Pump and vehicle

Abstract

The present invention provides a pump and a vehicle. The pump includes a housing, a rotating shaft, a motor part, a pump part and a bearing. The housing has a cavity, the rotating shaft is located in the cavity, the motor part and the pump part are respectively connected to the rotating shaft in a mating manner, the bearing is connected to the housing and is located between the motor part and the pump part. The bearing includes a body and a flexible support part. The body has a shaft hole, and the flexible support part is provided at at least one axial end of the body. The rotating shaft passes through the shaft hole and contacts the body and the flexible support part. The bearing in the present invention has a flexible support part, which can effectively buffer the radial offset force generated during the rotation of the rotating shaft driving the load, avoid the problem of local stress concentration on the bearing, reduce the wear of the bearing, enable flexible contact between the rotating shaft and the bearing, increase the contact area between the rotating shaft and the bearing, thereby reducing the surface pressure, decreasing the wear rate of the bearing, effectively reducing the damage rate of the bearing, and solving the problem of easy damage of the bearing caused by the rigid connection between the rotating shaft and the bearing in the related art.

Description

Technical Field

[0001] The present invention relates to the technical field of pump equipment, and in particular, to a pump and a vehicle. Background Art

[0002] In the machinery industry, in order to achieve low-friction operation, a clearance fit is usually provided between a sliding bearing and a rotating shaft.

[0003] However, during the rotation of the rotating shaft, due to the uncertainty of the axis center of the rotating shaft, the rotating shaft may be eccentrically loaded. At this time, the rotating shaft will contact the sliding bearing, thereby causing problems such as stress concentration and severe wear of the sliding bearing. Summary of the Invention

[0004] The present invention aims to solve at least one of the technical problems existing in the prior art or related technologies.

[0005] To this end, in a first aspect of the present invention, a pump is provided.

[0006] In a second aspect of the present invention, a vehicle is provided.

[0007] In view of this, according to the first aspect of the present invention, a pump is provided. The pump includes a housing, a rotating shaft, a motor part, a pump part, and a bearing. Among them, the housing has a cavity, the rotating shaft is located in the cavity, the motor part and the pump part are respectively connected to the rotating shaft in a matching manner, the bearing is connected to the housing and is located between the motor part and the pump part. The bearing includes a body and a flexible support part. The body has a shaft hole, the flexible support part is provided at at least one axial end of the body, the rotating shaft passes through the shaft hole and contacts the body and the flexible support part.

[0008] The pump provided by the present invention includes a housing, a rotating shaft, a motor part, a pump part and a bearing. The housing has a cavity, and the motor part and the pump part are arranged in the cavity. By means of the housing, it is ensured that the motor part and the pump part are not affected by the outside world and can operate normally. The pump part is arranged on one axial side of the rotating shaft, and the motor part is arranged on the other axial side of the rotating shaft. The pump part is matched with the rotating shaft. Specifically, the pump part is in interference fit with the rotating shaft, and the pump part can be driven by the rotating shaft to rotate. The bearing is located between the motor part and the pump part, and the motor part drives the pump part to rotate through the rotating shaft. Further, the bearing includes a body and a flexible support part. The body has a shaft hole, and a part of the rotating shaft is located in the shaft hole. The bearing provides a supporting effect for the rotating shaft. When the rotating shaft does not drive the load to rotate, there are gaps between the rotating shaft and the main body and the flexible support part. When the rotating shaft drives the load to rotate, the rotating shaft will move radially, resulting in changes in the gaps between the rotating shaft and the main body and the flexible support part. At this time, the pressure at the axial end of the bearing will be relatively large. Further, the body has two ends in the axial direction, and the flexible support part is arranged on at least one axial end of the body. During operation, when the rotating shaft has a radial offset load, it can not only contact the main body but also contact the flexible support part. The rotating shaft can transfer the radial offset load force to the flexible support part. Under the action of the radial offset load force, the flexible support part can deform compared with the main body, so as to effectively buffer the radial offset load force, avoid local stress concentration problems on the bearing, reduce the wear of the bearing, make the contact between the rotating shaft and the bearing flexible, increase the contact area between the rotating shaft and the bearing, thereby reducing the surface pressure, reducing the wear rate of the bearing, effectively reducing the damage rate of the bearing, and solving the problem that the bearing is easily damaged due to the rigid connection between the rotating shaft and the bearing in the related art.

[0009] In a possible design, further, the flexible support part is arranged around the shaft hole, and the flexible support part has a shaft channel communicating with the shaft hole. The shaft channel is used to accommodate the rotating shaft.

[0010] In this design, the flexible support part is arranged around the shaft hole, that is, there is a flexible support part in the circumferential direction of the rotating shaft. When the rotating shaft drives the load to rotate, the direction of the radial offset load force received by the rotating shaft may change at any time in the circumferential direction, that is, the rotating shaft will receive radial offset load forces with multiple direction changes. No matter which direction the radial offset load force of the rotating shaft faces, there will be a corresponding flexible support part to provide flexible support for it, providing an all-round deformation buffer space for the rotating shaft, so that the rotating shaft can be flexibly connected to the bearing in all directions of 360°, and further effectively buffer the radial offset load forces from all directions, thereby reducing the surface pressure, reducing the wear rate of the bearing, and effectively reducing the damage rate of the bearing.

[0011] Among them, the flexible support portion itself forms a shaft channel, and the shaft channel communicates with the shaft hole. The rotating shaft is not only located in the shaft hole but also in the shaft channel. That is to say, the rotating shaft can not only contact the inner wall of the shaft hole but also the inner wall of the shaft channel, effectively increasing the contact area between the bearing and the rotating shaft, reducing the surface pressure, and reducing the damage rate of the bearing.

[0012] It should be noted that the flexible support portion is a cylinder, or the flexible support portion is in a necked-down shape in the axial direction away from the body, that is, a part of the flexible support portion can contact the rotating shaft.

[0013] In a possible design, further, the shaft channel is a cylindrical channel, and the inner diameter of the cylindrical channel is equal to the aperture of the shaft hole.

[0014] In this design, the shaft channel is a cylindrical channel, and the inner diameter of the cylindrical channel is equal to the aperture of the shaft hole. That is, when the rotating shaft does not drive the load to rotate, the gap between the rotating shaft and the flexible support portion is equal to the gap between the rotating shaft and the body. Then, when the rotating shaft drives the load to rotate, the rotating shaft can first contact the flexible support portion at the axial end of the body, so that the radial offset force of the rotating shaft can be buffered and released by the flexible support portion first, so that the radial offset force can be released by the flexible support portion as much as possible first and will not be transmitted to the body, thereby further improving the flexible connection performance between the whole bearing and the rotating shaft.

[0015] In a possible design, further, the radial thickness t of the flexible support portion is greater than or equal to 0.5 mm and less than or equal to 4 mm.

[0016] In this design, when the flexible support portion is arranged around the shaft hole and forms a shaft channel, the thickness of the flexible support portion in the direction perpendicular to the axial direction is the radial thickness t of the flexible support portion, which satisfies the above range. When 0.5 mm ≤ t ≤ 4 mm, the maximum stress value I of the bearing max is relatively low, which can prevent the damage phenomenon caused by excessive bearing stress. The flexible support portion can provide sufficient deformation to effectively buffer the radial offset force of the rotating shaft, thereby reducing the maximum stress of the bearing.

[0017] It should be noted that the thickness of the flexible support portion can be an equal-thickness structure or an unequal-thickness structure. The equal-thickness / unequal-thickness here includes the equal-thickness situation of the flexible support portion in the axial and circumferential directions. As long as the radial thickness of the flexible support portion meets the requirements of this vertical numerical range, the buffer effect that the flexible support portion can generate can effectively buffer the radial offset force brought by the rotating shaft, reduce the maximum stress of the bearing, ensure the safe use performance of the bearing, and extend the service life of the bearing.

[0018] In a possible design, further, the axial height of the flexible support part is h, and the sum of the axial heights of the flexible support part and the body is H, where 0.02H ≤ h ≤ 0.5H.

[0019] In this design, the axial height of the flexible support part is h, and the sum of the axial heights of the flexible support part and the body is H. When the axial height h of the flexible support part and the axial height H of the bearing satisfy the above relationship, the maximum stress value I of the bearing at this time max has the most significant downward trend and can provide the optimal buffer deformation amount for the rotating shaft. When h > 0.5H, the maximum stress value I of the bearing at this time max changes gently, and the provided buffer deformation amount is limited. At the same time, when the proportion of the axial height of the flexible support part is too large, the proportion of the axial thickness of the main body must be too small. At this time, it is very difficult for the whole bearing to ensure the supporting effect on the rotating shaft. That is to say, for the rotating shaft, considering comprehensively the flexible buffer effect provided by the flexible support part and the supporting effect provided by the main body, it is more appropriate to make the axial thickness h of the flexible support part and the axial height H of the bearing satisfy the above range.

[0020] In a possible design, further, the flexible support part includes a flexible end face facing away from the body and a flexible inner side surface for contacting the rotating shaft. A transition surface is provided between the flexible end face and the flexible inner side surface, where the transition surface includes an inclined surface and / or a curved surface.

