JP7350180B2 - Pump equipment and vehicles - Google Patents

Description

This application is based on the priority of the Chinese patent application filed with the Chinese Patent Office on September 3, 2020, whose application number is 202010913992.2 and whose invention title is "Pump device and vehicle", and on September 3, 2020. We claim the priority of the Chinese patent application filed with the Chinese Patent Office on May 3, 202021898979.6, and the title of the invention is "Pump device and vehicle", and the entire content thereof is incorporated by reference. This is incorporated herein by reference.

TECHNICAL FIELD Embodiments of the present application relate to the field of pump device technology, and specifically to pump devices and vehicles.

Generally, a pump device includes a motor section and a pump section, and the pump section can rotate in conjunction with a rotating shaft of the motor section, thereby realizing a compression function of the pump device. However, the problem arises that the rotating shaft rubs against other structures of the pump device during high-speed rotation, and in order to reduce wear on the rotating shaft, it is common practice to use oil from the pump section to lubricate the rotating shaft. However, it is a difficult problem to solve how to ensure that the lubrication requirements of the rotating shaft are met while not affecting the discharge rate of the pump device.

In order to solve at least one of the above technical problems, one object of embodiments of the present application is to provide a pump device.

Another object of embodiments of the present application is to provide a vehicle having a pump device as described above.

To achieve the above object, an embodiment of the first aspect of the present application provides a pump device including a housing, a motor part, a pump part, a first bearing, a first oil groove and a throttle groove. Here, the housing has a chamber. The motor section includes a rotating shaft that rotates around a central axis of the motor section. The pump section is provided on one side of the motor section in the axial direction and contacts the rotating shaft, so that the pump section can rotate in conjunction with the rotating shaft. The pump section includes a first pressure chamber and a second pressure chamber, and the pressure received by the first pressure chamber is greater than the pressure received by the second pressure chamber. The first bearing is connected to the housing and fitted onto the rotating shaft, and the first bearing is located between the motor section and the pump section. The first oil groove is provided on the first end face of the first bearing facing the pump section, and the first oil groove communicates with the first pressure chamber. The throttle groove is provided on the first end surface, and the throttle groove communicates between the first oil groove and the gap between the first bearing and the rotating shaft.

According to an embodiment of the pump device provided in the present application, the pump device includes a housing, a motor section, a pump section, a first bearing, a first oil groove, and a throttle groove. Here, since the housing has a chamber and the motor section and the pump section are provided within the chamber, the housing ensures that the motor section and the pump section can operate normally without being affected by the external environment. The motor section includes a rotating shaft that rotates around the central axis of the motor section, and the pump section is provided on one side of the motor section in the axial direction and contacts the rotating shaft. is an interference fit with the rotating shaft, and the pump section is rotatable in conjunction with the rotating shaft. This can be understood as the motor section driving and operating the pump section via the rotating shaft. The pump section includes a first pressure chamber and a second pressure chamber, the pressure received by the first pressure chamber is greater than the pressure received by the second pressure chamber, and the first pressure chamber may be a high pressure chamber. , the second pressure chamber may be a low pressure chamber.

Further, the first bearing is connected to the housing, the first bearing is located between the motor section and the pump section, the first bearing is fitted onto the rotating shaft, and the first bearing supports the rotating shaft to some extent. can play a role. Note that the first bearing can provide lubricating support to the rotating shaft, and since the axes of the first bearing and the rotating shaft overlap, the rotating shaft drives the pump part to rotate during actual operation. The pump section applies a radial force to the rotating shaft, and the rotating shaft pushes the first bearing to one side while receiving the radial force. At this time, the rotating shaft applies a radial force to the first bearing. In contact, the first bearing provides a supporting effect to the rotating shaft, which allows the play of the rotating shaft to be controlled within a reasonable range, thereby facilitating the control of the axis of the rotating shaft. .

Note that the first bearing is a sliding bearing, and the sliding bearing refers to a bearing that operates by sliding friction. Compared to rolling bearings, sliding bearings operate smoothly, reliably, and without noise. Under liquid lubrication conditions, the sliding surfaces are separated by lubricating oil and do not come into direct contact, reducing friction loss and surface wear. In addition, the gap between the sliding bearing and the rotating shaft is filled with lubricating oil, and the lubricating oil on the sliding surface forms a layer of oil, realizing fluid lubrication. It also has a certain vibration absorption capacity, extending the service life of the first bearing and the rotating shaft.

Furthermore, the first oil groove is provided on the first end face of the first bearing facing the pump part, and the first oil groove communicates with the first pressure chamber. The oil flows from the first pressure chamber into the first oil groove and then into the gap between the rotating shaft and the first bearing, thereby ensuring lubrication performance between the first bearing and the rotating shaft.

Further, the throttle groove is provided on the first end face, that is, the throttle groove is provided on the first end face of the first bearing facing the pump part, and the throttle groove is connected to the first oil groove, the first bearing, and the rotating shaft. It is used to communicate with the gap between the In other words, the oil in the first pressure chamber first flows into the first oil groove, and then flows through the throttle groove into the gap between the first bearing and the rotating shaft. It is possible to effectively prevent oil from flowing excessively into the gap with the rotating shaft and further affecting the discharge amount of the pump device.

Therefore, in order to ensure fluid lubrication performance between the first bearing and the rotating shaft, in other words, sufficient lubricating oil is provided in the gap between the first bearing and the rotating shaft, and the discharge amount of the pump part is In order to prevent large leaks, that is, to ensure that the discharge amount of the pump section is not significantly affected by the lubricating oil, the first oil groove and the throttle groove are used together. In addition to realizing the lubrication requirements between the bearing and the rotating shaft, the flow rate in the first bearing is also not too large, which would reduce the output of the pumping device.

Specifically, the first oil groove can balance the pressure between the storage chambers on the high-pressure side of the pump section, and as a result, the pressures of the storage chambers on the high-pressure side become close, reducing noise during operation. and mechanical vibrations can be reduced.

Furthermore, since the flow passage cross-sectional area of the throttle groove is less than the flow passage cross-sectional area of the first oil groove, the flow rate of lubricating oil within the gap between the first bearing and the rotating shaft can be controlled by the throttle groove.

Further, the above technical means provided in this application may further have additional technical features as described below.

In the above technical means, a portion of the inner wall of the first bearing is further recessed in a direction away from the rotating shaft to form a first lubricating groove communicating with the throttle groove.

In this technical means, the first lubricating groove is formed by recessing a part of the inner wall of the first bearing in a direction away from the rotating shaft, and the first lubricating groove communicates with the throttle groove. Because of the pressure difference, the oil in the first pressure chamber passes through the first oil groove and the throttle groove in order, and then flows into the gap between the first bearing and the rotating shaft, filling the first lubricating groove. With the rotation of the rotating shaft, the oil in the first lubricating groove is applied to the surface of the rotating shaft, where the first lubricating groove plays the role of temporarily storing the lubricating oil, thereby A fluid lubricating oil film is formed between the inner wall of the first bearing and the rotating shaft, thereby further ensuring reliable lubricity between the rotating shaft and the bearing. Furthermore, the first lubricating groove is bored in the first bearing along the axial direction, the first lubricating groove communicates with the shaft hole of the first bearing, one end of the first lubricating groove communicates with the throttle groove, and the first lubricating groove communicates with the shaft hole of the first bearing. The other end of the first lubricating groove extends toward the motor chamber. Furthermore, the number of first lubrication grooves is at least one and can be installed flexibly according to actual lubrication requirements.

In any one of the above technical means, furthermore, the ratio of the flow passage cross-sectional area S1 of the throttle groove to the flow passage cross-sectional area S2 of the first lubricating groove is 0.1 or more and 0.4 or less.

In the technical means, by controlling the flow passage cross-sectional area of the throttle groove so that 0.1≦(S1/S2)≦0.4 and the flow passage cross-sectional area of the throttle groove does not become too large, It can be ensured that the oil on the high pressure side of the pump part does not leak too much to the extent that it affects the normal compression of the pump part, that is, the oil does not flow too much into the first lubrication groove through the throttle groove, and the discharge amount of the pump part is reduced. has no significant effect on By limiting the cross-sectional area of the first lubricating groove so that the cross-sectional area of the first lubricating groove does not become too small, the cross-sectional area of the first lubricating groove is limited to a sufficient amount to form an oil film between the first bearing and the rotating shaft. It can ensure the flow rate of lubricating oil and meet the requirements for fluid lubrication.

In any one of the above technical means, furthermore, the ratio of the flow passage cross-sectional area S2 of the first lubricating groove to the cross-sectional area S0 of the shaft hole of the first bearing is 0.02 or more and 0.08 or less.

In the technical means, the flow passage cross-sectional area of the first lubricating groove is limited so that 0.02≦(S2/S0)≦0.08 and the flow passage cross-sectional area of the first lubricating groove does not become too small. By doing so, it is possible to secure a sufficient flow rate of lubricating oil to form an oil film between the first bearing and the rotating shaft, thereby satisfying the requirements for fluid lubrication. The cross-sectional area of the first lubrication groove does not become so large that the oil film formed between the first bearing and the rotating shaft is too thick and the power consumption of the rotating shaft increases.

Furthermore, by limiting the cross-sectional area of the shaft hole of the first bearing, it is located within a suitable range and is not so small as to affect the oil entering the gap between the rotating shaft and the first bearing. Similarly, the cross-sectional area of the shaft hole of the first bearing is not so large as to affect the strength of the first bearing itself. Specifically, the shaft diameter of the first bearing is 6 mm or more and 12 mm or less. As can be seen from the relation diagram between the shaft diameter of the first bearing and the amount of deformation of the first bearing, and the relation diagram between the shaft diameter of the first bearing and power consumption, when compared, when the shaft diameter is less than 6 mm, the bearing The amount of deformation of the first bearing is large, which is disadvantageous for the bearing to support the rotating shaft, and if the shaft diameter is larger than 12 mm, the power consumption of the bearing will increase rapidly. Therefore, the shaft diameter of the first bearing satisfies the above range, Not only does it meet the requirements for bearing power consumption, but it also avoids excessive deformation of the bearing.

In any one of the above technical means, the pump device further includes a sealing member connected to the side of the first bearing remote from the pump part, the sealing member being fitted on the rotating shaft and sealing A liquid passage chamber is formed by the member, the first bearing, and the rotating shaft, and the liquid passage chamber communicates with the first lubricating groove.

In this technical means, the first bearing is connected to the housing, and the first bearing can partition a chamber surrounded by the housing into a motor chamber and a pump chamber, so that the space arrangement can be rationalized. . The motor section is located in the motor chamber, and the pump section is located in the pump chamber. Here, the seal member is connected to the side of the first bearing remote from the pump section, and the seal member is fitted onto the rotating shaft. Specifically, since the sealing member can isolate the motor chamber and the pump chamber, the operating medium will not flow into the motor chamber, which will affect the normal use of components such as the stator, rotor, and control section in the motor chamber. In order to ensure that the parts inside the motor chamber are not corroded, there is no need to separately install other structures in the motor chamber, the sealing performance of the pump device is better, and the structure is simpler. , which is advantageous in reducing costs.

Note that a part of the first bearing extends away from the pump part to form the mounting position, and since the mounting position is an integrated structure with the first bearing, the mechanics of the integrated structure are better than post-processing methods. Because of its good physical properties, connection strength can be improved. In addition, the first bearing can be mass-produced to improve the processing efficiency of the product, reduce the processing cost of the product, improve the overall integrity of the pump device, reduce the number of parts, reduce the installation process, and improve the installation efficiency. Improve. In addition, since a part of the first bearing forms an attachment position for attaching the seal member, the accuracy of attaching the seal member is improved, the assembly is simple, the sealing performance is good, and the cost is low.

Furthermore, the seal member, the first bearing, and the rotating shaft form a liquid passage chamber that communicates with the first lubricating groove. The liquid passage chamber formed by the sealing member, the first bearing, and the rotating shaft can store some lubricating oil, and the liquid passage chamber is used to store the lubricating oil from the first lubricating groove, and the sealing member By controlling the connection strength between the first bearing and the first bearing, that is, the pressure that the sealing member itself can withstand, the liquid passage chamber can play a buffering role. The oil in the groove can be brought into a pressure-equalized state, which is advantageous in ensuring fluid lubrication performance between the rotating shaft and the first bearing on the premise that the stability of the position of the seal member is ensured.

In any one of the above technical means, the pump device further includes a pressure relief groove provided in the first bearing and communicating the liquid passage chamber and the second pressure chamber.

In this technical means, the pressure relief groove is provided in the first bearing, and the pressure relief groove is used to communicate the liquid passage chamber and the second pressure chamber. The pressure relief groove here may take the form of a through hole so that both ends of the through hole communicate the second pressure chamber and the liquid passage chamber. The pressure can be better released and not relying only on the liquid passage chamber itself to buffer the oil pressure.

Furthermore, by installing a pressure relief groove in the first bearing, a complete lubricating oil path for the first bearing can be formed, that is, after the oil in the first pressure chamber (high pressure chamber) enters the first oil groove, It flows into the gap between the first bearing and the rotating shaft and the first lubricating groove via the throttle groove to sufficiently lubricate the rotating shaft and the first bearing, forming an oil film to meet the requirements for fluid lubrication, and then The lubricating oil flows into the liquid passage chamber and further flows into the second pressure chamber (low pressure chamber) from the pressure relief groove, thereby preventing the pressure in the entire lubricating oil path from becoming too high. It is possible to ensure that the pressure of To effectively avoid lubricating oil leaking from one bearing and failing to ensure sealing performance between a motor chamber and a pump chamber.

In any one of the above technical means, furthermore, the ratio of the passage cross-sectional area S3 of the pressure relief groove to the passage cross-sectional area S2 of the first lubrication groove is 1 or more and 4 or less.

In the technical means, 1≦(S3/S2)≦4. The cross-sectional area of the first lubricating groove is limited so that the cross-sectional area of the first lubricating groove does not become too small, and the flow rate is sufficient to form an oil film between the first bearing and the rotating shaft. In addition, the cross-sectional area of the first lubrication groove is such that the oil film formed between the first bearing and the rotating shaft is too thick and the It should not become so large that power consumption increases.

