CN114135383B

CN114135383B - Pump device and vehicle

Info

Publication number: CN114135383B
Application number: CN202010913984.8A
Authority: CN
Inventors: 曹小军; 化豪爽; 付威; 葛笑; 江波
Original assignee: Guangdong Welling Auto Parts Co Ltd; Anhui Welling Auto Parts Co Ltd
Current assignee: Guangdong Welling Auto Parts Co Ltd; Anhui Welling Auto Parts Co Ltd
Priority date: 2020-09-03
Filing date: 2020-09-03
Publication date: 2024-06-21
Anticipated expiration: 2040-09-03
Also published as: CN114135383A

Abstract

The invention provides a pump device and a vehicle. Wherein, the casing has the cavity. The motor portion is disposed in the cavity, and the motor portion includes a rotating shaft rotating around a central axis of the motor portion. The pump part is arranged on one axial side of the motor part and is contacted with the rotating shaft, and the pump part can be driven by the rotating shaft to rotate. The first bearing is connected with the shell and sleeved on the rotating shaft, and the first bearing is positioned on one side of the pump part, which is away from the motor part. The thrust lubrication groove is arranged on the end face of the first bearing close to the pump part and is communicated with the shaft hole of the first bearing. The lubricating oil in the thrust lubrication groove can flow to the end surface clearance of the first bearing and the pump part, so that the contact end surfaces of the first bearing and the pump part form fluid lubrication, the abrasion condition of the contact end surfaces of the pump part and the first bearing is greatly improved, the power consumption is reduced, and in addition, the running noise of the pump device can be reduced.

Description

Pump device and vehicle

Technical Field

The invention relates to the technical field of pump devices, in particular to a pump device and a vehicle.

Background

At present, the pump device comprises a motor part and a pump part, and a rotating shaft in the motor part drives the pump part to rotate, so that liquid compression is realized. However, during the high-speed rotation of the pump portion, the pump portion will be in contact with other structures of the pump device to wear, and although the lubricant exists on the contact surface of the pump portion with other structures, the planar contact can only achieve boundary lubrication due to the planar contact of the end surface of the pump portion, and in the state of boundary lubrication, the wear resistance of the pump device is poor.

Disclosure of Invention

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

To this end, a first aspect of the invention is directed to a pump device.

A second aspect of the present invention is to provide a vehicle.

In view of this, according to a first aspect of the present invention, there is provided a pump device including a housing, a motor portion, a pump portion, a first bearing, and a thrust lubrication groove. Wherein, the casing has the cavity. The motor portion is disposed in the cavity, and the motor portion includes a rotating shaft rotating around a central axis of the motor portion. The pump part is arranged on one axial side of the motor part and is contacted with the rotating shaft, and the pump part can be driven by the rotating shaft to rotate. The first bearing is connected with the shell and sleeved on the rotating shaft, and the first bearing is positioned on one side of the pump part, which is away from the motor part. The thrust lubrication groove is arranged on the end face of the first bearing close to the pump part and is communicated with the shaft hole of the first bearing.

The invention provides a pump device which comprises a shell, a motor part, a pump part, a first bearing and a thrust lubrication groove. The shell is provided with a cavity, and the motor part and the pump part are both accommodated in the shell, so that the motor part and the pump part are ensured not to be influenced by external environment through the shell, and can normally operate.

Further, the motor portion includes a rotation shaft around a central axis of the motor portion. The pump portion is arranged on one axial side of the motor portion, and the pump portion is in contact with the rotating shaft of the motor portion. Specifically, the pump part is in interference fit with the rotating shaft, so that the rotating shaft can drive the pump part to rotate, namely, the rotating shaft drives the pump part to synchronously move.

Further, the first bearing is arranged on one side, far away from the motor part, of the pump part, the first bearing is sleeved on the rotating shaft and is a sliding bearing, and the first bearing can provide a supporting effect for the rotating shaft. It is worth noting that, the first bearing can provide lubrication support to the pivot, because the axle center coincidence of first bearing and pivot, in actual operation in-process, the pump part rotates of pivot drive, therefore the pump part can exert radial direction's power to the pivot, the pivot can promote first bearing and incline towards one side when receiving radial force, at this moment, pivot and first bearing contact, first bearing will provide the supporting role to the pivot, thereby can control the play of pivot in reasonable within range, thereby the control of pivot axle center of being convenient for.