[0021] In this design, the flexible support part includes a flexible end face and a flexible inner side surface. The flexible end face is the axial end face facing away from the body, and the flexible inner side surface can contact the rotating shaft. The radial offset force on the rotating shaft is transmitted to the flexible support part through the flexible inner side surface. Among them, there is a transition surface between the flexible inner side surface and the flexible end face, and the transition surface is at least one of an inclined surface and a curved surface, which can avoid the formation of a sharp area between the flexible end face and the flexible inner side surface and avoid the wear problem caused by the scratching of the sharp area and the rotating shaft. At the same time, during the assembly process of the rotating shaft, the transition surface can also provide a certain guiding effect.

[0022] In addition, in order to further reduce the frictional wear between the rotating shaft and the bearing, lubricating oil is filled between the rotating shaft and the bearing, and the transition surface can well guide the lubricating oil, making the flow of the lubricating oil path between the rotating shaft and the bearing smoother.

[0023] In a possible design, further, the body and the flexible support part are of an integral structure.

[0024] In this design, the body and the flexible support part are specifically an integral structure. Since the integral structure has good mechanical properties, it can improve the connection strength between the body and the flexible support part. In addition, the body and the flexible support part can be integrally formed and mass-produced to improve the processing efficiency of the product and reduce the processing cost of the product. Moreover, by designing the body and the flexible support part as an integrally formed integral structure, the integrity of the bearing is improved, the number of parts is reduced, the installation process is reduced, the installation efficiency is improved, and the installation of the bearing is made more convenient and reliable.

[0025] In a possible design, further, the flexible support part includes a first support part and a second support part, and the first support part and the second support part are respectively arranged on both axial sides of the body.

[0026] In this design, the flexible support part specifically includes a first support part and a second support part. The first support part is arranged at one axial end of the main body, and the second support part is arranged at the other axial end of the main body, that is, the first support part and the second support part are located on both axial sides of the whole bearing. That is, the first support part and the second support part are the positions on the bearing that are first subjected to the radial offset load force, and can effectively buffer and release the radial offset load force in time, further ensuring the service life of the whole bearing and reducing wear. At the same time, the first support part and the second support part can effectively increase the flexible contact area between the rotating shaft and the bearing.

[0027] In a possible design, further, the bearing further includes a lubricating oil groove, and the lubricating oil groove is arranged on the body and the flexible support part. The lubricating oil groove is communicated with the shaft hole, and the lubricating oil groove is used to accommodate lubricating oil.

[0028] In this design, there is a lubricating oil groove on the body and the flexible support part. Specifically, the lubricating oil groove is arranged on the walls of the body and the flexible support part facing the rotating shaft. The lubricating oil groove is used to accommodate lubricating oil. That is to say, the gap between the rotating shaft and the bearing is filled with lubricating oil, that is, the rotating shaft and the bearing are separated by lubricating oil and do not come into direct contact, which can greatly reduce the frictional loss and surface wear. And the gap between the bearing and the rotating shaft is filled with lubricating oil, and the lubricating oil on the sliding surface will form an oil film to achieve fluid lubrication. The oil film also has a certain vibration absorption capacity, improving the service life of the bearing and the rotating shaft.

[0029] Among them, as the rotating shaft rotates, the lubricating oil in the lubricating oil groove will be coated on the surface of the rotating shaft. The lubricating oil groove plays a role in temporarily storing lubricating oil, making a fluid lubricating oil film formed between the bearing and the rotating shaft, and ensuring the reliable lubrication performance between the bearing and the rotating shaft.

[0030] Specifically, the bearing is a sliding bearing, which refers to a bearing that works under sliding friction. Compared with the form of rolling bearings, sliding bearings work smoothly, reliably and noiselessly.

[0031] Specifically, a portion of the body and a portion of the flexible support portion are respectively recessed in a direction away from the central axis of the shaft hole to form a lubricating oil groove.

[0032] In a possible design, further, the lubricating oil groove extends at least in the axial direction.

[0033] In this design, the lubricating oil groove extends at least axially, which can ensure that part of the rotating shaft located inside the bearing can be coated with the lubricating oil in the lubricating oil groove, further ensuring the formation of a fluid lubricating oil film between the bearing and the rotating shaft, thereby improving the reliable lubrication performance between the bearing and the rotating shaft.

[0034] Of course, the lubricating oil groove may also extend in any one of the circumferential direction and the radial direction or in any combination of directions.

[0035] When the lubricating oil groove extends in the radial direction, the radial depth of the lubricating oil groove at different positions is different. When the lubricating oil groove extends in the circumferential direction, the lubricating oil groove presents a zigzag extension shape on the inner wall surface of the bearing.

[0036] Specifically, the lubricating oil groove may be a straight groove extending axially, or a curved groove extending in a zigzag manner.

[0037] In a possible design, further, the lubricating oil groove extends axially and spirally to form a spiral oil groove.

[0038] In this design, the lubricating oil groove not only extends in the axial direction, but also extends in the circumferential spiral direction to form a spiral oil groove. The extension direction of the spiral oil groove is a combination of the axial direction and the circumferential direction. When the shaft rotates, the lubricating oil between the bearing and the shaft will also move accordingly. The spiral oil groove can adapt to the flow trend of the lubricating oil, making the flow of the lubricating oil path between the shaft and the bearing smoother.

[0039] In a possible design, further, the spiral oil groove includes a first notch and a second notch distributed in the axial direction, and a rotation angle of the first notch in the circumferential direction compared to the second notch is less than or equal to 300°.

[0040] In this design, the spiral oil groove includes two slots distributed in the axial direction, specifically a first slot and a second slot that are opposite to each other. The extension direction of the spiral oil groove includes an extension in the axial direction and an extension in the circumferential direction. The rotation angle of the first slot in the circumferential direction compared to the second slot is the rotation angle of the spiral oil groove in the circumferential direction. That is, the spiral oil groove does not surround the inner wall of the bearing in one circle, that is, it is less than one circle. While satisfying the function of guiding the lubricating oil, damage to the bearing structure itself can be avoided.

[0041] The rotation angle of the first notch in the circumferential direction compared to the second notch can also be expressed as the envelope angle of the spiral line of the spiral oil groove, that is, the envelope angle is less than 300°.

[0042] In a possible design, further, the lubricating oil groove includes an oil guiding section in a cross-section perpendicular to the axial direction. The oil guiding section includes a first end point M and a second end point N facing away from each other. Along the direction from the first end point to the second end point, the distance between the oil guiding section and the central axis O first increases and then decreases.

[0043] In this design, the lubricating oil groove includes an oil guiding section located in a cross-section perpendicular to the axial direction. The oil guiding section is the line segment formed by the groove wall of the lubricating oil groove in this cross-section. After the lubricating oil enters the lubricating oil groove, it can flow better under the guidance of the groove wall. The oil guiding section includes a first end point and a second end point facing away from each other. The lubricating oil enters the lubricating oil groove at the first end point, then flows along the oil guiding section, and then leaves the lubricating oil groove at the second end point. Among them, the distance between the first end point M of the oil guiding section and the central axis O is L1, the distance between the second end point N of the oil guiding section and the central axis O is L3, and the distance between any point at the middle position of the oil guiding section and the central axis O is L2, satisfying L2 > L1 and L2 > L3. That is to say, the lubricating oil in the lubricating oil groove realizes from shallow to deep and then to shallow, so as to realize the smooth flow of the lubricating oil.

[0044] In a possible design, further, the pump part includes a first pressure chamber, a second pressure chamber, a first oil groove, and a throttling groove. Among them, the pressure borne by the first pressure chamber is greater than the pressure borne by the second pressure chamber. At least a part of the first oil groove is opened towards the pump part on the body of the bearing, and the first oil groove is communicated with the first pressure chamber. The throttling groove is opened towards the pump part on the body, and the throttling groove communicates the lubricating oil groove of the bearing and the first oil groove.

[0045] In this design, the pump part includes a first pressure chamber and a second pressure chamber. The pressure borne by the first pressure chamber is greater than the pressure borne by the second pressure chamber. Further, the first pressure chamber can be a high-pressure chamber, and the second pressure chamber can be a low-pressure chamber.

[0046] Among them, the bearing is connected to the housing. The bearing is located between the motor part and the pump part. The bearing is sleeved on the rotating shaft. To a certain extent, the bearing can provide a supporting effect for the rotating shaft. The bearing and the rotating shaft are coaxially arranged. During the actual working process, the rotating shaft drives the pump part to rotate. Therefore, the pump part will exert a radial force on the rotating shaft. When the rotating shaft is subjected to the radial force, it will push the bearing to deflect to one side. At this time, the rotating shaft contacts the bearing, and the bearing will provide a supporting effect for the rotating shaft, so as to control the clearance of the rotating shaft within a reasonable range and facilitate the control of the axis center of the rotating shaft.

[0047] It should be noted that the bearing and the housing can be an integral structure or a split structure, and can be selected according to the actual situation.

