a pump cover oil guide groove (1-1) arranged on the high-pressure side of the end surface of the pump cover (1); the center of the pump cover (1) is provided with a pump cover center boss (1-3); the pump cover center boss (1-3) is matched with a groove in the center of the inner rotor (3) to form a pump cover oil storage cavity (1-2); and the outlet of the pump cover oil guide groove (1-1) is communicated with the pump cover oil storage cavity (1-2).

4. A wear resistant structure for an electronic oil pump according to claim 3, wherein The pump cover center boss (1-3) forms a pump cover bearing chamber (1-4); the first sliding bearing is connected in the pump cover bearing chamber (1-4) in an interference mode; the pump cover bearing chamber (1-4) protrudes from the end surface of the pump cover (1) and keeps a radial and end surface gap with the groove of the inner rotor (3).

5. A wear resistant structure for an electronic oil pump according to claim 1, wherein The second oil guide structure comprises a motor shell oil guide groove (8-4) arranged on the high-pressure side of the end surface of the motor shell (8); the groove on the lower end surface of the inner rotor (3) is matched with the groove on the upper end surface of the motor shell (8) to form a motor shell end oil storage cavity (8-9); the outlet of the motor shell oil guide groove (8-4) is communicated with the motor shell end oil storage cavity (8-9); and the motor shell end oil storage cavity (8-9) is communicated with a motor shell front end bearing chamber (8-5) where the sliding bearing group is arranged.

6. A wear resistant structure for an electronic oil pump according to claim 5, wherein The inner wall of the motor shell front end bearing chamber (8-5) is provided with a spiral oil guide groove (8-6); the pitch of the spiral oil guide groove (8-6) is consistent with the axial length of the motor shell front end bearing chamber (8-5) and covers the inner wall circumferential surface of the motor shell front end bearing chamber (8-5).

7. A wear resistant structure for an electronic oil pump according to claim 6, wherein The lower part of the motor shell front end bearing chamber (8-5) is further provided with a bearing chamber oil storage cavity (8-7) with an enlarged diameter; the spiral oil guide groove (8-6) guides the high-pressure oil liquid into the bearing chamber oil storage cavity (8-7).

8. A wear resistant structure for an electronic oil pump according to claim 7, wherein The lower part of the bearing chamber oil storage cavity (8-7) is further communicated with a motor shell rear end bearing chamber (8-8); and the motor shell rear end bearing chamber (8-8) is matched with the motor shaft (6-1) in a gap mode.

9. A wear resistant structure for an electronic oil pump according to claim 1, wherein The machine shell (8) is provided with a machine shell pressure relief hole (8-1) which respectively communicates with a machine shell high pressure area (8-2) and a machine shell low pressure area (8-3) of the machine shell (8), after high pressure oil liquid enters the motor cavity through the bearing chamber gap of the machine shell (8), the high pressure oil liquid is discharged through the machine shell pressure relief hole (8-1) to form oil liquid circulation for motor cooling.

10. An electric oil pump characterized by comprising: The control module is connected to the machine shell (8) of the wear-resistant structure and is located at an end away from the pump head module. The control module comprises a PCBA (11), a heat dissipation plate (10) and a placement plate (9), the placement plate (9) is connected to the machine shell (8) and seals the motor module from the PCBA (11), and the heat dissipation plate (10) is arranged between the placement plate (9) and the PCBA (11).

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