In addition, by limiting the flow area of the pressure relief groove, it is ensured that the pressure in the oil seal chamber does not become too high, ensuring the sealing effect of the oil seal, and preventing the pressure in the liquid passage chamber from becoming too high. To prevent the seal from coming off the first bearing. In the present application, the flow path cross-sectional area of the throttle groove, the flow path cross-sectional area of the first lubrication groove, and the flow path cross-sectional area of the pressure relief groove are made to satisfy the above relational expression. It can be guaranteed that the oil flow rate in the first lubrication groove is sufficient to ensure the lubrication between the first bearing and the rotating shaft, and the pressure in the liquid passage chamber is sufficiently low to ensure that the sealing member and the first bearing are It can also be ensured that the seal connection between the parts is not affected, effectively reducing oil leakage.

In any one of the above technical measures, the pump device further includes a buffer chamber provided at the end face of the first bearing remote from the pump part.

In the technical means, the buffer chamber is provided at the end face of the first bearing remote from the pump part, and specifically, the buffer chamber may be tapered, i.e., the buffer chamber is a tapered chamber. Therefore, the buffer chamber can reduce the rigidity of the first bearing, flexibly support the rotating shaft, reduce the surface pressure of the axial end face of the first bearing away from the pump part, and To effectively improve the wear situation between a first bearing and a rotating shaft.

Furthermore, the area of the opening of the buffer chamber is larger than the area of the bottom wall of the buffer chamber. The buffer chamber includes a first wall surface that is close to the rotation axis, and the distance between the first wall surface and the rotation axis increases from the open end of the buffer chamber to the bottom wall of the buffer chamber. , the position of the first wall surface located at the opening end of the buffer chamber is closer to the rotation axis, the distance between the first wall surface and the rotation shaft is small at the opening, and the distance between the first wall surface and the rotation shaft is is larger at the position located at the bottom of the chamber, so that it can be seen that no right angle structure is formed between the first wall surface and the groove bottom of the groove body. The first bearing is usually manufactured from an aluminum alloy material, so when the rotating shaft comes into contact with the end of the first bearing, the first bearing deforms and the connection point between the first wall surface and the bottom wall of the tapered chamber has a right-angled structure, and when stress is concentrated at the connection point between the first wall surface and the groove bottom of the groove body, and the first bearing receives pressure from the rotating shaft, the first bearing It is easy to break at the connection structure point between the bottom wall of the buffer chamber and the bottom wall of the buffer chamber. When the first wall surface is provided obliquely with respect to the axial direction of the rotating shaft, the first wall surface and the bottom wall of the buffer chamber do not have a right-angled structure, which effectively reduces the failure rate of the first bearing. I can do it.

In any one of the above technical means, the buffer chamber further includes a second wall surface provided opposite to the first wall surface, and the distance between the second wall surface and the rotation axis is at the open end of the buffer chamber. It becomes smaller from there to the bottom wall of the buffer chamber.

In the technical means, the second wall surface is provided obliquely with respect to the axial direction of the rotation shaft, the second wall surface is provided facing the first wall surface, and the distance between the second wall surface and the rotation shaft is becomes smaller from the open end of the buffer chamber to the bottom wall of the buffer chamber, so that the second wall surface and the first wall surface may be provided axially symmetrically with respect to the center line of the buffer chamber. The chamber may be regularly tapered and may also support the rotating shaft more flexibly. In the axial direction away from the motor section, the gap between the first wall surface and the rotating shaft becomes larger, and the gap between the second wall surface and the rotating shaft becomes smaller, so that the buffer chamber is configured in a reverse tapered shape, and the buffer chamber is formed into a reverse tapered shape. It can be seen that the reverse tapered buffer chamber is advantageous for mold cutting.

Furthermore, the buffer chamber has a ring-shaped structure, that is, the buffer chamber is provided in the circumferential direction of the first bearing, and when the rotating shaft rotates, the radial force applied to the first bearing may change at any time. In other words, the first bearing receives varying radial forces in a plurality of directions, and no matter which direction the radial forces applied to the first bearing are directed, the presence of the ring-shaped buffer chamber causes the first bearing to can be deformed to some extent, whereby the rotating shaft and the first bearing are flexibly connected, the first bearing plays a role of buffering against the radial force of the rotating shaft, and the rotating shaft and the first bearing are This avoids the problem that the first bearing is easily damaged due to the rigid connection with the first bearing.

In any one of the above technical means, the pump device further includes a second bearing connected to the housing, fitted on the rotating shaft, and located on the side of the pump part remote from the first bearing. include.

In this technical means, the second bearing is connected to the housing and fitted onto the rotating shaft, and the second bearing is located on the side of the pump part remote from the first bearing, that is, the first bearing and the second bearing The two bearings are respectively arranged on both sides of the pump section in the axial direction, the first bearing being closer to the motor section than the second bearing. The first bearing and the second bearing can play a role of supporting the rotating shaft, and by using the rotating shaft, the first bearing, and the second bearing together, the load of the pump part can be transferred to the rotating shaft, the first bearing, and the rotating shaft. It is possible to avoid damage to the rotating shaft that may occur due to load being concentrated on the rotating shaft by equally dividing the load among the three parts of the bearing and the second bearing.

Specifically, the first bearing and the second bearing are sliding bearings. Compared to double rolling bearings, sliding bearings operate smoothly, reliably, and without noise. Under liquid lubrication conditions, the sliding surfaces are separated by lubricating oil and do not come into direct contact, reducing friction loss and surface wear. In addition, the gap between the sliding bearing and the rotating shaft is filled with lubricating oil, and the lubricating oil on the sliding surface forms a layer of oil, realizing fluid lubrication. The oil film also has a certain vibration absorption capacity, extending the service life of the first bearing, the second bearing and the rotating shaft. Two sliding bearings support the rotating shaft, the play of the rotating shaft is small, the normal position of the axis of the rotating shaft can be controlled within a reasonable range, and the double rolling bearing and sliding bearing are combined. Compared to the embodiment, this embodiment uses only two sliding bearings, which not only simplifies the support structure but also reduces costs.

Further, the first bearing has a first bearing surface close to the rotating shaft, the second bearing has a second bearing surface close to the rotating shaft, and the axial height of the second bearing surface is equal to or smaller than the first bearing surface. is less than or equal to the axial height of, i.e., less than or equal to, the axial height of When the distance between the first bearing and the pump section is the same as the distance between the second bearing and the pump section, the loads from the pump section carried by the first bearing and the second bearing are the same. However, since the first bearing is closer to the motor than the second bearing, a radial force is generated between the stator and rotor while the rotor of the motor rotates, and a load is also generated on the rotating shaft. Therefore, the first bearing must also carry the load from the motor part, and by making the second bearing surface lower than the first bearing surface, the first bearing and the second bearing can be moved at different positions on the rotating shaft. The power consumption of the rotating shaft can be minimized, provided that it is better adapted to different load requirements and guarantees the reliability of the rotating shaft's lubrication.

In any one of the above technical means, further, a part of the inner wall of the second bearing is recessed in a direction away from the rotating shaft to form a second lubricating groove communicating with the first pressure chamber.

In this technical means, the second lubricating groove is formed by recessing a part of the inner wall of the second bearing in a direction away from the rotating shaft, and the second lubricating groove communicates with the first pressure chamber. Due to the pressure difference, the oil in the first pressure chamber flows into the gap between the first bearing and the rotating shaft through the second lubricating groove, and as the rotating shaft rotates, the oil in the second lubricating groove flows into the gap between the first bearing and the rotating shaft. Oil is applied to the surface of the rotating shaft, where the second lubricating groove can play the role of temporarily storing the lubricating oil, thereby allowing fluid flow between the inner wall of the second bearing and the rotating shaft. A lubricating oil film is formed, further ensuring lubrication performance between the rotating shaft and the bearing.

In any one of the above technical means, the pump device further includes a thrust lubrication groove provided on the end face of the second bearing close to the pump part and communicating with the shaft hole of the second bearing.

In this technical means, the thrust lubrication groove is provided on the end face of the second bearing near the pump part, and the thrust lubrication groove communicates with the shaft hole of the second bearing. When the rotating shaft rotates at high speed, the lubricating oil in the fitting gap with the second bearing is cut, and the lubricating oil enters the thrust lubricating groove through the oil groove of the second bearing under the action of the cutting force. Creates constant speed and pressure. The end face of the inner gear and the end face of the pump lid move relatively, and the lubricating oil in the thrust lubrication groove can form an oil film, thus creating a fluid lubrication condition between the contact surface of the end face of the inner gear and the end face of the pump lid. is configured, which lubricates the gear and reduces noise, and can also form a thrust force against the gear, which greatly improves the power consumption and wear of the thrust surface, that is, the sliding surface between the inner gear and the pump lid. can do.

Specifically, the thrust lubricating groove is provided on the end face of the second bearing near the pump part, and the thrust lubricating groove communicates with the second bearing and the shaft hole of the second bearing. There is lubricating oil in the fitting gap between the second bearing and the rotating shaft, and during high-speed rotation of the rotating shaft, the rotating shaft cuts the lubricating oil in the fitting gap between itself and the second bearing. enters into the thrust lubricating groove from the fitting gap under the action of the cutting force ω, and at this time, the lubricating oil entering the thrust lubricating groove has a constant speed and pressure. The contact end face clearance between the second bearing and the pump part is small, and the lubricating oil in the thrust lubrication groove may flow into the end face clearance between the second bearing and the pump part. Furthermore, since the pump part and the second bearing move relatively, a fluid lubrication condition is created between the contact end surface between the pump part and the second bearing, that is, the contact end surface between the second bearing and the pump part As an oil film is formed, the space between the second bearing and the pump section changes from boundary lubrication to fluid lubrication, thereby significantly improving the wear condition of the contact end surface between the pump section and the second bearing. In addition to being able to reduce power consumption, the operating noise of the pump device can also be reduced.

Furthermore, the area of the groove mouth in the axial direction of the thrust lubricating groove is larger than the area of the groove bottom of the thrust lubricating groove.

In this embodiment, the thrust lubrication groove includes two groove ports, and the two groove ports are oriented in different directions, with one groove port facing the pump part and the other groove port facing the rotation axis. In this design, the area of the groove mouth facing the pump part is limited to be larger than the area of the groove bottom. In other words, the thrust lubricating groove has a constricted shape in the axial direction away from the pump section, that is, in the direction from top to bottom. That is, the groove wall of the thrust lubrication groove has an inclined shape, and at this time, the lubricating oil that has entered the thrust lubrication groove has a constant velocity and pressure, while the gap between the end surface where the second bearing and the pump part contact each other is Because of its small size, the groove wall of the thrust lubrication groove has an inclined shape.Then, the thrust lubrication groove and the end face gap form a converging wedge-shaped included angle, and the lubricating oil in the thrust lubrication groove is transferred to the inclined groove wall. The lubricating oil flows along the end face gap between the pump part and the second bearing, that is, the lubricating oil enters from the "large port" to the "small port". Note that the "large mouth" refers to the thrust lubrication groove, and the "small mouth" refers to the gap between the second bearing and the pump section. As a result, the lubricity between the pump part and the second bearing can be increased, so the lubrication state between them changes from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate between them. lower.

Also, during high-speed rotation of the rotating shaft and the pump part, a force F is generated that pushes the pump part upward by the oil film between the contact surface of the pump part and the second bearing, which causes the second bearing to move upward. Since the lubricating oil located within the end face of the pump portion plays the role of a floating seal, leakage from the end face can be further reduced. According to related literature, the end face leakage of the pump device accounts for 75% to 80% of the total leakage of the pump device, and therefore, improving the leakage between each contact end face of the pump device becomes of utmost importance. Note that the lubricating oil has a constant viscosity.

Further, the thrust lubrication groove includes a thrust wall including at least one thrust segment, the at least one thrust segment including a first thrust segment, and the first thrust segment is arranged in the thrust lubrication groove in an axial direction away from the pump portion. extends close to the center of

In this technical means, the thrust lubrication groove includes a thrust wall that is an inclined wall. The thrust wall extends close to the center of the thrust lubrication groove in the axial direction away from the pump section, ie in the top-to-bottom direction. The thrust wall includes at least one thrust segment, the at least one thrust segment including a first thrust segment, the first thrust segment extending proximate the center of the thrust lubrication groove in an axial direction away from the pump section. At this time, when an end face gap is formed between the end faces of the thrust lubrication groove, the pump section, and the second bearing, and a converging wedge-shaped included angle is formed between them, the lubricating oil in the thrust lubrication groove is The lubricating oil flows into the end face gap between the pump part and the second bearing along the first thrust segment, that is, the lubricating oil enters from the "large port" to the "small port". Note that the "large mouth" refers to the thrust lubrication groove, and the "small mouth" refers to the gap between the second bearing and the pump section. Therefore, by increasing the lubricity between the pump section and the second bearing, the lubrication state between the two changes from boundary lubrication to fluid lubrication, effectively reducing the wear rate between the two.

Note that the first thrust segment may include at least one straight segment and at least one curved segment, and the first thrust segment has a first end close to the pump section and a first end remote from the pump section. The second end of the first thrust segment extends close to the center of the thrust lubrication groove, that is, the obliquely extending tendency of the first thrust segment is such that when the above relationship is satisfied, the lubricating oil flows. You can make it easier. The first thrust segment may be composed of a plurality of curved surfaces or a plurality of circular arcs.

Furthermore, the included angle α between the first thrust segment and the axial end surface of the second bearing is greater than 0° and less than 90°.