[0048] Furthermore, at least a part of the first oil groove is provided on the axial end face of the bearing facing the pump portion. The first oil groove communicates with the first pressure chamber. Since the pressure in the first pressure chamber is relatively high, a part of the oil fluid will flow from the first pressure chamber into the first oil groove and then into the gap between the rotating shaft and the bearing, ensuring the lubrication performance between the bearing and the rotating shaft. It should be noted that the first oil groove can also be referred to as a high-pressure oil groove.

[0049] Furthermore, the throttle groove is opened on the axial end face of the bearing facing the pump portion. The throttle groove is used to communicate the first oil groove and the gap between the bearing and the rotating shaft. That is to say, the lubricating oil in the first pressure chamber first flows into the first oil groove and then flows into the gap between the bearing and the rotating shaft through the throttle groove. The throttle groove can effectively prevent too much lubricating oil from flowing into the gap between the bearing and the rotating shaft, thereby affecting the displacement of the pump.

[0050] Therefore, in order to ensure the fluid lubrication performance between the bearing and the rotating shaft, that is, to provide sufficient lubricating oil to the gap between the bearing and the rotating shaft, and at the same time ensure that the displacement of the pump portion will not be severely leaked, that is, the displacement of the pump will not be significantly affected by the lubricating oil fluid. By using the first oil groove and the throttle groove in cooperation, the lubrication requirements between the bearing and the rotating shaft can be achieved, and the flow rate of the lubricating oil inside the bearing will not be too large to reduce the displacement of the pump.

[0051] Specifically, the first oil groove can balance the pressure between the various cavities of the pump portion on the high-pressure side of the pump portion, making the pressures of the cavities on the high-pressure side similar, thereby reducing the noise and mechanical vibration during operation.

[0052] Furthermore, the flow cross-sectional area of the throttle groove is smaller than that of the first oil groove, so that the flow rate of the lubricating oil in the gap between the bearing and the rotating shaft can be controlled through the throttle groove.

[0053] In a possible design, furthermore, the pump further includes an avoidance groove and a third pressure chamber. The avoidance groove is opened on the pump portion facing the bearing, and a part of the rotating shaft and the first supporting portion of the bearing are located in the avoidance groove. The third pressure chamber is located between the rotating shaft, the first supporting portion and the pump portion. The third pressure chamber communicates with the throttle groove and the lubricating oil groove. Among them, the pressure borne by the third pressure chamber is greater than the pressure borne by the second pressure chamber and less than the pressure borne by the first pressure chamber.

[0054] In this design, when the bearing in the motor includes a first support portion facing the pump portion, in order to avoid the first support portion, the pump portion is provided with an avoidance groove, the rotating shaft and the first support portion of the bearing sleeved on the rotating shaft are both located in the avoidance groove, and a third pressure chamber is provided between the first support portion and the pump portion. The third pressure chamber not only connects the throttling groove and the lubricating oil groove located on the bearing to store the lubricating oil, but also can provide a deformation space for the first support portion. When the first support portion is subjected to a radial offset load and radial deformation occurs, the third pressure chamber can prevent the first support portion from rigidly contacting the pump portion and causing damage to the pump portion.

[0055] It is worth noting that the third pressure chamber can be called a medium-pressure chamber, that is, the pressure borne by the third pressure chamber is smaller than that of the first pressure chamber as a high-pressure chamber, and larger than that of the second pressure chamber as a low-pressure chamber.

[0056] In a possible design, the pump further includes an oil seal and an oil seal cavity, the oil seal sleeve is arranged on the rotating shaft, the oil seal is located on the side of the bearing away from the pump part, the oil seal cavity is located between the oil seal, the rotating shaft and the bearing, and the oil seal cavity is connected to the lubricating oil groove.

[0057] In this design, the bearing is connected to the housing, and the bearing can separate the cavity surrounded by the housing into a motor cavity and a pump cavity, so that the spatial layout can be more reasonable. The motor part is located in the motor cavity, and the pump part is located in the pump cavity. Among them, the oil seal is connected to the side of the bearing away from the pump part, and the oil seal sleeve is arranged on the rotating shaft. Specifically, the oil seal can isolate the motor cavity from the pump cavity, so that the working medium will not flow into the motor cavity, and will not affect the normal use of the motor part, the electronic control part and other components in the motor cavity. There is no need to set up other additional structures in the motor cavity to ensure that the parts in the motor cavity are corroded, so that the sealing performance of the pump is better, and the structure is simpler, which is conducive to reducing costs.

[0058] Furthermore, the oil seal, the bearing and the rotating shaft form an oil seal cavity, and the oil seal cavity is connected to the lubricating oil groove. The oil seal cavity formed by the oil seal, the bearing and the rotating shaft can store a portion of the lubricating oil, and the oil seal cavity is used to store the lubricating oil from the lubricating oil groove. By controlling the connection strength between the oil seal and the bearing, which is related to the pressure that the oil seal itself can withstand, the oil seal cavity can also play a buffering role, so that the lubricating oil in the oil seal cavity, the lubricating oil groove and the throttling groove is in a pressure-balanced state, which is conducive to ensuring the fluid lubrication performance of the rotating shaft and the bearing while ensuring the stability of the oil seal position.

[0059] In a possible design, further, a part of the body extends away from the pump part to form a mounting part, and the oil seal is located between the mounting part and the rotating shaft. The second support part of the bearing is located on the side of the oil seal facing the pump part, and an oil seal cavity is provided between the second support part, the oil seal, the rotating shaft and the body. There is a gap between the second support part and the oil seal.

[0060] In this design, a part of the main body of the bearing extends away from the pump portion to form an installation portion. The oil seal is installed between the installation portion and the rotating shaft. The installation portion can ensure the installation accuracy of the oil seal, with simple assembly, good sealing performance, and low cost.

[0061] Furthermore, the bearing further includes a second support portion that extends away from the pump portion. The second support portion is located between the oil seal and the main body. There is an oil seal cavity among the second support portion, the oil seal, the rotating shaft, and the main body, so that the oil seal cavity is communicated with the lubricating oil groove, realizing the communication of the lubricating oil path.

[0062] Furthermore, there is a gap between the second support portion and the oil seal, that is, the second support portion and the oil seal do not contact. When the rotating shaft drives the load to rotate, the second support portion receives a radial offset force from the rotating shaft. The second support portion deforms independently to buffer and release the radial offset force, and will not transfer the offset force to the oil seal, ensuring the sealing performance of the oil seal for the motor cavity and the pump cavity, and improving the structural stability.

[0063] In a possible design, furthermore, the pump further includes a pressure relief groove and a second oil groove. The pressure relief groove is arranged on the main body and the pressure relief groove communicates with the oil seal cavity. At least a part of the second oil groove is opened on the main body towards the pump portion, and the second oil groove communicates with the pressure relief groove and the second pressure cavity respectively.

[0064] In this design, the pressure relief groove is arranged on the bearing, and the pressure relief groove is used to communicate the oil seal cavity and the second pressure cavity. The pressure relief groove here can adopt the form of a through hole, so that both ends of the through hole can communicate the second pressure cavity and the oil seal cavity. Since the pressure in the second pressure cavity is relatively small, the pressure in the oil seal cavity can be better released, not only relying on the oil seal cavity itself to buffer the pressure of the oil fluid.

[0065] Furthermore, by arranging the pressure relief groove on the bearing, a complete lubricating oil path of the bearing can be formed. That is, the oil fluid in the first pressure cavity (high-pressure cavity) enters the first oil groove, then flows through the throttle groove into the gap between the bearing and the rotating shaft and the lubricating oil groove, fully lubricating the rotating shaft and the bearing to form an oil film to meet the requirements of fluid lubrication. After that, the lubricating oil will flow into the oil seal cavity, further flow into the second oil groove from the pressure relief groove, and finally return to the second pressure cavity (low-pressure cavity), so as to ensure that the pressure in the whole lubricating oil path will not be too high, that is, the pressure in the oil seal cavity will not be too high, avoiding the pressure exceeding the pressure limit that the oil seal can bear, ensuring the reliability of the position of the oil seal, effectively avoiding the oil seal detaching from the bearing under high pressure, resulting in lubricating oil leakage and unable to ensure the sealing performance between the motor cavity and the pump cavity.

[0066] According to the second aspect of the present invention, a vehicle is provided, including the pump provided by any of the above designs.

[0067] The vehicle provided by the present invention includes the pump provided by any of the above designs, and thus has all the beneficial effects of the pump, which will not be elaborated here.

[0068] It should be noted that the vehicle can be a traditional fuel vehicle or a new energy vehicle. Among them, new energy vehicles include pure electric vehicles, range-extended electric vehicles, hybrid vehicles, fuel cell electric vehicles, hydrogen engine vehicles, etc.