By plain bearing is meant a bearing that operates under sliding friction. Compared with the form of double rolling bearings, the sliding bearing works stably and reliably without noise, the sliding surface is separated by the lubricating oil without direct contact under the condition of liquid lubrication, friction loss and surface abrasion can be greatly reduced, a gap between the sliding bearing and a rotating shaft is filled with the lubricating oil, the lubricating oil on the sliding surface can form a layer of oil film, fluid lubrication is realized, the oil film also has certain shock absorption capacity, and the service life of the first bearing and the rotating shaft is prolonged.

In addition, a thrust lubrication groove is provided on an end face of the first bearing near the pump portion, the thrust lubrication groove being in communication with the first bearing and the shaft hole of the first bearing. The lubricating oil is arranged in the fit clearance between the first bearing and the rotating shaft, the rotating shaft can shear the lubricating oil in the fit clearance between the rotating shaft and the first bearing in the high-speed rotating process, the lubricating oil can enter the thrust lubricating groove from the fit clearance under the action of the shearing force omega, and the lubricating oil entering the thrust lubricating groove has certain speed and pressure. The end surface clearance between the first bearing and the pump part is small, and the lubricating oil in the thrust lubricating groove can flow to the end surface clearance between the first bearing and the pump part. Meanwhile, because the pump part and the first bearing have relative motion, a fluid lubrication condition is formed between the contact end surfaces of the pump part and the first bearing, namely, an oil film is formed at the contact end surfaces of the first bearing and the pump part, so that the boundary lubrication between the first bearing and the pump part is transited to the fluid lubrication, the abrasion condition of the contact end surfaces of the pump part and the first bearing can be greatly improved, the power consumption is reduced, and in addition, the running noise of the pump device can be reduced.

In one possible design, the area of the notch of the thrust lubrication groove in the axial direction is further greater than the area of the groove bottom of the thrust lubrication groove.

In this design, the thrust lubrication groove includes two notches, the orientations of the two notches being different, one toward the pump portion and the other toward the spindle. The area of the slot defined towards the pump portion in this design is greater than the area of the slot bottom. That is, the thrust lubrication groove is necked in an axial direction away from the pump portion, i.e., in a top-down direction. The groove wall of the thrust lubrication groove is inclined, at this time, on one hand, because the lubricating oil entering the thrust lubrication groove has a certain speed and pressure, on the other hand, because the gap between the end face of the first bearing and the end face of the pump part is smaller, the groove wall of the thrust lubrication groove is inclined, and then a convergent wedge-shaped included angle is formed between the thrust lubrication groove and the end face gap, and the lubricating oil in the thrust lubrication groove flows into the end face gap of the pump part and the first bearing along the inclined groove wall, namely, the lubricating oil enters a small opening from a big opening, which is worth to say, the big opening refers to the thrust lubrication groove, and the small opening refers to the gap between the first bearing and the pump part. Thereby, lubrication between the pump part and the first bearing can be enhanced, so that the lubrication state between the pump part and the first bearing is transited from boundary lubrication to fluid lubrication, and the wear rate between the pump part and the first bearing is effectively reduced.

In addition, in the process of rotating the rotating shaft and the pump part at a high speed, an oil film between the contact surfaces of the pump part and the first bearing can generate a force F for pushing the pump part to move upwards, so that lubricating oil in the end surfaces of the first bearing and the pump part plays a role in floating sealing, and the end surface leakage can be further reduced. It has been shown in the relevant literature that the end face leakage of the pump device accounts for 75% to 80% of the total leakage of the pump device, and therefore it is important to improve the leakage between the individual contact end faces in the pump device. It is worth noting that the lubricating oil has a certain viscosity.

In one possible design, the thrust lubrication groove further comprises a thrust wall comprising at least one thrust segment, the at least one thrust segment comprising a first thrust segment extending near the center of the thrust lubrication groove in an axial direction away from the pump portion.

In this design, the thrust lubrication groove includes a thrust wall that is an inclined wall. The thrust wall extends close to the centre of the thrust lubrication groove in an axial direction facing away from the pump portion, i.e. in a top-down direction. The thrust wall comprises at least one thrust segment, which comprises a first thrust segment extending close to the centre of the thrust lubrication groove in an axial direction facing away from the pump portion. At this time, the thrust lubrication groove, the pump portion and the end face of the first bearing form an end face gap therebetween, and a converging wedge-shaped included angle is formed between the thrust lubrication groove and the end face gap, so that the lubrication oil in the thrust lubrication groove flows into the end face gap between the pump portion and the first bearing along the inclined first thrust section, i.e. the lubrication oil enters the small port from the large port. It should be noted that "large port" refers to the thrust lubrication groove, and "small port" refers to the gap between the first bearing and the pump portion. Thereby, lubrication between the pump part and the first bearing can be enhanced, so that the lubrication state between the pump part and the first bearing is transited from boundary lubrication to fluid lubrication, and the wear rate between the pump part and the first bearing is effectively reduced.