In this embodiment, the axial end surface of the second bearing refers to the axial end surface on the second bearing near the pump section, and the included angle between the first thrust segment and the axial end surface is 0°< Since α<90° is satisfied, the first thrust segment can better guide the lubricating oil into the end face gap between the second bearing and the pump part, and the lubricating oil The guide of the thrust segment ensures that it enters the end gap, and the thrust lubrication groove and the end gap form a converging wedge-shaped included angle, so that the lubricating oil in the thrust lubrication groove is absorbed by the inclined groove wall. The lubricating oil flows into the gap between the end faces of the pump part and the second bearing, that is, the lubricating oil enters from the "large port" to the "small port". Thereby, in order to improve the lubricity between the pump part and the second bearing, the lubrication state between the two changes from boundary lubrication to fluid lubrication, effectively reducing the wear rate between the two. Furthermore, the included angle α between the first thrust segment and the axial end face of the second bearing is 45°. Note that by machining with a forming cutter, it is possible to machine the inclined first thrust segment on the end face of the second bearing near the pump portion. Specifically, the longitudinal section (along the axial direction) of the thrust lubricating groove can have an inverted triangular shape, a semicircular shape, or the like.

Furthermore, the at least one thrust segment further includes a second thrust segment extending axially and connected between the first thrust segment and the groove bottom of the thrust lubrication groove.

In this embodiment, the at least one thrust segment further includes a second thrust segment extending along the axial direction and connected to the first thrust segment and the groove bottom, and the second thrust segment and the first thrust segment are different from each other. They cooperate to form a thrust wall, thereby ensuring that the volume of the thrust lubrication groove meets the lubrication requirements. Note that during machining, the first thrust segment and the second thrust segment can be formed by machining a straight groove on the end face facing the pump part of the second bearing and then machining the chamfer, and with the above machining order, The difficulty in machining the thrust lubrication groove can be reduced.

Furthermore, the number of thrust walls is at least two.

In such embodiments, the number of thrust walls is at least two, and each of the at least two thrust walls includes at least one thrust segment. The at least one thrust segment includes a first thrust segment. The at least one thrust segment further includes a second thrust segment. Note that the structures of at least two thrust walls may or may not be equal, and when the number of thrust walls is three, the structures of the three thrust walls may be partially equal, or Some parts do not have to be equal.

Further, the at least two thrust walls include a first thrust wall, a first end of the first thrust wall being coupled to an inner wall of the second bearing, and a connection between the first thrust wall and the inner wall of the second bearing. The tangential plane on which the point is located is the first reference plane, and the included angle β1 between the first thrust wall and the first reference plane is 0° or more and less than 90°.

In this embodiment, the first end of the first thrust wall is the starting end of the first thrust wall, the second end of the first thrust wall is the terminal end of the first thrust wall, and the first end is the end of the second bearing. The inner wall of the second bearing is connected to the inner wall, and the inner wall of the second bearing is a side wall of the shaft hole of the second bearing. The tangential plane on which the connection point between the first end and the second bearing is located is the first reference plane, and the included angle β1 between the first thrust wall and the first reference plane is 0° or more and less than 90°. . During high-speed rotation of the rotating shaft, the rotating shaft cuts the lubricating oil in the fitting gap between itself and the second bearing, and the lubricating oil flows from the fitting gap into the thrust lubrication groove under the action of cutting force ω. At this time, the lubricating oil entering the thrust lubricating groove has a constant velocity and pressure. Since the first thrust wall is biased in the direction of rotation of the rotating shaft, the lubricating oil in the thrust lubrication groove is cut into the shaft and the surface, and as a result, negative pressure is formed in the position of the thrust lubrication groove near the shaft hole, and the rotation The lubricating oil between the shaft and the second bearing is sucked in, and the pressure at the position of the thrust lubrication groove away from the shaft hole is high, and the lubricating oil in the thrust lubrication groove is better distributed along the inclined thrust wall to the second bearing. It can flow into the end face gap between the pump part and the second bearing, thereby increasing the lubricity between the pump part and the second bearing, thereby changing the lubrication state between the two from boundary lubrication to fluid lubrication. and effectively reduce the wear rate between the two.

Furthermore, the at least two thrust walls further include a second thrust wall provided opposite to the first thrust wall, and a first end of the second thrust wall is connected to an inner wall of the second bearing, and a second thrust wall is connected to the inner wall of the second bearing. The tangential plane on which the connection point between the thrust wall and the inner wall of the second bearing is located is the second reference plane, and the included angle β2 between the second thrust wall and the second reference plane is greater than 0° and 90°. less than °.

In such embodiments, the at least two thrust walls further include a second thrust wall, a first end of the second thrust wall being a beginning end of the second thrust wall, and a second end of the second thrust wall being a beginning end of the second thrust wall. A second end of the thrust wall is connected to an inner wall of the second bearing, and the inner wall of the second bearing is a side wall of the shaft hole of the second bearing. The tangential plane on which the connection point between the first end and the second bearing is located is the second reference plane, and the included angle β2 between the second thrust wall and the second reference plane is 0° or more and less than 90°. . During high-speed rotation of the rotating shaft, the rotating shaft cuts the lubricating oil in the fitting gap between itself and the second bearing, and the lubricating oil flows from the fitting gap into the thrust lubrication groove under the action of cutting force ω. At this time, the lubricating oil entering the thrust lubricating groove has a constant velocity and pressure. Since the second thrust wall is biased in the direction of rotation of the rotating shaft, the lubricating oil in the thrust lubrication groove is cut into the shaft and the surface, and as a result, negative pressure is formed in the position of the thrust lubrication groove near the shaft hole, and the rotation The lubricating oil between the shaft and the second bearing is sucked in, and the pressure at the position of the thrust lubrication groove away from the shaft hole is high, and the lubricating oil in the thrust lubrication groove is better distributed along the inclined thrust wall to the second bearing. It can flow into the gap between the end face and the pump part. Therefore, the lubricity between the pump section and the second bearing can be increased, and the lubrication state between the two changes from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate between the two.

Additionally, the at least two thrust walls further include a third thrust wall coupled to the second end of the first thrust wall and the second end of the second thrust wall, respectively.

In this embodiment, the at least two thrust walls further include a third thrust wall coupled to the second end of the first thrust wall and the second end of the second thrust wall, respectively. That is, since the first thrust wall, the second thrust wall, and the third thrust wall together constitute the thrust lubrication groove, it becomes easy to design the shape of the thrust lubrication groove.

Note that the projection of the first thrust wall, the second thrust wall, and the third thrust wall on the axial end surface of the second bearing may be a straight segment or a curved segment.

Furthermore, the third thrust wall of the thrust lubrication groove is an arcuate wall.

In this embodiment, the third thrust wall is an arcuate wall, that is, the projection of the third thrust wall on the axial end face of the second bearing is an arcuate segment. Since the position corresponding to the third thrust wall is far from the shaft hole of the thrust lubrication groove, the pressure of the lubricating oil corresponding to this position in the thrust lubrication groove is high, causing the third thrust wall to turn into an arcuate wall. By doing so, the lubricating oil in the thrust lubricating groove can easily flow, that is, the lubricating oil can easily enter from the "large mouth" to the "small mouth", and the lubricity between the pump part and the second bearing can be improved. As a result, the lubrication state between the two changes from boundary lubrication to fluid lubrication, effectively reducing the wear rate between the two.

In any one of the above technical measures, the housing further includes a case and a pump lid, the case is disposed around the outside of the motor part and the pump part, and the case is connected to the first bearing. The pump lid is connected to the case, the pump lid forms a chamber with the case, the pump lid is connected to the second bearing, and a portion of the pump lid extends away from the pump part to form an oil pool. constitute an extension section for The shaft hole of the second bearing is a through hole that penetrates in the axial direction, one end of the through hole is used to communicate with the thrust lubricating groove, and the other end of the through hole is used to communicate with the oil pool.

In this technical means, the housing includes a case and a pump lid connected to the case, the pump lid forms a chamber with the case, and the case is disposed around the outside of the motor part and the pump part. The case is connected to the first bearing, and the pump lid is connected to the second bearing. The first bearing may be integrally molded with the case, and the case is integrally molded with the first bearing, and compared with the post-processing method, the connection strength is higher, space is saved, and the overall height of the machine is lowered. In addition, it is possible to reduce the difficulty level of the manufacturing process and reduce manufacturing costs. The pump lid may be integrally molded with the second bearing, which can not only save more height space and reduce the overall height of the machine, but also reduce costs.

Furthermore, since the extension part is formed in a structure in which a part of the pump lid extends in a direction away from the pump part, the extension part is integrally molded with the pump lid, and the connection strength is greater than that in a post-processing method. The extension is used to form an oil pool in which lubricating oil can be stored. The shaft hole of the second bearing is a through hole that penetrates in the axial direction, and both ends of the through hole communicate with the thrust lubrication groove and the oil pool, respectively.

Specifically, during high-speed rotation of the rotary shaft, the rotary shaft cuts the lubricating oil in the fitting gap between itself and the second bearing, and the lubricating oil flows through the fitting gap (under the action of the cutting force). At this time, the lubricating oil entering the thrust lubricating groove has a constant velocity and pressure. Since the lubricating oil in the thrust lubrication groove is cut into shafts and faces, negative pressure is formed near the shaft hole in the thrust lubrication groove, sucking the lubricating oil between the rotating shaft and the second bearing, and the thrust The pressure in the lubricating groove at a position away from the shaft hole is high, and the lubricating oil in the thrust lubricating groove can be more effectively forced into the end face gap between the second bearing and the pump section. Therefore, the lubricity between the pump section and the second bearing can be improved, and the lubrication state between the two changes from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate between the two.

Furthermore, the oil is pumped into the thrust lubrication groove and then enters the gap between the second bearing and the pump part to lubricate the contact surface between the pump part and the second bearing, and then the oil Under the action of differential and gravity, it enters the oil pool in the low pressure area.

Specifically, the lubricating oil path of the second bearing is as follows. Oil enters the gap between the second bearing and the rotating shaft via the oil pool (through hole, second lubrication groove), then enters the thrust lubrication groove, and under the action of the thrust lubrication groove, the oil flows into the pump section. and the second bearing, and enters the low pressure oil pool under the action of pressure difference and gravity. Forming a complete lubricating oil path for the second bearing is advantageous in ensuring lubrication performance between the second bearing and the rotating shaft.

In addition, the pump lid is integrally molded with the second bearing, which has higher connection strength than post-processing methods, saves space, lowers the overall height of the machine, and reduces the difficulty of the manufacturing process. , manufacturing costs can be reduced.

In any one of the above technical measures, the housing further includes a case and a pump lid, the case is disposed around the outside of the motor part and the pump part, and the case is connected to the first bearing. The pump lid is connected to the case to form a chamber with the case, and is connected to the second bearing, the shaft hole of the second bearing being a blind hole with one end open. The communication groove is formed in the second bearing and/or the pump lid, and the communication groove communicates the first pressure chamber and the blind hole.

In this technical means, the housing includes a case and a pump lid connected to the case, the pump lid forms a chamber with the case, and the case is disposed around the outside of the motor part and the pump part. The case is connected to the first bearing, and the pump lid is connected to the second bearing. The first bearing may be integrally molded with the case, and the case is integrally molded with the first bearing, and compared with the post-processing method, the connection strength is higher, space is saved, and the overall height of the machine is lowered. In addition, it is possible to reduce the difficulty level of the manufacturing process and reduce manufacturing costs. The pump lid may be integrally molded with the second bearing, which can not only save more height space and reduce the overall height of the machine, but also reduce costs.

Furthermore, the shaft hole of the second bearing is a blind hole with one end open, and the communication groove is formed in the second bearing and/or the pump lid, and the communication groove is for communicating the first pressure chamber and the blind hole. used. Specifically, the lubricating oil path of the second bearing is as follows. The pressurized oil enters the blind hole (the gap between the second bearing and the rotating shaft, the second lubrication groove) from the first pressure chamber (high pressure chamber) via the communication groove, and then flows between the second bearing and the pump. The low pressure region is returned to the low pressure region via the gap between the oil supply port and the second pressure chamber. By forming a complete lubricating oil path for the second bearing, it is advantageous to ensure the lubrication performance between the second bearing and the rotating shaft.

In any one of the above technical means, the pump part further includes a first rotating member and a second rotating member, and the first rotating member is fitted with the rotating shaft. The second rotating member is provided outside the first rotating member, the second rotating member is rotatable in conjunction with the first rotating member, and the second rotating member is connected to the first rotating member and the first pressure chamber. A second pressure chamber is configured. The pump device further includes an oil supply inlet and an oil outlet, the oil supply inlet being axially opened in the pump lid and/or the second bearing, the oil supply inlet communicating with the second pressure chamber, and the oil outlet communicating with the second pressure chamber. , is radially opened in the pump lid and the second bearing, and the oil outlet communicates with the first pressure chamber of the pump section.

In the technical means, the pump part includes a first rotating member and a second rotating member, the first rotating member is fitted with the rotating shaft, the second rotating member is provided outside the first rotating member, The second rotating member is rotatable in conjunction with the first rotating member, which can be understood to mean that the rotating shaft can actuate the second rotating member via the first rotating member. By installing the structure of the first rotating member and the second rotating member, a first pressure chamber and a second pressure chamber are formed, and the first pressure chamber is a high pressure chamber and the second pressure chamber is a low pressure chamber. .

Note that the first rotating member is an inner gear, and the second rotating member is an outer gear, that is, the pump portion is a gear pump. Specifically, in the meshing process of a gear pump, while the front pair of teeth have not yet come out of mesh, the rear pair of teeth has already entered the meshing process, and each internal tooth surface is all in contact with the external tooth surface. As the internal gear rotates, the volume of the sealed storage chamber changes, and if it cannot communicate with the unloading channel, a trapped volume is formed. Since the compressibility of liquid is very low, when the confinement volume changes from large to small, the liquid present in the confinement volume is pushed and the pressure increases rapidly, which significantly increases the operating pressure of the gear pump. surpass. Also, since the liquid in the containment volume is also forced through all leakable slits, both the rotating shaft and bearings are subjected to very high shock loads, increasing power losses and heating the oil, causing noise and Vibration will occur, reducing the smoothness of operation and service life of the gear pump. When the confinement volume increases from small to large, a vacuum is formed and the air dissolved in the liquid is separated and bubbles are generated, resulting in harmful effects such as cavitation, noise, vibration, flow rate, and pressure pulsations. As a method to solve the entrapment phenomenon, unloading grooves are opened in the lids at both ends of the gear, and when the sealed volume becomes small, the unloading groove communicates with the pressure oil chamber, and when the sealed volume becomes large, the unloading groove is opened. A method of communicating with the oil absorption chamber via a groove is adopted.