[0069] The additional aspects and advantages of the present invention will become apparent in the following description section or be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0070] The above and / or additional aspects and advantages of the present invention will become apparent and be readily understood from the description of the embodiments in conjunction with the following drawings, wherein:

[0071] Figure 1 shows a schematic structural diagram of a pump according to an embodiment of the present invention;

[0072] Figure 2 shows Figure 1 a partial enlarged view of the pump shown in FIG. at A according to an embodiment of the present invention;

[0073] Figure 3 shows a partial structural schematic diagram of a bearing in the pump according to an embodiment of the present invention;

[0074] Figure 4 shows a structural schematic diagram of a bearing in the pump according to an embodiment of the present invention;

[0075] Figure 5 shows one of the partial structural schematic diagrams of the pump according to an embodiment of the present invention;

[0076] Figure 6 shows another partial structural schematic diagram of the pump according to an embodiment of the present invention;

[0077] Figure 7 shows yet another partial structural schematic diagram of the pump according to an embodiment of the present invention;

[0078] Figure 8 shows a graph of the maximum stress of the bearing corresponding to different radial thicknesses of the flexible support portion in the bearing according to an embodiment of the present invention;

[0079] Figure 9 shows a graph of the maximum stress of the bearing corresponding to different axial heights of the flexible support portion in the bearing according to an embodiment of the present invention.

[0080] Wherein, Figures 1 to 7The corresponding relationship between the reference numerals and the component names in the drawings is as follows:

[0081] 100 Bearing, 102 Rotating shaft, 104 Body, 106 Flexible support part, 108 Shaft channel, 109 Shaft hole, 110 Flexible end face, 112 Flexible inner side face, 114 Transition face, 116 First support part, 118 Second support part, 120 Lubricating oil groove, 122 Oil guiding line segment

[0082] 200 Pump, 202 Pump part, 204 Housing, 206 Cavity, 208 First pressure chamber, 212 First oil groove, 214 Throttle groove, 216 Third pressure chamber, 218 Oil seal, 220 Oil seal cavity, 222 Mounting part, 224 Pressure relief groove, 226 Second oil groove, 228 Machine housing, 230 Base, 232 Pump cover, 234 Inlet port, 236 Outlet port, 238 First rotating part, 240 Second rotating part. Detailed implementation manners

[0083] In order to more clearly understand the above objects, features and advantages of the present invention, the present invention will be further described in detail below with reference to the drawings and specific implementation manners. It should be noted that, without conflict, the embodiments of the present application and the features in the embodiments can be combined with each other.

[0084] In the following description, many specific details are set forth in order to fully understand the present invention. However, the present invention can also be implemented in other ways different from those described herein. Therefore, the protection scope of the present invention is not limited by the specific embodiments disclosed below.

[0085] Next, refer to Figures 1 to 9 Describe the pump 200 and the vehicle provided according to some embodiments of the present invention.

[0086] According to a first aspect of the present invention, a pump 200 is provided. The pump 200 includes a housing 204, a rotating shaft 102, a motor part, a pump part 202 and a bearing 100, as Figure 1 , Figure 2 and Figure 3 shown, wherein the housing 204 has a cavity 206, the rotating shaft 102 is located in the cavity 206, the motor part and the pump part 202 are respectively connected to the rotating shaft 102 in a mating manner, the bearing 100 is connected to the housing 204 and is located between the motor part and the pump part 202. The bearing 100 includes a body 104 and a flexible support part 106. The body 104 has a shaft hole 109. The flexible support part 106 is provided at at least one axial end of the body 104. The rotating shaft 102 passes through the shaft hole 109 and contacts the body 104 and the flexible support part 106.

[0087] The pump 200 provided by the present invention includes a housing 204, a rotating shaft 102, a motor part, a pump part 202, and a bearing 100. The housing 204 has a cavity 206. The motor part and the pump part 202 are arranged in the cavity 206. By means of the housing 204, it is ensured that the motor part and the pump part 202 are not affected by the outside world and can operate normally. The pump part 202 is arranged on one axial side of the rotating shaft 102, and the motor part is arranged on the other axial side of the rotating shaft 102. The pump part 202 is matched with the rotating shaft 102. Specifically, the pump part 202 is in interference fit with the rotating shaft 102, and the pump part 202 can be driven by the rotating shaft 102 to rotate. The bearing 100 is located between the motor part and the pump part 202, and the motor part drives the pump part 202 to rotate through the rotating shaft 102. Further, the bearing 100 includes a body 104 and a flexible support part 106. The body 104 has a shaft hole 109, and a part of the rotating shaft 102 is located in the shaft hole 109. The bearing 100 provides a supporting effect for the rotating shaft 102. When the rotating shaft 102 does not drive the load to rotate, there are gaps between the rotating shaft 102 and the main body and the flexible support part 106. When the rotating shaft 102 drives the load to rotate, the rotating shaft 102 will move radially, resulting in changes in the gaps between the rotating shaft 102 and the main body and the flexible support part 106. At this time, the pressure at the axial end of the bearing 100 is relatively large. Further, the body 104 has two ends in the axial direction, and the flexible support part 106 is arranged on at least one axial end of the body 104. During operation, when the rotating shaft 102 has a radial offset load, it can not only contact the body 104 but also contact the flexible support part 106. The rotating shaft 102 can transmit the radial offset load force to the flexible support part 106. Under the action of the radial offset load force, the flexible support part 106 can deform relative to the body 104, thereby effectively buffering the radial offset load force, avoiding local stress concentration problems on the bearing 100, reducing the wear of the bearing 100, enabling flexible contact between the rotating shaft 102 and the bearing 100, increasing the contact area between the rotating shaft 102 and the bearing 100, thereby reducing the surface pressure, decreasing the wear rate of the bearing 100, effectively reducing the damage rate of the bearing 100, and solving the problem of easy damage of the bearing caused by the rigid connection between the rotating shaft and the bearing in the related art.

[0088] Further, as Figure 2 and Figure 3 shown, the flexible support part 106 is arranged around the shaft hole 109. The flexible support part 106 has a shaft channel 108 communicating with the shaft hole 109, and the shaft channel 108 is used to accommodate the rotating shaft 102.

[0089] In this embodiment, the flexible support portion 106 is disposed around the shaft hole 109, that is, the flexible support portion 106 is present in the circumferential direction of the rotating shaft 102. When the rotating shaft 102 drives the load to rotate, the direction of the radial offset force received by the rotating shaft 102 may change at any time in the circumferential direction, that is, the rotating shaft 102 will receive radial offset forces with directions changing in multiple directions. Regardless of the direction of the radial offset force of the rotating shaft 102, there will be a corresponding flexible support portion 106 to provide flexible support for it, providing an all-round deformation buffer space for the rotating shaft 102, so that the rotating shaft 102 can be flexibly connected to the bearing 100 in all directions of 360°, thereby effectively buffering the radial offset forces from various directions, reducing the surface pressure, reducing the wear rate of the bearing 100, and effectively reducing the damage rate of the bearing 100.

[0090] Wherein, the flexible support portion 106 itself forms a shaft channel 108, and the shaft channel 108 communicates with the shaft hole 109. The rotating shaft 102 is not only located in the shaft hole 109, but also located in the shaft channel 108. That is to say, the rotating shaft 102 can not only contact the inner wall of the shaft hole 109, but also contact the inner wall of the shaft channel 108, effectively increasing the contact area between the bearing 100 and the rotating shaft 102, reducing the surface pressure, and reducing the damage rate of the bearing 100.

[0091] It should be noted that the flexible support portion 106 is a cylinder, or the flexible support portion 106 is in a flared shape in the axial direction away from the body 104, that is, a part of the flexible support portion 106 can contact the rotating shaft 102.

[0092] Furthermore, as Figure 2 and Figure 3 shown, the shaft channel 108 is a cylindrical channel, and the inner diameter of the cylindrical channel is equal to the aperture of the shaft hole 109.

[0093] In this embodiment, the shaft channel 108 is a cylindrical channel, and the inner diameter of the cylindrical channel is equal to the aperture of the shaft hole 109. That is, when the rotating shaft 102 does not drive the load to rotate, the gap between the rotating shaft 102 and the flexible support portion 106 is equal to the gap between the rotating shaft 102 and the body 104. Then, when the rotating shaft 102 drives the load to rotate, the rotating shaft 102 can first contact the flexible support portion 106 located at the axial end of the body 104, so that the radial offset force of the rotating shaft 102 can be buffered and released by the flexible support portion 106 first, so that the radial offset force can be released by the flexible support portion 106 as much as possible first, and will not be transmitted to the body 104, thereby further improving the flexible connection performance between the overall bearing 100 and the rotating shaft 102.

[0094] Furthermore, as Figure 2 shown, the thickness t of the flexible support portion 106 in the direction perpendicular to the axial direction is greater than or equal to 0.5 mm and less than or equal to 4 mm.

[0095] In this embodiment, when the flexible support portion 106 is disposed around the shaft hole 109 and forms a shaft channel 108, the thickness of the flexible support portion 106 in the direction perpendicular to the axial direction, i.e., the radial thickness t of the flexible support portion 106, satisfies the above range. As Figure 8 shown, when 0.5 mm ≤ t ≤ 4 mm, the maximum stress value I of the bearing 100 max is relatively low, which can prevent the damage phenomenon caused by excessive stress of the bearing 100. The flexible support portion 106 can provide sufficient deformation to effectively buffer the radial offset force of the rotating shaft 102, thereby reducing the maximum stress of the bearing 100.