It should be noted that the first thrust segment may be at least one straight segment and at least one curved segment, where the first thrust segment has a first end close to the pump portion and a second end far from the pump portion, and the second end of the first thrust segment extends close to the center of the thrust lubrication groove, that is, the inclined extending trend of the first thrust segment satisfies the above relationship, so that the flow of the lubricating oil can be facilitated. The first thrust section may be formed by a plurality of curved surfaces or may be formed by a plurality of circular arcs.

In one possible design, the angle α between the first thrust segment and the axial end face of the first bearing is further greater than 0 ° and less than 90 °.

In the design, the axial end face of the first bearing refers to the axial end face, close to the pump part, on the first bearing, an included angle between the first thrust section and the axial end face is satisfied, and 0 degrees is less than alpha and less than 90 degrees, so that the first thrust section can better guide lubricating oil into an end face gap between the first bearing and the pump part, ensure that the lubricating oil can flow into the end face gap through the speed and the pressure of the first thrust section, and lead the lubricating oil to enter the end face gap through the guide of the first thrust section, so that a convergent wedge-shaped included angle is formed between the thrust lubrication groove and the end face gap, and the lubricating oil in the thrust lubrication groove can flow into the end face gap between the pump part and the first bearing along the inclined groove wall, namely, the lubricating oil enters a small opening from a large opening. Thereby, lubrication between the pump part and the first bearing can be enhanced, so that the lubrication state between the pump part and the first bearing is transited from boundary lubrication to fluid lubrication, and the wear rate between the pump part and the first bearing is effectively reduced. Further, an included angle α between the first thrust segment and the axial end face of the first bearing is 45 °. It should be noted that the inclined first thrust segment may be machined on the end surface of the first bearing adjacent to the pump portion by machining with a forming cutter. Specifically, the longitudinal section (in the axial direction) of the thrust lubrication groove may be inverted triangle, semicircle, or the like.

In one possible design, the at least one thrust segment further comprises a second thrust segment extending axially and connected between the first thrust segment and the groove bottom of the thrust lubrication groove.

In this design, at least one thrust section still includes the second thrust section, and the second thrust section extends in order to connect at first thrust section and tank bottom along the axial, and the second thrust section cooperates with first thrust section in order to form the thrust wall jointly to ensure that the volume of thrust lubrication groove satisfies the lubrication demand. It is worth to say that during the processing, processing straight flute on the terminal surface that first bearing was towards pump portion, then processing chamfer to can form first thrust section and second thrust section, through above-mentioned processing order, can reduce the processing degree of difficulty of thrust lubrication groove.

In one possible design, further, the number of thrust walls is at least two.

In this design, the number of thrust walls is at least two, each of the at least two thrust walls including 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. It should be noted that, the structures of at least two thrust walls may be equal or unequal, and when the number of the thrust walls is three, the structures of the three thrust walls may be partially equal or partially unequal.

In one possible design, further, the at least two thrust walls include a first thrust wall, a first end of the first thrust wall is connected with an inner side wall of the first bearing, a section where a connection point of the first thrust wall and the inner side wall of the first bearing is located is a first reference plane, and an included angle β1 between the first thrust wall and the first reference plane is greater than or equal to 0 ° and smaller than 90 °.

In the design, 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 terminating end of the first thrust wall, the first end is connected with the inner side wall of the first bearing, and the inner side wall of the first bearing is the side wall of the shaft hole of the first bearing. The tangent plane at the junction of first end and first bearing is first reference surface, and contained angle β1 between first thrust wall and the first reference surface is more than or equal to 0, is less than 90. In the high-speed rotation process of the rotating shaft, the rotating shaft can shear lubricating oil in a fit clearance between the rotating shaft and the first bearing, the lubricating oil can enter the thrust lubrication groove from the fit clearance under the action of shearing force omega, and the lubricating oil entering the thrust lubrication groove has certain speed and pressure. Because the first thrust wall is biased to the rotating direction of the rotating shaft, the lubricating oil in the thrust lubrication groove can generate shaft shearing and surface shearing, so that negative pressure is formed at the position of the thrust lubrication groove close to the shaft hole, so that the lubricating oil between the rotating shaft and the first bearing is sucked, and the pressure at the position of the thrust lubrication groove far away from the shaft hole is higher, the lubricating oil in the thrust lubrication groove can better flow into an end surface gap between the first bearing and the pump part along the inclined thrust wall, namely, the lubricating oil enters a small opening from a large opening. Thereby, lubrication between the pump part and the first bearing can be enhanced, so that the lubrication state between the pump part and the first bearing is transited from boundary lubrication to fluid lubrication, and the wear rate between the pump part and the first bearing is effectively reduced.