Specifically, the inner gear meshes with the contour of the conjugate curved tooth profile of the outer gear, so that the teeth are in contact with each other, and the outer gears are interlocked and rotated in the same direction. The inner cavity of the outer gear is partitioned into multiple operating chambers by the inner gear, and because the centers of the inner and outer gears are offset, the volumes of the multiple operating chambers change with the rotation of the rotor, resulting in an area where the volume increases. A constant vacuum is created, an oil supply inlet is provided at that location, the pressure is higher in the area of reduced volume, and an oil outlet is correspondingly provided there.

Furthermore, the pump device further includes an oil supply port and an oil outlet, the oil supply port being opened in the pump lid and/or the second bearing in the axial direction, and the oil supply port communicating with the second pressure chamber. . Since the second pressure chamber is a low pressure chamber and has a pressure difference with the outside, oil enters the second pressure chamber through the oil supply port. The oil outlet is radially opened in the pump lid and the second bearing, and communicates with the first pressure chamber. Since the first pressure chamber is a high pressure chamber and has a pressure difference with the outside, the oil in the first pressure chamber flows out through the oil outlet. That is, the main oil passage of the pump device is as follows. Negative pressure can be generated in the second pressure chamber and the oil supply port, and under the action of the negative pressure, the oil in the oil pool is sucked into the oil supply port and enters the second pressure chamber (low pressure chamber), causing the second pressure The oil entering the chamber enters the high pressure chamber and is pressurized under the action of the first rotating member and the second rotating member, and the pressurized oil is discharged through the oil outlet.

The design principle of the oil supply port and oil outlet is as follows. In the process of ensuring the rotation of the gear, the oil supply port is communicated between the teeth of the first rotating member and the second rotating member as soon as possible, and the gear volume chamber is always maintained until the maximum volume is formed in the inner gear and the outer gear. It is necessary to extend the oil filling time as much as possible so as to ensure oil absorption by filling the volume chamber communicating with the oil supply port and between the internal and external teeth with oil. The oil outlet is also communicated with the high pressure oil between the teeth as soon as possible to reduce the overcompression work between the teeth, and is closed as late as possible to fully utilize the inertia of the fluid to exhaust the oil between the teeth. Improves the volumetric efficiency of internally meshing gear type oil pumps. However, it should be noted that when the inner gear and the outer gear form the maximum volume, they cannot communicate with the oil supply port to avoid affecting the volumetric efficiency of the pump device at low speeds.

In any one of the above technical means, the motor part further includes a rotor and a stator, the rotor is connected to the rotating shaft, the stator is fitted on the outside of the rotor, and the stator includes a stator core and a stator winding. , the stator windings are provided in the stator core. The pump device further includes a control section provided on a side of the motor section remote from the pump section, the control section being connected to the housing and located within the chamber, the end of the stator winding being connected to the control section. electrically connected.

In the technical means, the motor section further includes a rotor and a stator. Here, the rotor is connected to the rotating shaft, and the rotor and the rotating shaft may be coaxially provided, and the fitting method between the rotor and the rotating shaft may be an interference fit, and Possibly, the rotor and the axis of rotation are provided on different axes, but both are communicatively connected and provided flexibly depending on the actual situation. A stator is fitted outside the rotor, the stator includes a stator core and a stator winding, and the stator winding is provided on the stator core.

Further, the pump device further includes a control section provided on a side of the motor section remote from the pump section, that is, the control section is provided at a position remote from the pump section of the motor section, and the control section is provided at a position remote from the pump section of the motor section, and the control section is provided at a position remote from the pump section of the motor section, and the control section is provided at a position remote from the pump section of the motor section. Because the vibration in the vicinity is obvious and the load it receives is large, the control part is separated from the pump part, which can play a role of protecting the control part to a certain extent, extending the service life of the control part.

Further, the control section is connected to the housing and located within the chamber, and the ends of the stator windings are electrically connected to the control section.

Specifically, during operation of the pump device, the control unit controls the stator to generate a changing excitation magnetic field by controlling the current in the stator winding in the stator to change according to a certain rule, When the rotor rotates under the action of the excitation magnetic field, the first rotating member in the pump section rotates in conjunction with the rotating shaft, and the second rotating member also moves. When the first rotating member and the second rotating member in the pump section rotate, the second rotating member moves unevenly, so the volume of the compression chamber formed between the first rotating member and the second rotating member changes. This generates power that forces the working medium that has entered the compression chamber to flow to the oil outlet.

An embodiment of the second aspect of the present application provides a vehicle comprising a pump device according to any one of the embodiments described above.

According to an embodiment of the vehicle of the present application, which includes a pumping device, the vehicle may also be a special vehicle and has all the advantages of a pumping device.

Note that the vehicle may be a conventional gasoline vehicle or a new energy vehicle. Here, new energy vehicles include pure electric vehicles, extended range electric vehicles, hybrid vehicles, fuel cell vehicles, hydrogen engine vehicles, etc.

In the above technical means, the vehicle includes a vehicle body on which the pump device is provided, and an engine that is provided on the vehicle body and includes a mounting seat connected to an extension of the pump device.

In the technical means, the vehicle includes a body and an engine. Both the pump device and the engine are provided on the vehicle body, and the engine includes a mounting seat that is connected to the extension portion of the pump device, so that the engine and the pump device are connected by fitting the mounting seat and the extension portion. connection can be achieved.

Here, since the vehicle includes the pump device of any one of the first aspects described above, it has the beneficial effects of any one of the embodiments described above, and detailed description thereof will be omitted here.

Additional aspects and advantages of embodiments of the present application will be apparent from the description section below, or may be learned by practice of the present application.

FIG. 1 is a schematic diagram showing the structure of a pump device according to an embodiment of the present application. FIG. 2 is a partially enlarged view showing part A of the pump device according to an embodiment of the present application shown in FIG. 1; FIG. 1 is a schematic diagram showing a partial structure of a pump device according to an embodiment of the present application. FIG. 3 is a schematic diagram showing the structure of a pump device according to another embodiment of the present application. FIG. 3 is a schematic diagram showing the structure of a pump lid and a second bearing of a pump device according to an embodiment of the present application. 1 is a schematic diagram showing the structure of a vehicle according to an embodiment of the present application.

In order to more clearly understand the above objectives, features and advantages of the embodiments of the present application, the embodiments of the present application will be described in further detail below with reference to the drawings and specific embodiments. Note that the embodiments of the present application and the features in the embodiments may be combined with each other as long as no contradiction occurs.

Although many specific details are set forth in the following description to provide a thorough understanding of the present application, the embodiments of the present application may be practiced otherwise than as described herein. Therefore, the protection scope of the present application is not limited to the specific embodiments disclosed below.

Hereinafter, a pump device 100 and a vehicle 200 provided in some embodiments of the present application will be described with reference to FIGS. 1 to 6.

Example 1
The embodiment of the first aspect of the present application provides a pump device 100, which includes a housing 110, a motor section 120, a pump section 130, a first bearing 140, a first oil groove, as shown in FIGS. 141 and an aperture groove 142. Here, the housing 110 has a chamber 111. Motor section 120 includes a rotating shaft 121 that rotates around the central axis of motor section 120 . The pump section 130 is provided on one side of the motor section 120 in the axial direction and contacts the rotating shaft 121, so that the pump section 130 is rotatable in conjunction with the rotating shaft 121. The pump section 130 includes a first pressure chamber 131 and a second pressure chamber 132, and the pressure that the first pressure chamber 131 receives is greater than the pressure that the second pressure chamber 132 receives. The first bearing 140 is connected to the housing 110 and fitted onto the rotating shaft 121, and the first bearing 140 is located between the motor section 120 and the pump section 130. The first oil groove 141 is provided on the first end face of the first bearing 140 facing the pump section 130, and the first oil groove 141 communicates with the first pressure chamber 131. The throttle groove 142 is provided in the first end surface, and the throttle groove 142 communicates the first oil groove 141 with the gap between the first bearing 140 and the rotating shaft 121 .

According to the embodiment of the pump device 100 provided in the present application, the pump device 100 includes a housing 110, a motor section 120, a pump section 130, a first bearing 140, a first oil groove 141, and a throttle groove 142. Here, the housing 110 has a chamber 111, and the motor section 120 and the pump section 130 are provided in the chamber 111, so the housing 110 allows the motor section 120 and the pump section 130 to operate normally without being affected by the external environment. Ensure that it is operational. The motor section 120 includes a rotating shaft 121 that rotates around the central axis of the motor section 120, and the pump section 130 is provided on one side of the motor section 120 in the axial direction, contacts the rotating shaft 121, and has a concrete structure. Specifically, the pump section 130 is tightly fitted with the rotating shaft 121, and the pump section 130 is rotatable in conjunction with the rotating shaft 121. You can understand it by driving and operating it. The pump section 130 includes a first pressure chamber 131 and a second pressure chamber 132, the pressure that the first pressure chamber 131 receives is greater than the pressure that the second pressure chamber 132 receives, and the first pressure chamber 131 is a high pressure chamber. The second pressure chamber 132 may be a low pressure chamber.

Further, the first bearing 140 is connected to the housing 110, the first bearing 140 is located between the motor section 120 and the pump section 130, the first bearing 140 is fitted onto the rotating shaft 121, and the first bearing 140 is connected to the housing 110. can play a role of supporting the rotating shaft 121 to some extent. Note that the first bearing 140 can provide lubricating support to the rotating shaft 121, and since the axes of the first bearing 140 and the rotating shaft 121 overlap, the rotating shaft 121 drives the pump part 130 during actual operation. Therefore, the pump unit 130 applies a radial force to the rotating shaft 121, and the rotating shaft 121 pushes the first bearing 140 to one side while receiving the radial force. When the rotating shaft 121 contacts the first bearing 140, the first bearing 140 provides a supporting action to the rotating shaft 121, thereby controlling the play of the rotating shaft 121 within a reasonable range. Therefore, the axis of the rotating shaft 121 can be easily controlled.

Note that the first bearing 140 is a sliding bearing, and the sliding bearing refers to a bearing that operates by sliding friction. Compared to rolling bearings, sliding bearings operate smoothly, reliably, and without noise. Under liquid lubrication conditions, the sliding surfaces are separated by lubricating oil and do not come into direct contact, reducing friction loss and surface wear. In addition, the gap between the sliding bearing and the rotating shaft 121 is filled with lubricating oil, and the lubricating oil on the sliding surface forms a layer of oil to realize fluid lubrication. The oil film also has a certain vibration absorption ability, extending the service life of the first bearing 140 and the rotating shaft 121.

Further, as shown in FIG. 3, the first oil groove 141 is provided on the first end face of the first bearing 140 facing the pump part 130, the first oil groove 141 communicates with the first pressure chamber 131, and the first oil groove 141 communicates with the first pressure chamber 131. Since the pressure inside the pressure chamber 131 is large, a part of the oil flows from the first pressure chamber 131 into the first oil groove 141, and then flows into the gap between the rotating shaft 121 and the first bearing 140, and then flows into the first oil groove 141. The lubrication performance between the bearing 140 and the rotating shaft 121 is guaranteed.

Furthermore, as shown in FIG. 3, the throttle groove 142 is provided on the first end surface, that is, the throttle groove 142 is provided on the first end surface of the first bearing 140 facing the pump part 130, and the throttle groove 142 is It is used to communicate the first oil groove 141 with the gap between the first bearing 140 and the rotating shaft 121. That is, the oil in the first pressure chamber 131 first flows into the first oil groove 141 and then flows into the gap between the first bearing 140 and the rotating shaft 121 via the throttle groove 142. It is possible to effectively prevent oil from flowing excessively into the gap between the first bearing 140 and the rotating shaft 121 and further affecting the discharge amount of the pump device 100.

Therefore, in order to ensure fluid lubrication performance between the first bearing 140 and the rotating shaft 121, in other words, sufficient lubricating oil is provided in the gap between the first bearing 140 and the rotating shaft 121, and the pump part In order to ensure that the discharge amount of the pump section 130 does not leak significantly, that is, to ensure that the discharge amount of the pump section 130 is not significantly affected by the lubricating oil, the first oil groove 141 and the throttle groove 142 are aligned. By using this, it is possible to not only realize the lubrication requirements between the first bearing 140 and the rotating shaft 121, but also to prevent the flow rate in the first bearing 140 from being too large and reducing the discharge amount of the pump device 100. It won't happen either.

Specifically, the first oil groove 141 can balance the pressures between the high-pressure side storage chambers of the pump section 130, and as a result, the pressures of the high-pressure side storage chambers become close, so that during operation noise and mechanical vibration can be reduced.

Furthermore, as shown in FIG. 3, since the flow passage cross-sectional area of the throttle groove 142 is less than the flow passage cross-sectional area of the first oil groove 141, the throttle groove 142 creates a gap between the first bearing 140 and the rotating shaft 121. The flow rate of lubricating oil within the gap can be controlled.

Furthermore, as shown in FIGS. 1 to 3, a portion of the inner wall of the first bearing 140 is recessed in a direction away from the rotating shaft 121 to form a first lubricating groove 143 that communicates with the throttle groove 142.