[0096] It should be noted that the thickness of the flexible support portion 106 can be an equal-thickness structure or an unequal-thickness structure. The equal thickness / unequal thickness referred to here includes the equal-thickness condition of the flexible support portion 106 in the axial and circumferential directions. As long as the radial thickness of the flexible support portion 106 meets the requirements of this vertical numerical range, the buffering effect that the flexible support portion 106 can generate can effectively buffer the radial offset force brought by the rotating shaft 102, reduce the maximum stress of the bearing 100, ensure the safe use performance of the bearing 100, and extend the service life of the bearing 100.

[0097] Furthermore, as Figure 2 shown, the axial height of the flexible support portion 106 is h, and the sum of the axial heights of the flexible support portion 106 and the body 104 is H, where 0.02H ≤ h ≤ 0.5H.

[0098] In this embodiment, as Figure 9 shown, the axial height of the flexible support portion 106 is h, and the sum of the axial heights of the flexible support portion 106 and the body 104 is H. When the axial height h of the flexible support portion 106 and the axial height H of the bearing 100 satisfy the above relationship, the maximum stress value I of the bearing 100 at this time max has the most significant downward trend and can provide the optimal buffering deformation amount for the rotating shaft 102. When h > 0.5H, the change of the maximum stress value I of the bearing 100 at this time max tends to be gentle, and the provided buffering deformation amount is limited. At the same time, when the axial height ratio of the flexible support portion 106 is too large, the axial thickness of the main body must be too small. At this time, it is very difficult for the bearing 100 as a whole to ensure the supporting effect on the rotating shaft 102. That is to say, for the rotating shaft 102, considering the flexible buffering effect provided by the flexible support portion 106 and the supporting effect provided by the main body, it is more appropriate to make the axial thickness h of the flexible support portion 106 and the axial height H of the bearing 100 satisfy the above range.

[0099] Furthermore, as Figure 3As shown, the flexible support portion 106 includes a flexible end face 110 facing away from the body 104 and a flexible inner side face 112 for contacting the rotating shaft 102. A transition face 114 is provided between the flexible end face 110 and the flexible inner side face 112, where the transition face 114 includes an inclined face and / or a curved face.

[0100] In this embodiment, the flexible support portion 106 includes a flexible end face 110 and a flexible inner side face 112. The flexible end face 110 is an axial end face facing away from the body 104, and the flexible inner side face 112 can contact the rotating shaft 102. The radial offset force on the rotating shaft 102 is transmitted to the flexible support portion 106 through the flexible inner side face 112. Among them, a transition face 114 is provided between the flexible inner side face 112 and the flexible end face 110, and the transition face 114 is at least one of an inclined face and a curved face, which can avoid the formation of a sharp area between the flexible end face 110 and the flexible inner side face 112 and avoid the wear problem caused by the scratching of the sharp area and the rotating shaft 102. At the same time, during the assembly process of the rotating shaft 102, the transition face 114 can also provide a certain guiding function.

[0101] In addition, in order to further reduce the frictional wear between the rotating shaft 102 and the bearing 100, lubricating oil is filled between the rotating shaft 102 and the bearing 100. The transition face 114 can well guide the lubricating oil, making the flow of the lubricating oil path between the rotating shaft 102 and the bearing 100 smoother.

[0102] Furthermore, the body 104 and the flexible support portion 106 are of an integral structure.

[0103] In this embodiment, the body 104 and the flexible support portion 106 are specifically of an integral structure. Because the integral structure has good mechanical properties, it can improve the connection strength between the body 104 and the flexible support portion 106. In addition, the body 104 and the flexible support portion 106 can be integrally formed and mass-produced to improve the processing efficiency of the product and reduce the processing cost of the product. And by designing the body 104 and the flexible support portion 106 as an integrally formed integral structure, the integrity of the bearing 100 is improved, the number of components is reduced, the installation process is reduced, the installation efficiency is improved, and the installation of the bearing 100 is made more convenient and reliable.

[0104] Furthermore, as Figure 1 and Figure 2 shown, the flexible support portion 106 includes a first support portion 116 and a second support portion 118, and the first support portion 116 and the second support portion 118 are respectively arranged on both axial sides of the body 104.

[0105] In this embodiment, the flexible support portion 106 specifically includes a first support portion 116 and a second support portion 118. The first support portion 116 is provided at one axial end of the main body, and the second support portion 118 is provided at the other axial end of the main body. That is, the first support portion 116 and the second support portion 118 are located on both axial sides of the entire bearing 100. That is, the first support portion 116 and the second support portion 118 are the positions on the bearing 100 that are first subjected to the radial offset force, and can effectively buffer and release the radial offset force in a timely manner, further ensuring the overall service life of the bearing 100 and reducing wear. At the same time, the first support portion 116 and the second support portion 118 can effectively increase the flexible contact area between the rotating shaft 102 and the bearing 100.

[0106] Further, as Figure 1 , Figure 2 and Figure 3 shown, the bearing 100 further includes a lubricating oil groove 120. The lubricating oil groove 120 is provided on the main body 104 and the flexible support portion 106. The lubricating oil groove 120 is communicated with the shaft hole 109, and the lubricating oil groove 120 is used to accommodate lubricating oil.

[0107] In this embodiment, the lubricating oil groove 120 is provided on the main body 104 and the flexible support portion 106. Specifically, the lubricating oil groove 120 is provided on the walls of the main body 104 and the flexible support portion 106 facing the rotating shaft 102. The lubricating oil groove 120 is used to accommodate lubricating oil. That is to say, the gap between the rotating shaft 102 and the bearing 100 is filled with lubricating oil. That is, the rotating shaft 102 and the bearing 100 are separated by lubricating oil and do not come into direct contact, which can greatly reduce frictional losses and surface wear. Moreover, the gap between the bearing 100 and the rotating shaft 102 is filled with lubricating oil, and the lubricating oil on the sliding surface will form an oil film to achieve fluid lubrication. The oil film also has a certain vibration absorption ability, improving the service life of the bearing 100 and the rotating shaft 102.

[0108] Among them, as the rotating shaft 102 rotates, the lubricating oil in the lubricating oil groove 120 will be coated on the surface of the rotating shaft 102. The lubricating oil groove 120 plays a role of temporarily storing lubricating oil, making a fluid lubricating oil film formed between the bearing 100 and the rotating shaft 102, and ensuring the reliable lubrication performance between the bearing 100 and the rotating shaft 102.

[0109] Specifically, the bearing 100 is a sliding bearing. The sliding bearing 100 refers to a bearing 100 that operates under sliding friction. Compared with the form of a rolling bearing 100, the sliding bearing 100 operates smoothly, reliably, and noiselessly.

[0110] Specifically, as Figure 1 , Figure 2 and Figure 3As shown, a portion of the body 104 and a portion of the flexible support portion 106 are respectively recessed in a direction away from the central axis of the shaft hole 109 to form a lubricating oil groove 120 .

[0111] Furthermore, if Figure 2 and Figure 3 As shown, the lubricating oil groove 120 extends at least in the axial direction.

[0112] In this embodiment, the lubricating oil groove 120 extends at least in the axial direction, which can ensure that part of the rotating shaft 102 located inside the bearing 100 can be coated with the lubricating oil in the lubricating oil groove 120, further ensuring that a fluid lubricating oil film is formed between the bearing 100 and the rotating shaft 102, thereby improving the reliable lubrication performance between the bearing 100 and the rotating shaft 102.

[0113] Of course, the lubricating oil groove 120 may also extend in any one of the circumferential direction and the radial direction or in any combination of directions.

[0114] When the lubricating oil groove 120 extends in the radial direction, the radial depths of the lubricating oil groove 120 at different positions are different. When the lubricating oil groove 120 extends in the circumferential direction, the lubricating oil groove 120 extends in a zigzag shape on the inner wall surface of the bearing 100 .

[0115] Specifically, the lubricating oil groove 120 may be a straight groove extending axially, or the lubricating oil groove 120 may be a curved groove extending in a zigzag manner.

[0116] Furthermore, if Figure 3 As shown, the lubricating oil groove 120 extends axially and spirally to form a spiral oil groove.

[0117] In this embodiment, the lubricating oil groove 120 not only extends in the axial direction, but also extends in the circumferential spiral direction to form a spiral oil groove. The extension direction of the spiral oil groove is a combination of the axial direction and the circumferential direction. When the rotating shaft 102 rotates, the lubricating oil between the bearing 100 and the rotating shaft 102 will also move accordingly. The spiral oil groove can adapt to the flow trend of the lubricating oil, so that the flow of the lubricating oil path between the rotating shaft 102 and the bearing 100 is smoother.

[0118] Furthermore, the spiral oil groove includes a first notch and a second notch distributed in the axial direction, and a rotation angle of the first notch in the circumferential direction compared to the second notch is less than or equal to 300°.

[0119] In this embodiment, the spiral oil groove includes two notches distributed axially, specifically including a first notch and a second notch facing away from each other. The extending direction of the spiral oil groove includes an axial extension and a circumferential extension. The circumferential rotation angle of the first notch relative to the second notch is the circumferential rotation angle of the spiral oil groove, that is, the spiral oil groove does not go around the inner wall of the bearing 100 for a full circle, that is, less than one full circle. Under the condition of satisfying the lubricating oil guiding function, damage to the structure of the bearing 100 itself can be avoided.