In one possible design, further, the at least two thrust walls further include a second thrust wall, the second thrust wall is opposite to the first thrust wall, a first end of the second thrust wall is connected with an inner side wall of the first bearing, a section where a connection point of the second thrust wall and the inner side wall of the first bearing is located is a second reference plane, and an included angle beta 2 between the second thrust wall and the second reference plane is greater than 0 ° and smaller than 90 °.

In the design, the at least two thrust walls further comprise a second thrust wall, the first end of the second thrust wall is the starting end of the second thrust wall, the second end of the second thrust wall is the ending end of the second thrust wall, the second end is connected with the inner side wall of the first bearing, and the inner side wall of the first bearing is the side wall of the shaft hole of the first bearing. The tangent plane at the junction of first end and first bearing is the second reference surface, and contained angle beta 2 between second thrust wall and the second reference surface is more than or equal to 0, is less than 90. In the high-speed rotation process of the rotating shaft, the rotating shaft can shear lubricating oil in a fit clearance between the rotating shaft and the first bearing, the lubricating oil can enter the thrust lubrication groove from the fit clearance under the action of shearing force omega, and the lubricating oil entering the thrust lubrication groove has certain speed and pressure. Because the second thrust wall is biased to the rotating direction of the rotating shaft, the lubricating oil in the thrust lubrication groove can generate shaft shearing and surface shearing, so that negative pressure is formed at the position of the thrust lubrication groove close to the shaft hole, so that the lubricating oil between the rotating shaft and the first bearing is sucked, and the pressure at the position of the thrust lubrication groove far away from the shaft hole is higher, the lubricating oil in the thrust lubrication groove can better flow into an end surface gap between the first bearing and the pump part along the inclined thrust wall, namely, the lubricating oil enters a small opening from a large opening. Thereby, lubrication between the pump part and the first bearing can be enhanced, so that the lubrication state between the pump part and the first bearing is transited from boundary lubrication to fluid lubrication, and the wear rate between the pump part and the first bearing is effectively reduced.

In one possible design, the at least two thrust walls further comprise a third thrust wall connected to the second end of the first thrust wall and the second end of the second thrust wall, respectively.

In this design, the at least two thrust walls further include a third thrust wall connected to the second end of the first thrust wall and the second end of the second thrust wall, respectively. The thrust lubrication groove is formed by the first thrust wall, the second thrust wall and the third thrust wall, so that the shape design of the thrust lubrication groove can be facilitated.

It should be noted that, the projections of the first thrust wall, the second thrust wall and the third thrust wall on the axial end face of the first bearing may be straight sections or curved sections.

In one possible design, further, the third thrust wall of the thrust lubrication groove is an arc-shaped wall.

In this embodiment, the third thrust wall is an arc-shaped wall, i.e. the projection of the third thrust wall onto the axial end face of the first bearing is an arc segment. Because the third thrust wall corresponds the position of the thrust lubrication groove far away from the shaft hole, the pressure of the lubricating oil in the thrust lubrication groove corresponding to the position is higher, and the third thrust wall is an arc-shaped wall, so that the flow of the lubricating oil in the thrust lubrication groove can be facilitated, the lubricating oil can conveniently enter a small port from a big port, the lubrication between the pump part and the first bearing is enhanced, the lubrication state between the pump part and the first bearing is changed from boundary lubrication to fluid lubrication, and the wear rate between the pump part and the first bearing is effectively reduced.

In one possible design, the pump part further comprises a first gear, the first gear being fitted with the shaft, the plurality of tooth roots of the first gear forming root circles, the root circles extending in the axial direction to form an inner circular surface, the thrust lubrication groove being located in the inner circular surface.