In this embodiment, the first lubricating groove 143 is formed by recessing a part of the inner wall of the first bearing 140 in a direction away from the rotating shaft 121 , and the first lubricating groove 143 communicates with the throttle groove 142 . Since there is a pressure difference, the oil in the first pressure chamber 131 passes through the first oil groove 141 and the throttle groove 142 sequentially, and then flows into the gap between the first bearing 140 and the rotating shaft 121. The first lubricating groove 143 can also be filled, and as the rotating shaft 121 rotates, the oil in the first lubricating groove 143 is applied to the surface of the rotating shaft 121. It plays the role of temporary storage, thereby forming a fluid lubricating oil film between the inner wall of the first bearing 140 and the rotating shaft 121, further ensuring reliable lubricity between the rotating shaft 121 and the bearing. can. Furthermore, the first lubricating groove 143 is bored in the first bearing 140 along the axial direction, the first lubricating groove 143 communicates with the shaft hole of the first bearing 140, and one end of the first lubricating groove 143 is formed into a throttle groove. 142, and the other end of the first lubricating groove 143 extends toward the motor chamber. Furthermore, the number of first lubrication grooves 143 is at least one, and may be installed flexibly according to actual lubrication requirements.

Furthermore, the ratio of the passage cross-sectional area S1 of the throttle groove 142 to the passage cross-sectional area S2 of the first lubricating groove 143 is 0.1 or more and 0.4 or less.

In this embodiment, 0.1≦(S1/S2)≦0.4, and by controlling the flow passage cross-sectional area of the throttle groove 142 so that the flow passage cross-sectional area of the throttle groove 142 does not become too large. , it is possible to ensure that the oil on the high pressure side of the pump section 130 does not leak too much to the extent that it affects normal compression of the pump section 130, that is, the oil does not flow too much into the first lubrication groove 143 through the throttle groove 142. , does not significantly affect the discharge amount of the pump section 130. By limiting the cross-sectional area of the first lubricating groove 143 so that the cross-sectional area of the first lubricating groove 143 does not become too small, an oil film can be formed between the first bearing 140 and the rotating shaft 121. The lubricating oil flow rate is sufficient to meet the requirements for fluid lubrication.

Further, the ratio between the flow passage cross-sectional area S2 of the first lubricating groove 143 and the cross-sectional area S0 of the shaft hole of the first bearing 140 is 0.02 or more and 0.08 or less.

In this embodiment, 0.02≦(S2/S0)≦0.08, and the cross-sectional area of the first lubricating groove 143 is set so that the cross-sectional area of the first lubricating groove 143 does not become too small. By limiting the amount, a flow rate of lubricating oil sufficient to form an oil film between the first bearing 140 and the rotating shaft 121 can be secured, and the requirements for fluid lubrication are satisfied. The cross-sectional area of the first lubrication groove 143 does not become so large that the oil film formed between the first bearing 140 and the rotating shaft 121 is too thick and the power consumption of the rotating shaft 121 increases.

Furthermore, by limiting the cross-sectional area of the shaft hole of the first bearing 140, it can be positioned within a suitable range and influence the oil entering the gap between the rotating shaft 121 and the first bearing 140. Similarly, the cross-sectional area of the shaft hole of the first bearing 140 is not so large as to affect the strength of the first bearing 140 itself. Specifically, the shaft diameter of the first bearing 140 is 6 mm or more and 12 mm or less. As can be seen from the relationship diagram between the shaft diameter of the first bearing 140 and the amount of deformation of the first bearing 140 and the relationship diagram between the shaft diameter of the first bearing 140 and power consumption, in comparison, the shaft diameter is less than 6 mm. In this case, the amount of deformation of the bearing is large and it is disadvantageous for the bearing to support the rotating shaft 121, and if the shaft diameter is larger than 12 mm, the power consumption of the bearing increases rapidly. This not only satisfies the requirements for bearing power consumption, but also avoids excessive deformation of the bearing.

Furthermore, as shown in FIGS. 1, 2, and 4, the pump device 100 further includes a seal member 150 connected to the side of the first bearing 140 remote from the pump section 130, and the seal member 150 A liquid passing chamber 151 is formed by the sealing member 150 , the first bearing 140 and the rotating shaft 121 , and the liquid passing chamber 151 communicates with the first lubricating groove 143 .

In this embodiment, the first bearing 140 is connected to the housing 110, and the first bearing 140 can partition the chamber 111 surrounded by the housing 110 into a motor chamber and a pump chamber, thereby rationalizing the space arrangement. It can be. The motor section 120 is located in a motor chamber, and the pump section 130 is located in a pump chamber. Here, the seal member 150 is connected to the side of the first bearing 140 remote from the pump section 130, and the seal member 150 is fitted onto the rotating shaft 121. Specifically, since the sealing member 150 can isolate the motor chamber and the pump chamber, the operating medium does not flow into the motor chamber, and the members such as the stator 123, rotor 122, and control unit 190 in the motor chamber can operate normally. There is no need to separately install other structures in the motor chamber, and the sealing performance of the pump device 100 is better, and the structure is is easier and is advantageous in reducing costs.

As shown in FIGS. 1, 2, and 4, a part of the first bearing 140 extends in a direction away from the pump part 130 to constitute an attachment position, and the attachment position is an integral structure with the first bearing 140. Compared to post-processing methods, the integral structure has better mechanical properties and can improve connection strength. In addition, the first bearing 140 can be mass-produced to improve the processing efficiency of the product, reduce the processing cost of the product, improve the overall integrity of the pump device 100, reduce the number of parts, reduce the installation process, and Improve efficiency. In addition, a part of the first bearing 140 forms an attachment position for attaching the seal member 150, thereby improving the accuracy of attaching the seal member 150, making assembly easy, having good sealing performance, and low cost. .

Further, as shown in FIG. 2, a liquid passage chamber 151 communicating with the first lubricating groove 143 is formed by the seal member 150, the first bearing 140, and the rotating shaft 121. The liquid passage chamber 151 formed by the seal member 150, the first bearing 140, and the rotating shaft 121 can store some lubricating oil, and the liquid passage chamber 151 can store the lubricating oil from the first lubricating groove 143. By controlling the strength of the connection between the sealing member 150 and the first bearing 140, that is, the pressure that the sealing member 150 itself can withstand, the liquid passage chamber 151 can play the role of a buffer. On the premise that the oil in the liquid passage chamber 151, the first lubricating groove 143, and the throttle groove 142 can be brought into an equal pressure state and the stability of the position of the seal member 150 is ensured, the rotation shaft 121 and the first bearing 140 are This is advantageous in ensuring fluid lubrication performance.

Furthermore, as shown in FIGS. 1, 2, 3, and 4, the pump device 100 further includes a pressure relief groove provided in the first bearing 140 and communicating between the liquid passage chamber 151 and the second pressure chamber 132. 144 included.

In this embodiment, the pressure relief groove 144 is provided in the first bearing 140, and the pressure relief groove 144 is used to communicate the liquid passage chamber 151 and the second pressure chamber 132. The pressure relief groove 144 here may take the form of a through hole so that both ends of the through hole communicate with the second pressure chamber 132 and the liquid passage chamber 151, and since the pressure inside the second pressure chamber 132 is small, , the pressure within the liquid passage chamber 151 can be better released, and the liquid passage chamber 151 itself is not solely relied upon to buffer the oil pressure.

Furthermore, by installing the pressure relief groove 144 in the first bearing 140, a complete lubricating oil path for the first bearing 140 can be formed, that is, the oil in the first pressure chamber 131 (high pressure chamber) can be After that, it flows into the gap between the first bearing 140 and the rotating shaft 121 and the first lubricating groove 143 via the throttle groove 142, sufficiently lubricates the rotating shaft 121 and the first bearing 140, and forms an oil film. After that, the lubricating oil flows into the liquid passage chamber 151, and further flows into the second pressure chamber 132 (low pressure chamber) from the pressure relief groove 144, whereby the lubricating oil path It is possible to ensure that the overall pressure does not become too high, that is, the pressure within the liquid passage chamber 151 does not become too high, and to avoid the pressure being higher than the pressure limit value that the seal member 150 can withstand. 150, and effectively prevent the sealing member 150 from coming off from the first bearing 140 under high pressure, lubricating oil leaking, and sealing performance between the motor chamber and the pump chamber not being ensured. To avoid.

Furthermore, the ratio of the passage cross-sectional area S3 of the pressure relief groove 144 to the passage cross-sectional area S2 of the first lubricating groove 143 is 1 or more and 4 or less.

In this example, 1≦(S3/S2)≦4. An oil film is formed between the first bearing 140 and the rotating shaft 121 by limiting the cross-sectional area of the first lubricating groove 143 so that the cross-sectional area of the first lubricating groove 143 does not become too small. The flow path cross-sectional area of the first lubrication groove 143 is designed to ensure a sufficient flow rate of lubricating oil to satisfy the requirements for fluid lubrication. is so thick that it does not become so large that the power consumption of the rotating shaft 121 increases.

In addition, by limiting the flow path area of the pressure relief groove 144, it is ensured that the pressure in the oil seal chamber does not become too high, ensuring the sealing effect of the oil seal, and preventing the pressure in the liquid passage chamber 151 from becoming too high. This prevents the oil seal from coming off the first bearing 140. In the present application, the flow path cross-sectional area of the throttle groove 142, the flow path cross-sectional area of the first lubrication groove 143, and the flow path cross-sectional area of the pressure relief groove 144 are taken into consideration so that the three satisfy the above relational expression. This ensures that the oil flow rate in the first lubrication groove 143 is sufficient to ensure lubrication between the first bearing 140 and the rotating shaft 121, and that the pressure in the liquid passage chamber 151 is sufficiently low. , it can also be ensured that the sealing connection between the sealing member 150 and the first bearing 140 is not affected, which effectively reduces oil leakage.

According to the simulation data, it is determined that the flow rate of lubricating oil in the lubricating oil path of the first bearing 140 should not be lower than 3 ml/s, and the shaft diameter of the first bearing 140 is 8 mm, and the strength of the bearing is determined by the simulation. After confirming this, it is determined that the flow passage cross-sectional area S2 of the first lubricating groove 143 is 1.57 mm ² as the optimum selection. Next, structures with different flow passage cross-sectional areas S1 of the throttle grooves 142 and flow passage cross-sectional areas S3 of the pressure relief grooves 144 are designed to obtain simulation data as shown in Table 1.

Based on the simulation data in Table 1, it can be determined that the solution number 3 is the optimal means, that is, the flow passage cross-sectional area S1 of the throttle groove 142 is 0.4 mm ² and the first lubricating groove 143 is The flow passage cross-sectional area S2 is 1.57 ^mm2 , the flow passage cross-sectional area S3 of the pressure relief groove 144 is 3.14 ^mm2 , and in this case, the oil flow rate in the first lubrication groove 143 is 7.3 ml/s. Yes, the lubrication requirements are met, the oil flow rate in the first bearing 140 is not large enough to reduce the discharge amount of the pump device 100, and the pressure in the liquid passage chamber 151 is 112 kPa, and the pressure increases. Serious oil leaks can be avoided because there is no excess oil.

Example 2
This example describes the specific structure of the first bearing 140 based on Example 1, and as shown in FIG. It includes a buffer chamber 160 provided at the end face.

In this embodiment, the buffer chamber 160 is provided on the end face of the first bearing 140 remote from the pump part 130, and specifically, the buffer chamber 160 may have a tapered shape. Since it may be a tapered chamber, the buffer chamber 160 can reduce the rigidity of the first bearing 140, flexibly supports the rotating shaft 121, and extends the axial end surface of the first bearing 140 away from the pump section 130. This effectively improves the wear condition between the first bearing 140 and the rotating shaft 121.

Further, the area of the opening of the buffer chamber 160 is larger than the area of the bottom wall of the buffer chamber 160. The buffer chamber 160 includes a first wall surface 161 that is a wall surface close to the rotating shaft 121, and the distance between the first wall surface 161 and the rotating shaft 121 increases from the open end of the buffer chamber 160 to the bottom wall of the buffer chamber 160. This is because the first wall surface 161 is provided diagonally, the position of the first wall surface 161 located at the open end of the buffer chamber 160 is closer to the rotating shaft 121, and the distance between the first wall surface 161 and the rotating shaft 121 is open. It is understood that the distance between the first wall surface 161 and the rotating shaft 121 is large at the position located at the bottom of the chamber, so that a right-angled structure is not formed between the first wall surface 161 and the groove bottom of the groove body. can. Since the first bearing 140 is usually manufactured from an aluminum alloy material, when the rotating shaft 121 comes into contact with the end of the first bearing 140, the first bearing 140 is deformed, causing the first wall surface 161 and the bottom of the tapered chamber to deform. The connection point with the wall has a right-angled structure, and if stress is concentrated at the connection point between the first wall surface 161 and the groove bottom of the groove body, and the first bearing 140 receives pressure from the rotating shaft 121, The first bearing 140 is likely to break at the connection structure between the first wall surface 161 and the bottom wall of the buffer chamber 160. When the first wall surface 161 is provided obliquely with respect to the axial direction of the rotating shaft 121, the first wall surface 161 and the bottom wall of the buffer chamber 160 do not have a right-angled structure, which reduces the damage rate of the first bearing 140. can be effectively reduced.

Furthermore, the buffer chamber 160 includes a second wall surface 162 provided opposite to the first wall surface 161 , and the distance between the second wall surface 162 and the rotating shaft 121 is set such that the distance between the second wall surface 162 and the rotating shaft 121 is from the open end of the buffer chamber 160 to the second wall surface 162 . It becomes smaller towards the bottom wall.

In this embodiment, the second wall surface 162 is provided obliquely with respect to the axial direction of the rotating shaft 121, the second wall surface 162 is provided facing the first wall surface 161, and the second wall surface 162 and the rotating shaft 121 The distance between them becomes smaller from the open end of the buffer chamber 160 to the bottom wall of the buffer chamber 160, so that the second wall surface 162 and the first wall surface 161 are axially symmetrical with respect to the center line of the buffer chamber 160. In other words, the buffer chamber 160 may have a regular tapered shape, and furthermore, the rotating shaft 121 can be supported more flexibly. In the axial direction away from the motor section 120, the gap between the first wall surface 161 and the rotating shaft 121 becomes larger, and the gap between the second wall surface 162 and the rotating shaft 121 becomes smaller, so that the buffer chamber 160 is configured in a reverse tapered shape. , it can be seen that during processing of the buffer chamber 160, the reversely tapered buffer chamber 160 is advantageous for mold cutting.