[0120] Among them, the circumferential rotation angle of the first notch relative to the second notch can also be expressed as the envelope angle of the spiral line of the spiral oil groove, that is, the envelope angle is less than 300°.

[0121] Furthermore, as Figure 4 shown, the lubricating oil groove 120 includes an oil guiding segment 122 in a cross-section perpendicular to the axial direction. The oil guiding segment 122 includes a first end point M and a second end point N facing away from each other. Along the direction from the first end point to the second end point, the distance between the oil guiding segment 122 and the central axis O first increases and then decreases.

[0122] In this embodiment, the lubricating oil groove 120 includes an oil guiding segment 122 in a cross-section perpendicular to the axial direction. The oil guiding segment is the line segment formed by the groove wall of the lubricating oil groove 120 in this cross-section. After the lubricating oil enters the lubricating oil groove 120, it flows better under the guidance of the groove wall. The oil guiding segment 122 includes a first end point and a second end point facing away from each other. The lubricating oil enters the lubricating oil groove 120 at the first end point, then flows along the oil guiding segment 122, and then leaves the lubricating oil groove 120 at the second end point. Among them, the distance between the first end point M of the oil guiding segment 122 and the central axis O is L1, the distance between the second end point N of the oil guiding segment 122 and the central axis O is L3, and the distance between any point at the middle position of the oil guiding segment 122 and the central axis O is L2, satisfying L2 > L1, L2 > L3. That is to say, the lubricating oil in the lubricating oil groove 120 realizes from shallow to deep and then shallow out, so as to realize the smooth flow of the lubricating oil.

[0123] As Figure 1 、 Figure 2 、 Figure 5 、 Figure 6 and Figure 7 shown, the pump 200 includes a pump part 202 and a housing 204. The pump part 202 is in contact with the rotating shaft 102 and can be driven by the rotating shaft 102 to rotate. The housing 204 has a cavity 206, and the cavity 206 is used to accommodate the pump part 202 and the motor part.

[0124] The pump 200 provided by the present invention includes a pump part 202 and a housing 204. The housing 204 has a cavity 206. The motor and the pump part 202 are arranged in the cavity 206. By means of the housing 204, it is ensured that the motor and the pump part 202 are not affected by the outside world and can operate normally. The pump part 202 is arranged on one axial side of the rotating shaft 102 and is matched with the rotating shaft 102. Specifically, the pump part 202 is in interference fit with the rotating shaft 102, and the pump part 202 can be driven by the rotating shaft 102 to rotate.

[0125] Among them, the housing 204 includes a machine shell 228, a pump cover 232 connected to one end of the machine shell 228, and a base 230 connected to the other end of the machine shell 228. The pump cover 232, the base 230 and the machine shell 228 form the cavity 206, and the machine shell 228 surrounds the outside of the motor part and the pump part 202. The machine shell 228 is connected to the bearing 100. The bearing 100 and the machine shell 228 can be integrally formed. Compared with the post-processing method, the connection strength is higher, the space can be saved, the overall height of the machine can be reduced, and the difficulty of the preparation process can be reduced, and the manufacturing cost can be reduced.

[0126] Further, as Figure 2 , Figure 5 and Figure 6 shown, the motor includes a motor part. The motor part is arranged at one end of the rotating shaft 102, the pump part 202 is arranged at the other end of the rotating shaft 102, and the bearing 100 of the motor is located between the motor part and the pump part 202. The pump part 202 includes a first pressure chamber 208, a second pressure chamber, a first oil groove 212 and a throttling groove 214. Among them, the pressure borne by the first pressure chamber 208 is greater than the pressure borne by the second pressure chamber. At least a part of the first oil groove 212 is opened towards the pump part 202 on the body 104 of the bearing 100, and the first oil groove 212 is communicated with the first pressure chamber 208. The throttling groove 214 is opened towards the pump part 202 on the body 104, and the throttling groove 214 communicates the lubricating oil groove 120 of the bearing 100 and the first oil groove 212.

[0127] In this embodiment, the motor includes a motor part. The motor part is arranged at one end of the rotating shaft 102, the pump part 202 is arranged at the other end of the rotating shaft 102, the bearing 100 is located between the motor part and the pump part 202, and the motor part can drive the pump part 202 to operate through the rotating shaft 102. The pump part 202 includes a first pressure chamber 208 and a second pressure chamber. The pressure borne by the first pressure chamber 208 is greater than the pressure borne by the second pressure chamber. Further, the first pressure chamber 208 can be a high-pressure chamber, and the second pressure chamber can be a low-pressure chamber.

[0128] Specifically, the pump section 202 includes a first rotating member 238 and a second rotating member 240. The first rotating member 238 is engaged with the rotating shaft 102. The second rotating member 240 is disposed outside the first rotating member 238. The first rotating member 238 can drive the second rotating member 240 to rotate. It can be understood that the rotating shaft 102 can drive the second rotating member 240 to operate through the first rotating member 238. By arranging the first rotating member 238 and the second rotating member 240, a first pressure chamber 208 and a second pressure chamber are formed. The first pressure chamber 208 is a high-pressure chamber, and the second pressure chamber is a low-pressure chamber.

[0129] It should be noted that the first rotating member 238 is an internal gear, and the second rotating member 240 is an external gear, that is, the pump section 202 is a gear pump 200. Specifically, during the meshing process of the gear pump 200, before the previous pair of teeth disengages from meshing, the next pair of teeth has already entered meshing. Each internal tooth surface contacts the external tooth surface to form a sealed cavity. As the internal gear rotates, the volume of the sealed cavity 206 will change. If the unloading channel cannot be connected, a trapped oil volume will be formed. Due to the very small compressibility of the liquid, when the trapped oil volume changes from large to small, the liquid in the trapped oil volume is squeezed, and the pressure rises sharply, far exceeding the working pressure of the gear pump 200. At the same time, the liquid in the trapped oil volume is also forced out from all leakable gaps, causing the rotating shaft 102 and the bearing 100 to bear a large impact load, increasing power loss, heating the oil, causing noise and vibration, and reducing the working stability and service life of the gear pump 200. When the trapped oil volume changes from small to large, a vacuum is formed, causing the air dissolved in the liquid to separate and generate bubbles, resulting in cavitation, noise, vibration, flow rate and pressure pulsation and other hazards. The method to eliminate the trapped oil phenomenon is to open unloading grooves on both end covers of the gear, so that when the closed volume decreases, the unloading groove is connected to the pressure oil chamber, and when the closed volume increases, it is connected to the suction oil chamber through the unloading groove.

[0130] Specifically, through the meshing of the conjugate curve tooth profiles of the internal gear and the external gear, each tooth contacts each other and drives the external gear to rotate in the same direction. The internal gear divides the inner cavity of the external gear into multiple working chambers. Due to the offset of the centers of the internal and external gears, the volumes of the multiple working chambers change as the rotor rotates. The area where the volume increases forms a certain vacuum, and the oil inlet 234 is arranged at this part. The pressure in the area where the volume decreases increases, and the oil outlet 236 is correspondingly arranged here.

[0131] Among them, the bearing 100 is connected to the housing 204. The bearing 100 is located between the motor part and the pump part 202. The bearing 100 is sleeved on the rotating shaft 102. To a certain extent, the bearing 100 can provide a supporting effect for the rotating shaft 102. The bearing 100 and the rotating shaft 102 are coaxially arranged. During the actual working process, the rotating shaft 102 drives the pump part 202 to rotate. Therefore, the pump part 202 will apply a force in the radial direction to the rotating shaft 102. When the rotating shaft 102 is subjected to the radial force, it will push the bearing 100 to deflect to one side. At this time, the rotating shaft 102 contacts the bearing 100, and the bearing 100 will provide a supporting effect for the rotating shaft 102, so that the clearance of the rotating shaft 102 can be controlled within a reasonable range, which is convenient for the control of the axis of the rotating shaft 102.

[0132] It should be noted that the bearing 100 and the housing 204 can be of an integral structure or a split structure, and can be set according to the actual situation.

[0133] Furthermore, at least a part of the first oil groove 212 is provided on the axial end face of the bearing 100 facing the pump part 202. The first oil groove 212 is communicated with the first pressure chamber 208. Since the pressure in the first pressure chamber 208 is relatively high, a part of the oil will flow from the first pressure chamber 208 into the first oil groove 212, and then flow into the gap between the rotating shaft 102 and the bearing 100 to ensure the lubrication performance between the bearing 100 and the rotating shaft 102. It should be noted that the first oil groove 212 can also be called a high-pressure oil groove.

[0134] Furthermore, the throttling groove 214 is opened on the axial end face of the bearing 100 facing the pump part 202. The throttling groove 214 is used to communicate the first oil groove 212 and the gap between the bearing 100 and the rotating shaft 102. That is to say, the lubricating oil in the first pressure chamber 208 first flows into the first oil groove 212, and then flows into the gap between the bearing 100 and the rotating shaft 102 through the throttling groove 214. The throttling groove 214 can effectively prevent too much lubricating oil from flowing into the gap between the bearing 100 and the rotating shaft 102, thereby affecting the displacement of the pump 200.