In this design, the pump portion includes a first gear, and first gear and pivot interference fit, pivot rotate in order to drive first gear rotation. The plurality of roots of the first gear form a root circle. The root circle is a circle formed by the root of the tooth slot of the gear. The root circle extends in an axial direction to form an inner circular surface, and the thrust lubrication groove is arranged on the first bearing and is positioned in the inner circular surface. When the first bearing is in contact with the pump portion, the thrust lubrication groove on the first bearing can be completely located below the first gear, namely, the situation that part of the thrust lubrication groove is not covered by the first gear does not exist, and the leakage of lubricating oil is prevented.

In one possible design, the pump portion further includes a second gear, the second gear is disposed outside the first gear, the first gear is capable of driving the second gear to rotate, the second gear and the first gear form a first pressure chamber and a second pressure chamber, and the pressure born by the first pressure chamber is greater than the pressure born by the second pressure chamber.

In this design, the first gear is engaged with the conjugate curve tooth profile of the second gear, and each tooth is contacted with each other, so that the second gear is driven to rotate in the same direction. The first gear divides the inner cavity of the second gear into a plurality of working cavities, the volumes of the working cavities change along with the rotation of the rotor due to the offset of the center of the second gear, a certain vacuum is formed in the area with the increased volume, the oil inlet is arranged at the position, the pressure of the area with the reduced volume is increased, and the oil outlet is correspondingly arranged at the position.

In one possible design, the housing further comprises a pump cover arranged on a side of the pump section facing away from the motor section, the pump cover being connected to the first bearing.

In this design, the housing comprises a pump cover arranged on the side of the pump section facing away from the motor section, the pump cover being connected to the first bearing. The first bearing and the pump cover may be detachably connected, and of course, the first bearing and the pump cover may be fixedly connected. Specifically, the first bearing and the pump cover are of an integrated structure, and the mechanical property of the integrated structure is good, so that the connection strength between the first bearing and the pump cover can be improved. In addition, the first bearing and the pump cover can be integrally manufactured, and the pump cover is produced in batches, so that the processing efficiency of products is improved, and the processing cost of the products is reduced. Meanwhile, the first bearing and the pump cover are arranged into an integrated structure, so that the integrity of the pump device is improved, the number of parts is reduced, the installation procedure is reduced, and the installation efficiency is improved.

In one possible design, the pump device further comprises an oil inlet which is axially formed in the pump cover and/or the first bearing and which communicates with the second pressure chamber. The pump device further comprises an oil outlet which is radially arranged on the pump cover and the first bearing, and the oil outlet is communicated with the first pressure cavity. The tail end of the thrust lubrication groove extends away from the shaft hole, and the tail end of the thrust lubrication groove is positioned between the oil inlet and the oil outlet.

In this design, the pump device further comprises an oil inlet and an oil outlet. The oil inlet is axially formed in the pump cover and/or the first bearing, and two ends of the oil inlet are respectively communicated with the oil pool and a second pressure cavity (low-pressure cavity) of the pump part, so that oil flows out of the oil pool and flows into the second pressure cavity through the oil inlet.

Further, the oil outlet is radially arranged on the pump cover and the first bearing, the oil outlet is communicated with a first pressure cavity (high pressure cavity) of the pump part, and oil in the pump part enters a second pressure cavity through the oil inlet, flows into the first pressure cavity and flows out through the oil outlet.

In one possible design, further, the number of thrust lubrication grooves is plural, the plurality of thrust lubrication grooves being arranged at intervals on the first bearing.

In the design, the number of the thrust lubrication grooves is multiple, and when the number of the thrust lubrication grooves is two, the two thrust lubrication grooves are symmetrically arranged on the first bearing around the axis of the first bearing. When the number of the thrust lubrication grooves is three, the three thrust lubrication grooves are uniformly distributed on the first bearing. By uniformly arranging the plurality of thrust lubrication grooves on the first bearing, lubrication oil can be guided and drained uniformly.

In one possible design, further, a portion of the pump cap extends away from the pump portion to form an extension for forming an oil sump. The pump device further comprises a first lubrication groove which is arranged on the first bearing in a penetrating way along the axial direction, and the first lubrication groove is respectively communicated with the shaft hole, the thrust lubrication groove and the oil pool of the first bearing.

In this design, the shaft hole of first bearing is the through-hole of axial run-through seting up, and the extension is formed by the partly extension structure that deviates from pump part of pump cover, and the extension forms the oil sump, and the oil sump is used for storing lubricating oil, and the through-hole can communicate oil sump and thrust lubrication groove. Specifically, in the high-speed rotation process of the rotating shaft, the rotating shaft can shear lubricating oil in a clearance matched with the first bearing, the lubricating oil enters a clearance between the rotating shaft and the first bearing from an oil pool, the lubricating oil enters a thrust lubrication groove from the clearance under the action of shearing force omega, oil in the clearance between the first bearing and the rotating shaft forms a layer of oil film and plays a lubrication role, and then the oil is pumped into the thrust lubrication groove to lubricate a contact surface between the first gear and the first bearing, then enters the clearance between the first bearing, a pump cover and a pump part, and then enters a low-pressure area oil pool under the action of pressure difference and gravity.