Further, the buffer chamber 160 has a ring-shaped structure, that is, the buffer chamber 160 is provided in the circumferential direction of the first bearing 140, and when the rotating shaft 121 rotates, the radial force received by the first bearing 140 is constantly reduced. that is, the first bearing 140 is subjected to varying radial forces in multiple directions, and no matter which direction the radial forces experienced by the first bearing 140 are directed, the ring-shaped buffer chamber 160 allows the first bearing 140 to be deformed to some extent, thereby connecting the rotating shaft 121 and the first bearing 140 flexibly, so that the first bearing 140 resists the force in the radial direction of the rotating shaft 121. The rigid connection between the rotating shaft 121 and the first bearing 140 avoids the problem that the first bearing 140 is easily damaged.

Example 3
Based on the above embodiments, this embodiment describes a support structure for the rotating shaft 121 of the pump device 100, and as shown in FIGS. 1, 4, and 5, the pump device 100 further includes a housing. 110 , a second bearing 170 that is fitted onto the rotating shaft 121 and located on the side of the pump section 130 remote from the first bearing 140 .

In this embodiment, the second bearing 170 is connected to the housing 110 and fitted onto the rotating shaft 121, and the second bearing 170 is located on the side of the pump section 130 remote from the first bearing 140, that is, The first bearing 140 and the second bearing 170 are respectively arranged on both sides of the pump section 130 in the axial direction, and the first bearing 140 is closer to the motor section 120 than the second bearing 170. The first bearing 140 and the second bearing 170 can play a role of supporting the rotating shaft 121, and by using the rotating shaft 121, the first bearing 140, and the second bearing 170 together, the load on the pump section 130 can be reduced. is equally distributed among the three parts of the rotating shaft 121, the first bearing 140, and the second bearing 170, and damage to the rotating shaft 121 that can occur due to load concentration on the rotating shaft 121 can be avoided.

Specifically, the first bearing 140 and the second bearing 170 are sliding bearings. Compared to double rolling bearings, sliding bearings operate smoothly, reliably, and without noise. Under liquid lubrication conditions, the sliding surfaces are separated by lubricating oil and do not come into direct contact, reducing friction loss and surface wear. In addition, the gap between the sliding bearing and the rotating shaft 121 is filled with lubricating oil, and the lubricating oil on the sliding surface forms a layer of oil, realizing fluid lubrication. , the oil film also has a certain vibration absorption ability, extending the service life of the first bearing 140, the second bearing 170 and the rotating shaft 121. Two sliding bearings support the rotating shaft 121, the play of the rotating shaft 121 is small, and the normal position of the axis of the rotating shaft 121 can be controlled within a reasonable range. Compared to a configuration in which both slide bearings are used, in this embodiment, only two sliding bearings are used, which not only simplifies the support structure but also reduces costs.

Furthermore, the first bearing 140 has a first bearing surface close to the rotating shaft 121, the second bearing 170 has a second bearing surface close to the rotating shaft 121, and the axial height of the second bearing surface is less than or equal to, i.e., less than or equal to, the axial height of the first bearing surface. When the distance between the first bearing 140 and the pump section 130 is the same as the distance between the second bearing 170 and the pump section 130, the loads from the pump section 130 carried by the first bearing 140 and the second bearing 170 are the same. It is. However, since the first bearing 140 is closer to the motor section 120 than the second bearing 170, a radial force is generated between the stator 123 and the rotor 122 during rotation of the rotor 122 of the motor section 120, and the rotating shaft 121, the first bearing 140 must also carry the load from the motor section 120. By making the second bearing surface below the first bearing surface, the first bearing 140 and The power consumption of the rotating shaft 121 can be minimized on the premise that the second bearing 170 is adapted to different load requirements at different positions of the rotating shaft 121 and the lubrication reliability of the rotating shaft 121 is guaranteed.

Further, as shown in FIG. 5, a portion of the inner wall of the second bearing 170 is recessed in a direction away from the rotating shaft 121 to form a second lubricating groove 171 that communicates with the first pressure chamber 131.

In this embodiment, the second lubricating groove 171 is formed by recessing a part of the inner wall of the second bearing 170 in a direction away from the rotating shaft 121, and the second lubricating groove 171 communicates with the first pressure chamber 131. Because of the pressure difference, the oil in the first pressure chamber 131 flows into the gap between the first bearing 140 and the rotating shaft 121 via the second lubricating groove 171, and as the rotating shaft 121 rotates, The oil in the second lubricating groove 171 is applied to the surface of the rotating shaft 121, where the second lubricating groove 171 can play the role of temporarily storing the lubricating oil, thereby making the second bearing 170 A fluid lubricating oil film is formed between the inner wall of the rotary shaft 121 and the rotating shaft 121, further ensuring lubrication performance between the rotating shaft 121 and the bearing.

Example 4
Based on the above-mentioned embodiments, this embodiment describes the specific structure of the second bearing 170, and furthermore, as shown in FIG. It includes a thrust lubricating groove 172 that is provided on an end surface near the shaft hole of the second bearing 170 and communicates with the shaft hole of the second bearing 170 .

In this embodiment, the thrust lubrication groove 172 is provided on the end surface of the second bearing 170 near the pump section 130, and the thrust lubrication groove 172 communicates with the shaft hole of the second bearing 170. The rotating shaft 121 cuts the lubricating oil in the fitting gap with the second bearing 170 during high-speed rotation, and the lubricating oil passes through the oil groove of the second bearing 170 to the thrust lubricating groove under the action of the cutting force. 172 to establish constant velocity and pressure. The end face of the inner gear and the end face of the pump lid 113 move relative to each other, and the lubricating oil in the thrust lubrication groove 172 can form an oil film between the contact surfaces of the end face of the inner gear and the end face of the pump lid 113. Hydrodynamic lubrication conditions are configured, which lubricates the gear and reduces noise, and can also create a thrust force on the gear, reducing power consumption and wear of the thrust surface, i.e. the sliding surface between the inner gear and the pump lid 113. can be significantly improved.

Specifically, the thrust lubrication groove 172 is provided on the end surface of the second bearing 170 near the pump section 130, and the thrust lubrication groove 172 communicates with the second bearing 170 and the shaft hole of the second bearing 170. There is lubricating oil in the fitting gap between the second bearing 170 and the rotating shaft 121, and during high-speed rotation of the rotating shaft 121, the rotating shaft 121 absorbs the lubricating oil in the fitting gap between itself and the second bearing 170. After cutting, the lubricating oil enters the thrust lubricating groove 172 from the fitting gap under the action of the cutting force ω, and at this time, the lubricating oil entering the thrust lubricating groove 172 has a constant speed and pressure. The contact end face clearance between the second bearing 170 and the pump part 130 is small, and the lubricating oil in the thrust lubrication groove 172 may flow into the end face clearance between the second bearing 170 and the pump part 130. Moreover, since the pump part 130 and the second bearing 170 move relatively, a fluid lubrication condition is established between the contact end surfaces of the pump part 130 and the second bearing 170, that is, the second bearing 170 and the pump part Since an oil film is formed on the contact end surface between the second bearing 170 and the pump section 130, the interface between the second bearing 170 and the pump section 130 transitions from boundary lubrication to fluid lubrication. It is possible to significantly improve the wear condition of the pump device 100, reduce power consumption, and also reduce the operating noise of the pump device 100.

Further, the area of the groove mouth in the axial direction of the thrust lubricating groove 172 is larger than the area of the groove bottom of the thrust lubricating groove 172.

In this embodiment, the thrust lubrication groove 172 includes two groove openings, and the two groove openings are oriented in different directions, with one groove opening facing the pump part 130 and the other groove opening facing the rotating shaft 121. In this design, the area of the groove mouth facing the pump part 130 is limited to be larger than the area of the groove bottom. In other words, the thrust lubricating groove 172 has a constricted shape in the axial direction away from the pump section 130, that is, in the direction from top to bottom. That is, the groove wall of the thrust lubrication groove 172 has an inclined shape, and at this time, the lubricating oil entering the thrust lubrication groove 172 has a constant speed and pressure, while the second bearing 170 and the pump part 130 are in contact with each other. Since the gap between the end faces is small, the groove wall of the thrust lubrication groove 172 has an inclined shape, and a wedge-shaped included angle converges between the thrust lubrication groove 172 and the end face gap, and the lubrication inside the thrust lubrication groove 172 is reduced. The oil flows along the inclined groove wall into the end face gap between the pump section 130 and the second bearing 170, that is, the lubricating oil enters from the "large port" to the "small port". Note that the "large mouth" refers to the thrust lubricating groove 172, and the "small mouth" refers to the gap between the second bearing 170 and the pump section 130. As a result, the lubricity between the pump section 130 and the second bearing 170 can be improved, so the lubrication state between them changes from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate between them. to lower the target.

Further, during high-speed rotation of the rotating shaft 121 and the pump part 130, a force is generated by the oil film between the contact surface of the pump part 130 and the second bearing 170 to push the pump part 130 upward, and thereby Since the lubricating oil located within the end faces of the second bearing 170 and the pump section 130 serves as a floating seal, leakage from the end faces can be further reduced. According to related literature, the end surface leakage of the pump device 100 accounts for 75% to 80% of the total leakage amount of the pump device 100, and therefore, improving the leakage between each contact end surface of the pump device 100 becomes most important. . Note that the lubricating oil has a constant viscosity.

Furthermore, the thrust lubrication groove 172 includes a thrust wall including at least one thrust segment, the at least one thrust segment including a first thrust segment, and the first thrust segment is configured to provide thrust lubrication in the axial direction away from the pump portion 130. It extends close to the center of groove 172.

In this embodiment, the thrust lubrication groove 172 includes a thrust wall that is an inclined wall. The thrust wall extends close to the center of the thrust lubrication groove 172 in an axial direction away from the pump section 130, ie, in a top-to-bottom direction. The thrust wall includes at least one thrust segment, and the at least one thrust segment includes a first thrust segment that extends proximate the center of thrust lubrication groove 172 in an axial direction away from pump section 130 . At this time, when an end face gap is formed between the end faces of the thrust lubrication groove 172, the pump part 130, and the second bearing 170, and a converging wedge-shaped included angle is formed between them, the lubrication inside the thrust lubrication groove 172 is The oil flows along the inclined first thrust segment into the end face gap between the pump part 130 and the second bearing 170, ie, the lubricating oil enters from the "big mouth" to the "small mouth". Note that the "large mouth" refers to the thrust lubricating groove 172, and the "small mouth" refers to the gap between the second bearing 170 and the pump section 130. Therefore, by increasing the lubricity between the pump section 130 and the second bearing 170, the lubrication state between the two changes from boundary lubrication to fluid lubrication, effectively reducing the wear rate between the two.

Note that the first thrust segment may include at least one straight segment and at least one curved segment, and the first thrust segment may include a first end close to the pump section 130 and a first end far from the pump section 130. and the second end of the first thrust segment extends close to the center of the thrust lubrication groove 172, i.e., the diagonally extending tendency of the first thrust segment is such that when the above relationship is satisfied, the lubrication oil can be made to flow easily. The first thrust segment may be composed of a plurality of curved surfaces or a plurality of circular arcs.

Furthermore, the included angle α between the first thrust segment and the axial end surface of the second bearing 170 is greater than 0° and less than 90°.

In this embodiment, the axial end surface of the second bearing 170 refers to the axial end surface on the second bearing 170 close to the pump part 130, and the included angle between the first thrust segment and the axial end surface is: Since 0°<α<90° is satisfied, the first thrust segment can better guide the lubricating oil into the end face gap between the second bearing 170 and the pump part 130, and the lubricating oil can be adjusted at its own speed. and the pressure and the guide of the first thrust segment ensure that it enters the end face clearance, and the thrust lubrication groove 172 and the end face clearance form a converging wedge-shaped included angle, and then the lubrication inside the thrust lubrication groove 172 The oil flows into the end face gap between the pump part 130 and the second bearing 170 along the inclined groove wall, that is, the lubricating oil enters from the "large mouth" to the "small mouth". Thereby, in order to improve the lubricity between the pump part 130 and the second bearing 170, the lubrication state between the two changes from boundary lubrication to fluid lubrication, effectively reducing the wear rate between the two. Further, the included angle α between the first thrust segment and the axial end face of the second bearing 170 is 45°. Note that by machining with a forming cutter, it is possible to machine the inclined first thrust segment on the end face of the second bearing 170 near the pump section 130. Specifically, the longitudinal section (along the axial direction) of the thrust lubricating groove 172 can have an inverted triangular shape, a semicircular shape, or the like.

Additionally, the at least one thrust segment further includes a second thrust segment extending axially and connected between the first thrust segment and the groove bottom of the thrust lubrication groove 172.

In this embodiment, the at least one thrust segment further includes a second thrust segment extending along the axial direction and connected to the first thrust segment and the groove bottom, and the second thrust segment and the first thrust segment are different from each other. Together they form a thrust wall, thereby ensuring that the volume of thrust lubrication groove 172 meets lubrication requirements. Note that during machining, the first thrust segment and the second thrust segment can be formed by machining a straight groove on the end face of the second bearing 170 facing the pump part 130 and then machining a chamfer, and the above machining order Accordingly, the difficulty in machining the thrust lubricating groove 172 can be reduced.

Furthermore, the number of thrust walls is at least two.

In such embodiments, the number of thrust walls is at least two, and each of the at least two thrust walls includes at least one thrust segment. The at least one thrust segment includes a first thrust segment. The at least one thrust segment further includes a second thrust segment. Note that the structures of at least two thrust walls may or may not be equal, and when the number of thrust walls is three, the structures of the three thrust walls may be partially equal, or Some parts do not have to be equal.

Further, the at least two thrust walls include a first thrust wall, a first end of the first thrust wall is coupled to an inner wall of the second bearing 170, and the first thrust wall and the inner wall of the second bearing 170 are connected to each other. The tangential plane on which the connection point is located is the first reference plane, and the included angle β1 between the first thrust wall and the first reference plane is 0° or more and less than 90°.