[0135] Therefore, in order to ensure the fluid lubrication performance between the bearing 100 and the rotating shaft 102, that is, to provide sufficient lubricating oil for the gap between the bearing 100 and the rotating shaft 102, and at the same time ensure that the displacement of the pump part 202 will not leak seriously, that is, the displacement of the pump 200 will not be significantly affected by the lubricating oil, through the combined use of the first oil groove 212 and the throttling groove 214, the lubrication requirements between the bearing 100 and the rotating shaft 102 can be achieved, and the flow rate of the lubricating oil inside the bearing 100 will not be too large to reduce the displacement of the pump 200.

[0136] Specifically, the first oil sump 212 can balance the pressure among the respective cavities of the pump section 202 in the high-pressure side of the pump section 202, making the pressures of the high-pressure side cavities similar, thereby reducing noise and mechanical vibration during operation.

[0137] Furthermore, the flow cross-sectional area of the throttling groove 214 is smaller than that of the first oil sump 212, so that the flow rate of the lubricating oil in the gap between the bearing 100 and the rotating shaft 102 can be controlled through the throttling groove 214.

[0138] Furthermore, as Figure 1 、 Figure 2 、 Figure 5 and Figure 6 shown, the pump 200 further includes an avoidance groove and a third pressure cavity 216. The avoidance groove is formed in the pump section 202 facing the bearing 100, and a part of the rotating shaft 102 and the first support portion 116 of the bearing 100 are located in the avoidance groove. The third pressure cavity 216 is located between the rotating shaft 102, the first support portion 116 and the pump section 202. The third pressure cavity 216 communicates with the throttling groove 214 and the lubricating oil groove 120. Among them, the pressure borne by the third pressure cavity 216 is greater than the pressure borne by the second pressure cavity and less than the pressure borne by the first pressure cavity 208.

[0139] In this embodiment, when the bearing 100 in the motor includes a first support portion 116 facing the pump section 202, in order to avoid the first support portion 116, the pump section 202 is provided with an avoidance groove. Both the rotating shaft 102 and the first support portion 116 of the bearing 100 sleeved on the rotating shaft 102 are located in the avoidance groove. There is a third pressure cavity 216 between the first support portion 116 and the pump section 202. The third pressure cavity 216 not only communicates with the throttling groove 214 and the lubricating oil groove 120 located on the bearing 100, playing a role in storing lubricating oil, but also can provide a deformation space for the first support portion 116. When the first support portion 116 is subjected to a radial offset force and undergoes radial deformation, the third pressure cavity 216 can prevent the first support portion 116 from making rigid contact with the pump section 202 and causing damage to the pump section 202.

[0140] It should be noted that the third pressure cavity 216 can be called the medium-pressure cavity, that is, the pressure borne by the third pressure cavity 216 is less than that of the first pressure cavity 208 as the high-pressure cavity and greater than that of the second pressure cavity as the low-pressure cavity.

[0141] Furthermore, as Figure 1 and Figure 2 shown, the pump 200 further includes a oil seal 218 and an oil seal cavity 220. The oil seal 218 is sleeved on the rotating shaft 102, and the oil seal 218 is located on the side of the bearing 100 away from the pump section 202. The oil seal cavity 220 is located between the oil seal 218, the rotating shaft 102 and the bearing 100, and the oil seal cavity 220 communicates with the lubricating oil groove 120.

[0142] In this embodiment, the bearing 100 is connected to the housing 204. The bearing 100 can divide the cavity 206 surrounded by the housing 204 into a motor cavity and a pump cavity, thereby making the spatial arrangement more reasonable. The motor part is located in the motor cavity, and the pump part 202 is located in the pump cavity. Among them, the oil seal 218 is connected to the side of the bearing 100 facing away from the pump part 202, and the oil seal 218 is sleeved on the rotating shaft 102. Specifically, the oil seal 218 can isolate the motor cavity from the pump cavity, so that the working medium will not flow into the motor cavity and will not affect the normal use of components such as the motor part and the electronic control part in the motor cavity. There is no need to additionally set other structures in the motor cavity to ensure that the components in the motor cavity are not corroded, making the sealing performance of the pump 200 better, and at the same time the structure is simpler, which is beneficial to reducing costs.

[0143] Furthermore, the oil seal 218, the bearing 100 and the rotating shaft 102 form an oil seal cavity 220, and the oil seal cavity 220 communicates with the lubricating oil groove 120. The oil seal cavity 220 formed by the oil seal 218, the bearing 100 and the rotating shaft 102 can store a part of the lubricating oil. The oil seal cavity 220 is used to store the lubricating oil from the lubricating oil groove 120. By controlling the connection strength between the oil seal 218 and the bearing 100, the connection strength is related to the pressure that the oil seal 218 itself can withstand, and the oil seal cavity 220 can also play a buffering role, so that the lubricating oil in the oil seal cavity 220, the lubricating oil groove 120 and the throttling groove 214 is in a pressure equilibrium state. On the premise of ensuring the position stability of the oil seal 218, it is beneficial to ensure the fluid lubrication performance between the rotating shaft 102 and the bearing 100.

[0144] Furthermore, as Figure 2 shown, a part of the body 104 extends away from the pump part 202 to form a mounting part 222, and the oil seal 218 is located between the mounting part 222 and the rotating shaft 102. The second support part 118 of the bearing 100 is located on the side of the oil seal 218 facing the pump part 202, and there is an oil seal cavity 220 between the second support part 118, the oil seal 218, the rotating shaft 102 and the body 104. Among them, there is a gap between the second support part 118 and the oil seal 218.

[0145] In this embodiment, a part of the body 104 of the bearing 100 extends away from the pump part 202 to construct a mounting part 222. The oil seal 218 is installed between the mounting part 222 and the rotating shaft 102. The mounting part 222 can ensure the installation accuracy of the oil seal 218, with simple assembly, good sealing performance and low cost.

[0146] Further, the bearing 100 further includes a second support portion 118 facing away from the pump portion 202. The second support portion 118 is located between the oil seal 218 and the body 104. There is an oil seal cavity 220 between the second support portion 118, the oil seal 218, the rotating shaft 102 and the body 104, so that the oil seal cavity 220 communicates with the lubricating oil groove 120, realizing the connection of the lubricating oil path.

[0147] Further, there is a gap between the second support portion 118 and the oil seal 218, that is, the second support portion 118 and the oil seal 218 do not contact. When the rotating shaft 102 drives the load to rotate, the second support portion 118 receives a radial offset force from the rotating shaft 102. The second support portion 118 deforms independently to buffer and release the radial offset force, and will not transfer the offset force to the oil seal 218, ensuring the sealing performance of the oil seal 218 for the motor cavity and the pump cavity, and improving the structural stability.

[0148] Further, as Figure 2 and Figure 5 shown, the pump 200 further includes a pressure relief groove 224 and a second oil groove 226. The pressure relief groove 224 is provided on the body 104, and the pressure relief groove 224 communicates with the oil seal cavity 220. At least a part of the second oil groove 226 is opened on the body 104 facing the pump portion 202. The second oil groove 226 communicates with the pressure relief groove 224 and the second pressure chamber respectively.

[0149] In this embodiment, the pressure relief groove 224 is provided on the bearing 100, and the pressure relief groove 224 is used to communicate the oil seal cavity 220 and the second pressure chamber. The pressure relief groove 224 here can be in the form of a through hole, so that both ends of the through hole can communicate the second pressure chamber and the oil seal cavity 220. Since the pressure in the second pressure chamber is relatively small, the pressure in the oil seal cavity 220 can be better released, not only relying on the oil seal cavity 220 itself to buffer the pressure of the oil fluid.

[0150] Further, by providing the pressure relief groove 224 on the bearing 100, a complete lubricating oil path of the bearing 100 can be formed, that is, the oil fluid in the first pressure chamber 208 enters the first oil groove 212, then flows through the throttling groove 214 into the gap between the bearing 100 and the rotating shaft 102 and the lubricating oil groove 120, lubricating the rotating shaft 102 and the bearing 100 sufficiently to form an oil film to meet the requirements of fluid lubrication. After that, the lubricating oil will flow into the oil seal cavity 220, further flow into the second oil groove 226 from the pressure relief groove 224, and finally return to the second pressure chamber, so as to ensure that the pressure in the entire lubricating oil path will not be too high, that is, the pressure in the oil seal cavity 220 will not be too high, avoiding the pressure exceeding the pressure limit that the oil seal 218 can bear, ensuring the reliability of the position of the oil seal 218, and effectively avoiding the oil seal 218 detaching from the bearing 100 under high pressure, resulting in lubricating oil leakage and unable to ensure the sealing performance between the motor cavity and the pump cavity.