Further, the first lubrication groove penetrates through the first bearing along the axial direction, and the first lubrication groove is communicated with the shaft hole of the first bearing. I.e. a portion of the inner side wall of the first bearing facing away from the spindle recess constitutes a first lubrication groove. Lubricating oil enters a gap between the rotating shaft and the first bearing and a first lubricating groove from an oil pool, oil can be filled and stored in the first lubricating groove, and the oil in the first lubricating groove is coated on the rotating shaft along with the rotation of the rotating shaft, so that the inner wall of the first bearing is lubricated, the reliable lubrication between the rotating shaft and the first bearing is further ensured, and the minimum oil film thickness of fluid lubrication between the first bearing and the rotating shaft is ensured. It is worth noting that the number of the first lubrication grooves is at least one.

In one possible design, the housing further comprises a housing and a second bearing, the housing being connected to the pump cover, the housing enclosing the motor section and the pump section. The second bearing is connected with the shell and sleeved on the rotating shaft, and the second bearing is positioned between the motor part and the pump part.

In the design, the first bearing and the second bearing are sleeved on the rotating shaft, so that the first bearing and the second bearing can play a role in supporting the rotating shaft. The support is a lubrication support, the axes of the first bearing, the second bearing and the rotating shaft are overlapped, and in the working process, the rotating shaft drives the pump part to rotate, so that the pump part can apply a radial force to the rotating shaft, the radial force can push the bearing to deflect towards one side, the first bearing and the second bearing can play a supporting role on the rotating shaft, the play of the rotating shaft is controlled within a reasonable range, the position of the axis of the rotating shaft can not be greatly controlled, and the position of the axis of the rotating shaft can be controlled.

It is worth to say that, compared with the form of the double rolling bearing, the sliding bearing works stably, reliably and noiseless, under the liquid lubrication condition, the sliding surface is separated by the lubricating oil without direct contact, friction loss and surface abrasion can be greatly reduced, the gap between the sliding bearing and the rotating shaft is filled with the lubricating oil, the lubricating oil on the sliding surface can form a layer of oil film, fluid lubrication is realized, the oil film also has certain shock absorption capability, and the service lives of the first bearing, the second bearing and the rotating shaft are prolonged. The two sliding bearings support the rotating shaft, the play of the rotating shaft is small, and the position degree of the axis of the rotating shaft can be controlled within a reasonable range; compared with the form that the double rolling bearing is matched with the sliding bearing, only two sliding bearings are used, so that the supporting structure can be simplified, and the cost can be reduced.

In addition, the second bearing is arranged on one side of the pump part, which is close to the motor part, namely, the first bearing and the second bearing are respectively positioned on two sides of the axial direction of the pump part, and in the working process, the rotating shaft is required to drive the pump part to rotate, so that the load of the rotating shaft is mainly concentrated on the pump part, and the load from the pump part can be shared by the rotating shaft, the first bearing and the second bearing through the matched use of the rotating shaft, the first bearing and the second bearing, so that the damage of the rotating shaft caused by the concentrated load on the rotating shaft in the long-time working process can be avoided to a certain extent.

In one possible design, the pump device further comprises an oil groove and a throttle groove, the oil groove being provided on the first end face of the second bearing facing the pump part, the oil groove being in communication with the first pressure chamber of the pump part. The throttling groove is arranged on the first end face and is communicated with the oil groove and a gap between the second bearing and the rotating shaft.

In this design, the oil groove sets up in the high pressure side of pump portion, and the oil groove can balance the pressure between each appearance chamber in the high pressure side for each appearance chamber pressure in the high pressure side is close, thereby can reduce noise and the mechanical vibration in the operation. The throttling groove is arranged on the first end face, namely the throttling groove is arranged on the first end face of the first bearing facing the pump part, and the throttling groove is used for communicating the first oil groove, the second bearing and the gap between the rotating shaft. That is, the oil in the first pressure cavity flows to the oil groove firstly, and then flows to the gap between the second bearing and the rotating shaft through the throttling groove, so that excessive oil can be effectively prevented from flowing into the gap between the second bearing and the rotating shaft at the same time, and the displacement of the pump is further influenced. In order to ensure the fluid lubrication performance between the second bearing and the rotating shaft, namely to provide sufficient lubricating oil for a gap between the second bearing and the rotating shaft, and simultaneously ensure that the displacement of the pump part is not seriously leaked, namely that the displacement is not obviously influenced by the lubricating oil, through the cooperation of the oil groove and the throttling groove, the lubricating requirement between the second bearing and the rotating shaft can be realized, and the excessive flow of the lubricating oil is not caused, so that the displacement of the pump device is reduced.