In this embodiment, the first end of the first thrust wall is the starting end of the first thrust wall, the second end of the first thrust wall is the terminal end of the first thrust wall, and the first end is the second bearing 170. The inner wall of the second bearing 170 is the side wall of the shaft hole of the second bearing 170. The tangential plane on which the connection point between the first end and the second bearing 170 is located is the first reference plane, and the included angle β1 between the first thrust wall and the first reference plane is 0° or more and less than 90°. be. During high-speed rotation of the rotating shaft 121, the rotating shaft 121 cuts the lubricating oil in the fitting gap between itself and the second bearing 170, and the lubricating oil is thrust from the fitting gap under the action of the cutting force ω. The lubricating oil entering the thrust lubricating groove 172 has a constant velocity and pressure. Since the first thrust wall is biased in the rotational direction of the rotating shaft 121, the lubricating oil in the thrust lubrication groove 172 is cut off in the shaft and the surface, and as a result, negative pressure is formed in the position of the thrust lubrication groove 172 near the shaft hole. Therefore, the lubricating oil between the rotating shaft 121 and the second bearing 170 is sucked, and the pressure at the position of the thrust lubricating groove 172 away from the shaft hole is high, and the lubricating oil in the thrust lubricating groove 172 is better absorbed by the inclined thrust wall. The flow can flow along the end face gap between the second bearing 170 and the pump part 130, and therefore, the lubricity between the pump part 130 and the second bearing 170 can be improved, and thereby the lubricity between them can be increased. The lubrication state changes from boundary lubrication to fluid lubrication, effectively reducing the wear rate between the two.

Furthermore, the at least two thrust walls further include a second thrust wall provided opposite to the first thrust wall, a first end of the second thrust wall being coupled to an inner wall of the second bearing 170, and a first end of the second thrust wall being connected to an inner wall of the second bearing 170. The tangential plane on which the connection point between the second thrust wall and the inner wall of the second bearing 170 is located is the second reference plane, and the included angle β2 between the second thrust wall and the second reference plane is less than 0°. It is largely less than 90°.

In such embodiments, the at least two thrust walls further include a second thrust wall, a first end of the second thrust wall being a beginning end of the second thrust wall, and a second end of the second thrust wall being a beginning end of the second thrust wall. A second end of the thrust wall is connected to an inner wall of the second bearing 170, and the inner wall of the second bearing 170 is a side wall of the shaft hole of the second bearing 170. The tangential plane on which the connection point between the first end and the second bearing 170 is located is the second reference plane, and the included angle β2 between the second thrust wall and the second reference plane is 0° or more and less than 90°. be. During high-speed rotation of the rotating shaft 121, the rotating shaft 121 cuts the lubricating oil in the fitting gap between itself and the second bearing 170, and the lubricating oil is thrust from the fitting gap under the action of the cutting force ω. The lubricating oil entering the lubrication groove 172, in this case the thrust lubrication groove 172, has a constant velocity and pressure. Since the second thrust wall is biased in the direction of rotation of the rotating shaft 121, the lubricating oil in the thrust lubrication groove 172 is cut off in the shaft and the surface, and as a result, negative pressure is formed in the position of the thrust lubrication groove 172 near the shaft hole. Therefore, the lubricating oil between the rotating shaft 121 and the second bearing 170 is sucked, and the pressure at the position of the thrust lubricating groove 172 away from the shaft hole is high, and the lubricating oil in the thrust lubricating groove 172 is better absorbed by the inclined thrust wall. The liquid can flow along the end face gap between the second bearing 170 and the pump part 130. Therefore, the lubricity between the pump part 130 and the second bearing 170 can be increased, and the lubrication state between the two changes from boundary lubrication to fluid lubrication, effectively reducing the wear rate between the two. let

Additionally, the at least two thrust walls further include a third thrust wall coupled to the second end of the first thrust wall and the second end of the second thrust wall, respectively.

In this embodiment, the at least two thrust walls further include a third thrust wall coupled to the second end of the first thrust wall and the second end of the second thrust wall, respectively. That is, since the first thrust wall, the second thrust wall, and the third thrust wall together constitute the thrust lubrication groove 172, the shape of the thrust lubrication groove 172 can be easily designed.

Note that the projection of the first thrust wall, the second thrust wall, and the third thrust wall on the axial end surface of the second bearing 170 may be a straight segment or a curved segment.

Furthermore, the third thrust wall of the thrust lubricating groove 172 is an arcuate wall.

In this embodiment, the third thrust wall is an arcuate wall, that is, the projection of the third thrust wall on the axial end face of the second bearing 170 is an arcuate segment. Since the position corresponding to the third thrust wall is far from the shaft hole of the thrust lubrication groove 172, the pressure of the lubricating oil corresponding to this position within the thrust lubrication groove 172 is high, causing the third thrust wall to form an arcuate shape. By forming a wall, the lubricating oil in the thrust lubricating groove 172 can easily flow, that is, the lubricating oil can easily enter from the "large mouth" to the "small mouth", improving the lubricity between the pump section 130 and the second bearing 170. As a result, the lubrication state between the two changes from boundary lubrication to fluid lubrication, effectively reducing the wear rate between the two.

Example 5
Based on the previous embodiment, this embodiment describes the lubricating oil path of the second bearing 170, and as shown in FIG. 4, the housing 110 includes a case 112 and a pump lid 113, and the case 112 , are disposed around the outside of the motor part 120 and the pump part 130, and the case 112 is connected to the first bearing 140. The pump lid 113 is connected to the case 112, the pump lid 113 forms a chamber 111 with the case 112, the pump lid 113 is connected to the second bearing 170, and a part of the pump lid 113 is directed away from the pump part 130. The extension portion 114 extends to form an oil pool 115. The shaft hole of the second bearing 170 is a through hole that penetrates in the axial direction, one end of the through hole is used to communicate with the thrust lubrication groove 172, and the other end of the through hole is used to communicate with the oil pool 115. .

In this embodiment, the housing 110 includes a case 112 and a pump lid 113 connected to the case 112, the pump lid 113 forms a chamber 111 with the case 112, and the case 112 includes a motor part 120 and a pump part 130. It is placed around the outside. The case 112 is connected to the first bearing 140 and the pump lid 113 is connected to the second bearing 170. The first bearing 140 may be integrally molded with the case 112, and the case 112 is integrally molded with the first bearing 140. Compared with post-processing methods, the connection strength is higher, space is saved, and the overall height of the machine is reduced. This makes it possible to reduce the difficulty of the manufacturing process and reduce manufacturing costs. The pump lid 113 may be integrally molded with the second bearing 170, which can save more height space and reduce the overall height of the machine, as well as reduce costs.

Furthermore, since the extension part 114 is formed in a structure in which a part of the pump lid 113 extends in a direction away from the pump part 130, the extension part 114 is integrally molded with the pump lid 113, and compared to a post-processing method, Strong connection strength. The extension 114 is used to form an oil pool 115 in which lubricating oil can be stored. The shaft hole of the second bearing 170 is a through hole that penetrates in the axial direction, and both ends of the through hole communicate with the thrust lubrication groove 172 and the oil pool 115, respectively.

Specifically, during high-speed rotation of the rotating shaft 121, the rotating shaft 121 cuts the lubricating oil in the fitting gap between itself and the second bearing 170, and the lubricating oil is removed under the action of the cutting force. The lubricating oil enters the thrust lubricating groove 172 from the fitting gap (through hole), and in this case, the lubricating oil that enters the thrust lubricating groove 172 has a constant velocity and pressure. Since the lubricating oil in the thrust lubricating groove 172 is subjected to shaft cutting and face cutting, a negative pressure is formed near the shaft hole of the thrust lubricating groove 172, and the lubricating oil between the rotating shaft 121 and the second bearing 170 is The pressure at the position of the thrust lubrication groove 172 away from the shaft hole is high, and the lubricating oil in the thrust lubrication groove 172 can be better pushed into the end face gap between the second bearing 170 and the pump part 130. . Therefore, the lubricity between the pump part 130 and the second bearing 170 can be improved, and the lubrication state between the two changes from boundary lubrication to fluid lubrication, effectively reducing the wear rate between the two. .

Furthermore, oil is pumped into the thrust lubrication groove 172 and then into the gap between the second bearing 170 and the pump part 130 to lubricate the contact surface between the pump part 130 and the second bearing 170. It then enters the oil pool 115 in the low pressure region under the influence of pressure differential and gravity.

Specifically, the lubricating oil path of the second bearing 170 is as follows. The oil enters the gap between the second bearing 170 and the rotating shaft 121 (through hole, second lubrication groove 171) via the oil pool 115, then enters the thrust lubrication groove 172, and is then under the action of the thrust lubrication groove 172. Then, the oil enters the end face clearance between the pump part 130 and the second bearing 170, and enters the low pressure oil pool 115 under the action of the pressure difference and gravity. Forming a complete lubricating oil path for the second bearing 170 is advantageous in ensuring lubrication performance between the second bearing 170 and the rotating shaft 121.

In addition, the pump lid 113 is integrally molded with the second bearing 170, which has higher connection strength than post-processing methods, saves space, reduces the overall height of the machine, and reduces the difficulty of the manufacturing process. It is possible to reduce the manufacturing cost.

Example 6
Based on the previous embodiment, this embodiment describes another lubricant path of the second bearing 170, and further, as shown in FIG. 1, the housing 110 includes a case 112 and a pump lid 113, and the case 112 is provided around the outside of the motor section 120 and the pump section 130, and the case 112 is connected to the first bearing 140. The pump lid 113 is connected to the case 112 to form a chamber 111 with the case 112, and is connected to the second bearing 170, and the shaft hole of the second bearing 170 is a blind hole with one end open. The communication groove is opened in the second bearing 170 and/or the pump lid 113, and the communication groove communicates the first pressure chamber 131 with the blind hole.

In this embodiment, the housing 110 includes a case 112 and a pump lid 113 connected to the case 112, the pump lid 113 forms a chamber 111 with the case 112, and the case 112 includes a motor part 120 and a pump part 130. It is placed around the outside of the area. The case 112 is connected to the first bearing 140 and the pump lid 113 is connected to the second bearing 170. The first bearing 140 may be integrally molded with the case 112, and the case 112 is integrally molded with the first bearing 140. Compared with post-processing methods, the connection strength is higher, space is saved, and the overall height of the machine is reduced. This makes it possible to reduce the difficulty of the manufacturing process and reduce manufacturing costs. The pump lid 113 may be integrally molded with the second bearing 170, which can save more height space and reduce the overall height of the machine, as well as reduce costs.

Furthermore, the shaft hole of the second bearing 170 is a blind hole with one end open, and the communication groove is opened in the second bearing 170 and/or the pump lid 113, and the communication groove connects the first pressure chamber 131 and the blind hole. Used to communicate. Specifically, the lubricating oil path of the second bearing 170 is as follows. The pressurized oil enters the blind hole (the gap between the second bearing 170 and the rotating shaft 121, the second lubricating groove 171) from the first pressure chamber 131 (high pressure chamber) via the communication groove, and then enters the second lubricating groove 171. It returns to the low pressure area via the gap between the two bearings 170 and the pump part 130, and the low pressure area here specifically refers to the oil supply port 181 and the second pressure chamber 132. By forming a complete lubricating oil path for the second bearing 170, it is advantageous to ensure the lubrication performance between the second bearing 170 and the rotating shaft 121.

Example 7
Based on the above embodiments, this embodiment describes the specific structure of the pump section 130, and furthermore, as shown in FIGS. 1 and 4, the pump section 130 includes a first rotating member 133 and a second It includes a rotating member 134 , and the first rotating member 133 is fitted with the rotating shaft 121 . The second rotating member 134 is provided outside the first rotating member 133, the second rotating member 134 is rotatable in conjunction with the first rotating member 133, and the second rotating member 134 is connected to the first rotating member 133. A first pressure chamber 131 and a second pressure chamber 132 are configured. The pump device 100 further includes an oil supply port 181 and an oil outlet 182, the oil supply port 181 is opened in the pump lid 113 and/or the second bearing 170 in the axial direction, and the oil supply port 181 is connected to the second pressure chamber. 132 , the oil outlet 182 is radially opened in the pump lid 113 and the second bearing 170 , and the oil outlet 182 communicates with the first pressure chamber 131 of the pump part 130 .

In this embodiment, the pump section 130 includes a first rotating member 133 and a second rotating member 134, the first rotating member 133 is fitted with the rotating shaft 121, and the second rotating member 134 is connected to the first rotating member 133. The second rotating member 134 is rotatable in conjunction with the first rotating member 133. This is because the rotating shaft 121 operates the second rotating member 134 via the first rotating member 133. I understand that it is possible. By installing the structure of the first rotating member 133 and the second rotating member 134, a first pressure chamber 131 and a second pressure chamber 132 are formed, and the first pressure chamber 131 is a high pressure chamber and the second pressure chamber is a high pressure chamber. 132 is a low pressure chamber.

Note that the first rotating member 133 is an inner gear, and the second rotating member 134 is an outer gear, that is, the pump section 130 is a gear pump. Specifically, in the meshing process of a gear pump, while the front pair of teeth have not yet come out of mesh, the rear pair of teeth has already entered the meshing process, and each internal tooth surface is all in contact with the external tooth surface. As the inner gear rotates, the volume of the sealed storage chamber 111 changes, and if it cannot communicate with the unloading channel, a trapped volume is formed. Since the compressibility of liquid is very low, when the confinement volume changes from large to small, the liquid present in the confinement volume is pushed and the pressure increases rapidly, which significantly increases the operating pressure of the gear pump. surpass. Also, since the liquid in the containment volume is also forced through all leakable slits, both the rotating shaft 121 and the bearings are subjected to very high shock loads, increasing power losses, heating the oil, and making noise. and vibration will occur, reducing the smoothness of operation and service life of the gear pump. When the confinement volume increases from small to large, a vacuum is formed and the air dissolved in the liquid is separated and bubbles are generated, resulting in harmful effects such as cavitation, noise, vibration, flow rate, and pressure pulsations. As a method to solve the entrapment phenomenon, unloading grooves are opened in the lids at both ends of the gear, and when the sealed volume becomes small, the unloading groove communicates with the pressure oil chamber, and when the sealed volume becomes large, the unloading groove is opened. A method of communicating with the oil absorption chamber via a groove is adopted.