[0151] Among them, the bearing 100 includes a main body 104 and a flexible support portion 106. The main body 104 has a shaft hole 109, and a part of the rotating shaft 102 is located in the shaft hole 109. The bearing 100 provides a supporting function for the rotating shaft 102. When the rotating shaft 102 does not drive the load to rotate, there are gaps between the rotating shaft 102 and the main body and the flexible support portion 106. When the rotating shaft 102 drives the load to rotate, the rotating shaft 102 will move radially, resulting in changes in the gaps between the rotating shaft 102 and the main body and the flexible support portion 106. At this time, the pressure at the axial end of the bearing 100 will be relatively large. Further, the main body 104 has two ends in the axial direction, and the flexible support portion 106 is provided on at least one axial end of the main body 104. During operation, when the rotating shaft 102 has a radial offset load, it can not only contact the main body 104 but also contact the flexible support portion 106. The rotating shaft 102 can transfer the radial offset load to the flexible support portion 106. Under the action of the radial offset load, the flexible support portion 106 can deform relative to the main body 104, thereby effectively buffering the radial offset load, avoiding local stress concentration problems on the bearing 100, reducing the wear of the bearing 100, making the contact between the rotating shaft 102 and the bearing 100 flexible, increasing the contact area between the rotating shaft 102 and the bearing 100, thereby reducing the surface pressure, reducing the wear rate of the bearing 100, effectively reducing the damage rate of the bearing 100, and solving the problem of easy damage of the bearing caused by the rigid connection between the rotating shaft and the bearing in the related art.

[0152] Further, as Figure 2 and Figure 3 shown, the flexible support portion 106 is arranged around the shaft hole 109. The flexible support portion 106 has a shaft channel 108 communicating with the shaft hole 109, and the shaft channel 108 is used to accommodate the rotating shaft 102.

[0153] In this embodiment, the flexible support portion 106 is arranged around the shaft hole 109, that is, the flexible support portion 106 is provided in the circumferential direction of the rotating shaft 102. When the rotating shaft 102 drives the load to rotate, the direction of the radial offset load received by the rotating shaft 102 may change at any time in the circumferential direction, that is, the rotating shaft 102 will receive radial offset loads with directions changing in multiple directions. No matter which direction the radial offset load of the rotating shaft 102 faces, there will be a corresponding flexible support portion 106 to provide flexible support for it, providing an all-round deformation buffer space for the rotating shaft 102, so that the rotating shaft 102 can be flexibly connected to the bearing 100 in all directions of 360°, and then effectively buffering the radial offset loads from various directions, thereby reducing the surface pressure, reducing the wear rate of the bearing 100, and effectively reducing the damage rate of the bearing 100.

[0154] Among them, the flexible support portion 106 itself forms a shaft channel 108, and the shaft channel 108 communicates with the shaft hole 109. The rotating shaft 102 is not only located in the shaft hole 109 but also in the shaft channel 108. That is to say, the rotating shaft 102 can not only contact the inner wall of the shaft hole 109 but also the inner wall of the shaft channel 108, effectively increasing the contact area between the bearing 100 and the rotating shaft 102, reducing the surface pressure, and reducing the damage rate of the bearing 100.

[0155] It should be noted that the flexible support portion 106 is a cylinder, or the flexible support portion 106 is in a flared shape in the axial direction away from the body 104, that is, a part of the flexible support portion 106 can contact the rotating shaft 102.

[0156] Furthermore, the pump 200 further includes an electric control portion located in the cavity 206. The rotor of the motor and the rotating shaft form a rotating member, and a heat dissipation impeller is provided on the side of the rotating member away from the pump portion 202. The rotating member can drive the heat dissipation impeller to rotate to disturb the air flow in the cavity 206, improving the heat dissipation performance of the pump 200.

[0157] According to the second aspect of the present invention, a vehicle is provided, including the pump 200 provided by any of the above designs.

[0158] The vehicle provided by the present invention includes the pump 200 provided by any of the above designs, and thus has all the beneficial effects of the pump 200, which will not be elaborated here.

[0159] It should be noted that the vehicle can be a traditional fuel vehicle or a new energy vehicle. Among them, the new energy vehicle includes a pure electric vehicle, an extended-range electric vehicle, a hybrid vehicle, a fuel cell electric vehicle, a hydrogen engine vehicle, etc.

[0160] In the present invention, the term "a plurality of" refers to two or more, unless otherwise clearly defined. Terms such as "installed", "connected", "connected", "fixed", etc. should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral connection; "connected" can be a direct connection or an indirect connection through an intermediate medium. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0161] In the description of this specification, the description of terms such as "one embodiment", "some embodiments", "specific embodiments", etc. means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or instance. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0162] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. A pump, characterized in that, include: A housing having a cavity; A rotating shaft is located in the cavity; The motor part and the pump part are respectively connected with the rotating shaft; A bearing connected to the housing and located between the motor portion and the pump portion, the bearing comprising: A body having an axial hole; A flexible support portion is provided at least one axial end of the body, the rotating shaft is passed through the shaft hole and is in contact with the body and the flexible support portion; The bearing further comprises a lubricating oil groove, and the lubricating oil groove is provided on the body and the flexible support portion; The pump section includes a first pressure chamber and a second pressure chamber; A throttling groove, the throttling groove is opened on the main body toward the pump part; The pump further comprises a relief groove and a third pressure chamber; The avoidance groove is opened in the pump part toward the bearing, and a part of the rotating shaft and the first supporting part of the bearing are located in the avoidance groove; The third pressure chamber is located between the rotating shaft, the first support portion of the bearing and the pump portion, and the third pressure chamber is connected to the throttling groove and the lubricating oil groove. The pressure borne by the third pressure chamber is greater than the pressure borne by the second pressure chamber, and less than the pressure borne by the first pressure chamber.

2. The pump according to claim 1, characterized in that The flexible support portion is arranged around the shaft hole, and the flexible support portion has a shaft channel communicated with the shaft hole, and the shaft channel is used to accommodate the rotating shaft.

3. The pump according to claim 2, characterized in that The shaft channel is a cylindrical channel, and the inner diameter of the cylindrical channel is equal to the aperture of the shaft hole.

4. The pump according to claim 1, characterized in that The radial thickness t of the flexible support portion is greater than or equal to 0.5 mm and less than or equal to 4 mm.

5. The pump according to claim 1, characterized in that The axial height of the flexible support portion is h, and the sum of the axial heights of the flexible support portion and the body is H, wherein 0.02H≤h≤0.5H.

6. The pump according to claim 1, characterized in that The flexible support portion includes a flexible end surface facing away from the body and a flexible inner side surface for contacting the rotating shaft, and a transition surface is provided between the flexible end surface and the flexible inner side surface, wherein the transition surface includes an inclined surface and / or a curved surface.

7. The pump according to claim 1, characterized in that The main body and the flexible support portion are an integrated structure.

8. The pump according to claim 1, characterized in that The flexible support portion includes a first support portion and a second support portion, and the first support portion and the second support portion are respectively arranged on two axial sides of the body.

9. The pump according to any one of claims 1 to 8, characterized in that, The lubricating oil groove is communicated with the shaft hole, and the lubricating oil groove is used for accommodating lubricating oil.

10. The pump according to claim 9, characterized in that The lubricating oil groove extends at least in the axial direction.

11. The pump according to claim 9, characterized in that The lubricating oil groove extends axially and spirally to form a spiral oil groove.

12. The pump according to claim 11, characterized in that The spiral oil groove includes a first notch and a second notch distributed axially, and the rotational angle of the first notch relative to the second notch in the circumferential direction is less than or equal to 300°.

13. The pump according to claim 9, wherein the lubricating oil groove includes an oil guiding section in a cross-section perpendicular to the axial direction, the oil guiding section includes a first end point and a second end point facing away from each other, and along the direction from the first end point to the second end point, the distance between the oil guiding section and the central axis first increases and then decreases.

14. The pump according to claim 9, wherein the pressure borne by the first pressure chamber is greater than the pressure borne by the second pressure chamber; a first oil groove, at least a part of the first oil groove is opened towards the pump part on the body of the bearing, and the first oil groove communicates with the first pressure chamber; the throttling groove communicates the lubricating oil groove of the bearing and the first oil groove.

15. The pump according to claim 14, characterized in that, The pump further includes: a shaft seal, sleeved on the rotating shaft and located on the side of the bearing away from the pump part; a shaft seal chamber, located between the shaft seal, the rotating shaft and the bearing, and the shaft seal chamber communicates with the lubricating oil groove.

16. The pump according to claim 15, wherein a part of the body extends away from the pump part to form a mounting part, and the shaft seal is located between the mounting part and the rotating shaft; the second supporting part of the bearing is located on the side of the shaft seal facing the pump part, and there is the shaft seal chamber between the second supporting part, the shaft seal, the rotating shaft and the body; wherein, there is a gap between the second supporting part and the shaft seal.

17. The pump according to claim 15, wherein, The pump further includes: a pressure relief groove, provided on the body, and the pressure relief groove communicates with the shaft seal chamber; a second oil groove, at least a part of the second oil groove is opened towards the pump part on the body, and the second oil groove communicates with the pressure relief groove and the second pressure chamber respectively.

18. A vehicle, characterized in that, including: the pump according to any one of claims 1 to 17.

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