In one possible design, the pump device further comprises a second lubrication groove, which is arranged axially through the second bearing, which communicates with the shaft bore and the throttle groove of the second bearing, respectively.

In this design, a second lubrication groove is provided through the second bearing in the axial direction, the second lubrication groove communicating with the shaft hole of the second bearing. That is, the second lubrication groove is formed by a portion of the inner side wall of the second bearing being recessed away from the rotating shaft, the second lubrication groove being in communication with the throttle groove. Because there is pressure difference, the fluid in the first pressure chamber flows into the gap between the second bearing and the rotating shaft through the oil groove and the throttling groove in sequence, and meanwhile, the second lubrication groove can be filled, and along with the rotation of the rotating shaft, the fluid in the second lubrication groove can be coated on the surface of the rotating shaft, and the second lubrication groove plays a role of temporarily storing lubricating oil, so that a fluid lubrication film is formed between the inner wall of the second bearing and the rotating shaft, and the reliable lubrication between the rotating shaft and the second bearing is further ensured.

In one possible design, the pump device further comprises a sealing member connected to a side of the second bearing facing away from the pump portion, the sealing member being arranged around the shaft, the sealing member, the second bearing and the shaft forming a liquid passing chamber, the liquid passing chamber being in communication with the second lubrication groove.

In the design, the second bearing is connected to the casing, and the second bearing can divide a cavity enclosed by the casing into a motor cavity and a pump cavity, so that the space arrangement is more reasonable. The motor part is located in the motor cavity, and the pump part is located in the pump cavity. The pump device also comprises a sealing element which is connected to the second bearing and is positioned in the motor cavity, and the sealing element is sleeved on the rotating shaft. Further, through setting up the sealing member to can separate the cavity into relative sealed motor chamber and pump chamber, make working medium (lubricating oil) can not flow into the motor intracavity, can not influence the normal use of parts such as stator, rotor, control portion in the motor chamber, the motor intracavity need not additionally set up other structures in order to guarantee that the spare part in the motor chamber receives the corruption, make the sealing performance of pump device better, the while structure is simpler, be favorable to reduce cost.

Further, the sealing member, the second bearing and the rotating shaft form a liquid passing cavity, and the liquid passing cavity is communicated with the second lubrication groove. The liquid passing cavity formed by the sealing element, the second bearing and the rotating shaft can store a part of lubricating oil, the part of lubricating oil can also flow into the second lubricating groove, and the liquid passing cavity can play a certain buffering role by controlling the connection strength of the sealing element and the first bearing, namely the pressure born by the sealing element, so that the oil in the liquid passing cavity, the second lubricating groove and the throttling groove can be in a pressure relative balance state, and the fluid lubricating performance of the rotating shaft and the second bearing is guaranteed.

In one possible design, the pump device further comprises a pressure relief groove provided on the second bearing, the pressure relief groove communicating the fluid passage chamber with the second pressure chamber of the pump section.

In this design, the pressure relief groove is provided on the second bearing, and the pressure relief groove is for connecting through the liquid chamber and the second pressure chamber. The pressure relief groove can be in the form of a through hole, so that two ends of the through hole can be respectively communicated with the second pressure cavity and the liquid passing cavity, and the pressure in the liquid passing cavity can be better released due to smaller pressure born by the second pressure cavity, and the pressure of oil liquid is buffered by the liquid passing cavity.

Further, through set up oil groove, throttling groove, second lubrication groove, cross liquid chamber and pressure release groove on the second bearing to form the lubrication circuit of complete second bearing, high pressure oil liquid is from the oil groove, through throttling groove, second lubrication groove and cross the liquid chamber, get back to the second pressure intracavity that pressure is lower through the pressure release groove, thereby can ensure to cross liquid intracavity pressure and can not be too high, avoid the pressure to be higher than the pressure limit value that the sealing member can bear, ensure the reliability of sealing member's position, effectually avoid under the high pressure sealing member to break away from the second bearing, lead to lubricating oil leakage, can't ensure the sealing performance between motor chamber and the pump chamber.