Specifically, the inner gear meshes with the contour of the conjugate curved tooth profile of the outer gear, so that the teeth are in contact with each other, and the outer gears are interlocked and rotated in the same direction. The inner cavity of the outer gear is partitioned into a plurality of operating chambers by the inner gear, and since the centers of the inner gear and the outer gear are offset, the volumes of the plurality of operating chambers change with the rotation of the rotor 122, and the volume increases. A constant vacuum is created in the region, an oil supply inlet 181 is provided at that location, the pressure in the region of decreasing volume is higher, and an oil outlet 182 is correspondingly provided here.

Furthermore, the pump device 100 further includes an oil supply port 181 and an oil outlet 182, the oil supply port 181 is opened in the pump lid 113 and/or the second bearing 170 in the axial direction, and the oil supply port 181 is opened in the pump lid 113 and/or the second bearing 170 in the axial direction. It communicates with the second pressure chamber 132 . Since the second pressure chamber 132 is a low pressure chamber and has a pressure difference with the outside, oil enters the second pressure chamber 132 through the oil supply port 181. The oil outlet 182 is opened in the pump lid 113 and the second bearing 170 in the radial direction, and communicates with the first pressure chamber 131 . Since the first pressure chamber 131 is a high pressure chamber and has a pressure difference with the outside, the oil in the first pressure chamber 131 flows out through the oil outlet 182. That is, the main oil passage of the pump device 100 is as follows. Negative pressure can be generated in the second pressure chamber 132 and the oil supply port 181, and under the action of the negative pressure, oil in the oil pool 115 is sucked into the oil supply port 181 and flows into the second pressure chamber 132 (low pressure chamber). The oil entering the second pressure chamber 132 enters the high pressure chamber and is pressurized under the action of the first rotating member 133 and the second rotating member 134, and the pressurized oil is discharged through the oil outlet 182. be done.

The design principle of the oil supply port 181 and the oil outlet 182 is as follows. In the process of ensuring the rotation of the gear, the oil supply port 181 is communicated between the teeth of the first rotating member 133 and the second rotating member 134 as soon as possible, and the gear volume is increased until the maximum volume is formed in the inner gear and the outer gear. The chamber always communicates with the oil supply port 181, and it is necessary to extend the oil filling time as much as possible so that the volume chamber between the internal and external teeth is filled with oil and the amount of oil absorption is guaranteed. The oil outlet 182 is also connected to the high-pressure oil between the teeth as soon as possible to reduce the overcompression work between the teeth, and is closed as late as possible to fully utilize the inertia of the fluid to exhaust the oil between the teeth. , improving the volumetric efficiency of internally meshing gear type oil pumps. However, it should be noted that when the inner gear and the outer gear form the maximum volume, they cannot communicate with the oil supply port 181 to avoid affecting the volumetric efficiency of the pump device 100 at low speed.

Example 8
Based on the above embodiments, this embodiment describes the specific structure of the motor section 120, and furthermore, as shown in FIGS. 1 and 4, the motor section 120 further includes a rotor 122 and a stator 123. The rotor 122 is connected to the rotating shaft 121, the stator 123 is fitted on the outside of the rotor 122, the stator 123 includes a stator core and a stator winding, and the stator winding is provided on the stator core. The pump device 100 further includes a control section 190 provided on the side of the motor section 120 remote from the pump section 130, the control section 190 is connected to the housing 110 and located in the chamber 111, and controls the stator windings. The end portion is electrically connected to the control unit 190.

In this embodiment, the motor section 120 further includes a rotor 122 and a stator 123. Here, the rotor 122 is connected to the rotating shaft 121, and the rotor 122 and the rotating shaft 121 may be coaxially provided, and the fitting method of the rotor 122 and the rotating shaft 121 is an interference fit. Although the rotor 122 and the rotating shaft 121 may be provided on different axes, they are communicably connected and may be provided flexibly depending on the actual situation. The stator 123 is fitted on the outside of the rotor 122, and includes a stator core and a stator winding, and the stator winding is provided on the stator core.

Further, the pump device 100 further includes a control unit 190 provided on a side of the motor unit 120 remote from the pump unit 130, that is, the control unit 190 is provided at a position remote from the pump unit 130 of the motor unit 120. During operation, the vibration near the pump part 130 is obvious and the load it receives is large, so the control part 190 is moved away from the pump part 130, which can play a role of protecting the control part 190 to some extent, and the control Extending the useful life of part 190.

Further, the control section 190 is connected to the housing 110 and located in the chamber 111, and the ends of the stator windings are electrically connected to the control section 190.

Specifically, during operation of the pump device 100, the control unit 190 controls the stator 123 so that the current in the stator winding in the stator 123 changes according to a certain rule, thereby controlling the excitation magnetic field that changes. is generated, and the rotor 122 rotates under the action of the excitation magnetic field, so that the first rotating member 133 in the pump section 130 rotates in conjunction with the rotating shaft 121, and further, the second rotating member 134 moves. Become. When the first rotating member 133 and the second rotating member 134 in the pump section 130 rotate, the second rotating member 134 moves unevenly, so that the compression formed between the first rotating member 133 and the second rotating member 134 The change in the volume of the chamber generates power that forces the working medium that has entered the compression chamber to flow toward the oil outlet 182.

Example 9
As shown in FIG. 6, the embodiment of the second aspect of the present application provides a vehicle 200 including the pump device 100 of any one of the embodiments described above. Since the vehicle 200 provided in the present application includes the pump device 100 of any one of the embodiments described above, it also has the beneficial effects of any one of the embodiments described above, and a detailed explanation will be given here. Omitted.

Note that vehicle 200 may be a new energy vehicle. Here, new energy vehicles include pure electric vehicles, extended range electric vehicles, hybrid vehicles, fuel cell vehicles, hydrogen engine vehicles, etc. Of course, vehicle 200 may be a conventional gasoline vehicle.

In one specific example, vehicle 200 includes a vehicle body 210 and an engine 220. Both the pump device 100 and the engine 220 are provided in the vehicle body 210, and the engine 220 includes a mounting seat 221 connected to the extension portion 114 of the pump device 100. As a result, an oil pool 115 is formed, and further, the oil pool 115 is communicated with the oil source of the engine 220 to realize oil passage communication.

In a specific application, when the vehicle 200 is a new energy vehicle, the engine 220 is an electric motor, and when the vehicle 200 is a gasoline vehicle, the engine 220 is a fuel engine.

In this application, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as stating or implying relative importance. The term "plurality" means two or more than one, unless specifically limited otherwise. The terms "mounting", "coupling", "connecting", "fixing" etc. should all be understood broadly, e.g. "connecting" may be fixedly connected or removably connected. They may be connected or integrally connected, and a "coupling" may be directly connected or indirectly connected through an intermediate interposition. Those skilled in the art can understand the specific meanings of the above terms in this application based on the specific situation.

In the explanation of this application, the orientation or positional relationship indicated by terms such as "top", "bottom", "left", "right", "front", "rear", etc. is based on the orientation or positional relationship shown in the drawings. and are used solely for the purpose of explaining the present application and for ease of explanation, and do not imply that the devices or units shown necessarily have a particular orientation or must be constructed and operated in a particular orientation. It should be understood that nothing is stated or implied and therefore cannot be construed as limiting the present application.

As used herein, the terms "one embodiment," "some embodiments," "specific embodiments," and the like refer to the features, structure, materials, or advantages of the details described in the embodiment or illustration. are intended to be included in at least one embodiment or illustration of this application. As used herein, exemplary references to the above terms do not necessarily refer to the same embodiment or illustration. Moreover, the described features, structures, materials or advantages may be combined in any suitable manner in any one or more embodiments or illustrations.

The above is only a preferred embodiment of the present application, and is not intended to limit the present application, and those skilled in the art can make various modifications and changes to the present application. All modifications, equivalent substitutions, improvements, etc. made within the scope of the present application shall be included in the protection scope of the present application.

100...pump device,
110... Housing, 111... Chamber, 112... Case, 113... Pump lid, 114... Extension part, 115... Oil pool,
120...Motor section, 121...Rotating shaft, 122...Rotor, 123...Stator,
130... Pump part, 131... First pressure chamber, 132... Second pressure chamber, 133... First rotating member, 134... Second rotating member,
140...first bearing, 141...first oil groove, 142...throttle groove, 143...first lubrication groove, 144...pressure relief groove,
150... Seal member, 151... Liquid passage chamber,
160... Buffer chamber, 161... First wall surface, 162... Second wall surface,
170...Second bearing, 171...Second lubrication groove, 172...Thrust lubrication groove,
181...Oil supply port, 182...Oil outlet,
190...control unit,
200...vehicle,
210...Vehicle body,
220...Engine, 221...Mounting seat.

Claims (18)

a housing having a chamber;
a motor section including a rotating shaft that rotates around a central axis;
It is provided on one side of the motor section in the axial direction, contacts the rotating shaft, is rotatable in conjunction with the rotating shaft, and includes a first pressure chamber and a second pressure chamber, and includes a first pressure chamber and a second pressure chamber. a pump portion whose pressure is greater than the pressure received by the second pressure chamber;
a first bearing connected to the housing, fitted onto the rotating shaft, and located between the motor section and the pump section;
a first oil groove provided on a first end face of the first bearing facing the pump section and communicating with the first pressure chamber;
A pump device comprising: a throttle groove provided in the first end surface and communicating the first oil groove and a gap between the first bearing and the rotating shaft,
The pump device further includes a buffer chamber provided at an end face of the first bearing remote from the pump section . The pump device according to claim 1, wherein a part of the inner wall of the first bearing is recessed in a direction away from the rotating shaft to form a first lubricating groove communicating with the throttle groove. The pump device according to claim 2, wherein a ratio of a flow passage cross-sectional area of the throttle groove to a flow passage cross-sectional area of the first lubricating groove is 0.1 or more and 0.4 or less. 3. The pump device according to claim 2, wherein a ratio between a flow path cross-sectional area of the first lubricating groove and a cross-sectional area of the shaft hole of the first bearing is 0.02 or more and 0.08 or less. The pump device further includes a seal member connected to a side of the first bearing remote from the pump section,
2. The sealing member is fitted onto the rotating shaft, and the sealing member, the first bearing, and the rotating shaft form a liquid passage chamber, and the liquid passage chamber communicates with the first lubricating groove. Pump device described in. The pump device according to claim 5, further comprising a pressure relief groove provided in the first bearing and communicating the liquid passage chamber and the second pressure chamber. 7. The pump device according to claim 6, wherein a ratio of a flow passage cross-sectional area of the pressure relief groove to a flow passage cross-sectional area of the first lubrication groove is 1 or more and 4 or less. The buffer chamber has a tapered shape extending along the rotation axis from an end surface of the first bearing remote from the pump section, and the area of the opening of the buffer chamber is larger than the area of the bottom wall of the buffer chamber. The pump device according to claim 1 , wherein the pump device is also large. The buffer chamber has a tapered shape extending along the rotation axis from an end surface of the first bearing remote from the pump part, and the buffer chamber has a first wall surface that is close to the rotation axis of the buffer chamber. 1 wall included,
The pump device according to claim 1 , wherein a distance between the first wall surface and the rotating shaft increases from an open end of the buffer chamber to a bottom wall of the buffer chamber. The buffer chamber includes a second wall surface provided opposite to the first wall surface,
10. The pump device according to claim 9 , wherein a distance between the second wall surface and the rotating shaft decreases from an open end of the buffer chamber to a bottom wall of the buffer chamber. The pump device includes:
According to any one of claims 1 to 10 , further comprising a second bearing connected to the housing, fitted onto the rotating shaft, and located on a side of the pump section remote from the first bearing. pump equipment. The pump device according to claim 11 , wherein a part of the inner wall of the second bearing is recessed in a direction away from the rotating shaft to form a second lubricating groove communicating with the first pressure chamber. The pump device according to claim 11 , further comprising a thrust lubricating groove provided on an end surface of the second bearing near the pump portion and communicating with a shaft hole of the second bearing. The housing includes:
a case disposed around the outside of the motor section and the pump section and connected to the first bearing;
An extension part is connected to the case to form the chamber with the case, is connected to the second bearing, and has a portion extending away from the pump part to form an oil pool. including a pump lid;
The shaft hole of the second bearing is a through hole that penetrates in the axial direction, one end of the through hole communicates with the thrust lubrication groove, and the other end of the through hole communicates with the oil pool. The pump device according to claim 13 , which is used. The housing includes:
a case disposed around the outside of the motor section and the pump section and connected to the first bearing;
a pump lid connected to the case, forming the chamber with the case, and connected to the second bearing, the shaft hole being a blind hole with an open end;
The pump device according to claim 12 , further comprising a communication groove opened in the second bearing and/or the pump lid and communicating the first pressure chamber and the blind hole. The pump section is
a first rotating member that fits with the rotating shaft;
a second rotating member that is provided outside the first rotating member, is rotatable in conjunction with the first rotating member, and configures the first rotating member, the first pressure chamber, and the second pressure chamber; including;
The pump device includes:
an oil supply port opened in the pump lid and/or the second bearing in the axial direction and communicating with the second pressure chamber;
The pump device according to claim 14 or 15 , further comprising an oil outlet opened in the pump lid and the second bearing in a radial direction and communicating with the first pressure chamber of the pump section. The motor section is
a rotor connected to the rotating shaft;
further comprising a stator fitted outside the rotor and including a stator core and a stator winding provided on the stator core,
The pump device includes:
further comprising a control unit provided on a side of the motor unit remote from the pump unit, connected to the housing, located within the chamber, and electrically connected to an end of the stator winding; A pump device according to any one of claims 1 to 10 . A vehicle comprising a pump device according to any one of claims 1 to 17 .

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