In one possible design, the pump device further comprises a buffer chamber, which is arranged on the end face of the second bearing facing away from the pump part.

In this design, the buffer chamber is located on the terminal surface that the second bearing deviates from the pump portion, specifically, the buffer chamber can be the toper, and the buffer chamber can be the toper chamber to the rigidity of second bearing can be reduced to the buffer chamber, provides flexible support for the pivot, reduces the face pressure on the axial terminal surface that the second bearing deviates from the pump portion, effectively improves the wearing and tearing condition of second bearing and pivot.

Further, the opening area of the buffer cavity is larger than the bottom wall area of the buffer cavity, so that the buffer cavity can be arranged as a conical cavity, and the flexible support can be provided for the rotating shaft, so that the buffer cavity is convenient to maintain and demould.

In one possible design, the motor part further comprises a rotor and a stator, the rotor being connected to the shaft. The stator is sleeved outside the rotor, and comprises a stator core and a stator winding, wherein the stator winding is arranged on the stator core. The pump device further comprises a control part arranged on one side of the motor part, which is away from the pump part, the control part is connected to the shell and positioned in the cavity, and the end part of the stator winding is electrically connected with the control part.

In this design, the motor section also includes a rotor and a stator. The rotor and the rotating shaft are connected, the rotor and the rotating shaft can be coaxially arranged, the rotor and the rotating shaft are in interference fit, the rotor and the rotating shaft are not coaxially arranged, but are in transmission connection, and the rotor and the rotating shaft are flexibly arranged according to practical conditions. The stator is sleeved outside the rotor, and comprises a stator core and a stator winding, wherein the stator winding is arranged on the stator core. In addition, the pump device still includes the control portion, and the control portion sets up in the one side that the motor portion deviates from the pump portion, and the control portion sets up the position of keeping away from the pump portion at the motor portion promptly, because the position vibration that is close to the pump portion in the course of the work is comparatively obvious, and the load that receives is great, so the control portion keeps away from the pump portion, can play the effect of protection to the control portion to a certain extent, improves the life of control portion. Further, the control part is connected to the housing and located in the cavity, and the end parts of the stator winding are electrically connected to the control part, and the stator winding is typically copper wire.

Specifically, in the working process of the pump device, the control part controls the current of the stator winding in the stator to change according to a certain rule, so that the stator is controlled to generate a changed excitation magnetic field, and the rotor rotates under the action of the excitation magnetic field, so that the rotating shaft drives the first gear in the pump part to rotate, and further the second gear moves. When the first gear and the second gear in the pump part rotate, the volume of the compression chamber formed between the first gear and the second gear changes due to the eccentric movement of the second gear, so that the working medium entering the compression chamber is pressed out to the oil outlet to generate flowing power.

According to a second aspect of the present invention there is provided a vehicle comprising a pump arrangement provided by any of the designs described above.

The vehicle provided by the invention comprises the pump device provided by any design, so that the vehicle has all the beneficial effects of the pump device, and the description is omitted herein.

In one possible design, the vehicle further comprises a body and an engine, the pump device being arranged in the body. The engine is disposed in the vehicle body, and the engine includes a mount that is connected to an extension of the pump device.

In this design, the vehicle includes a body and an engine. The pump device and the engine are arranged in the vehicle body, the engine comprises a mounting seat, the mounting seat is connected with the extending part of the pump device, so that an oil pool is formed through the cooperation of the mounting seat and the extending part, and the oil pool is communicated with an oil source of the engine to realize oil way communication.

It is worth to say that the vehicle can be a traditional fuel vehicle or a new energy vehicle. The new energy automobile comprises a pure electric automobile, a range-extended electric automobile, a hybrid electric automobile, a fuel cell electric automobile, a hydrogen engine automobile and the like.

Additional aspects and advantages of the invention will be set forth in part in the description which follows, or may be learned by practice of the invention.

Drawings

The foregoing and/or additional aspects and advantages of the invention will become apparent and may be better understood from the following description of embodiments taken in conjunction with the accompanying drawings in which:

FIG. 1 shows a schematic structural view of a pump device according to an embodiment of the present invention;

FIG. 2 shows a schematic structural view of a pump cover and a first bearing in a pump device according to an embodiment of the present invention;

FIG. 3 shows a cross-sectional view along A-A of the pump device of FIG. 2 according to the present invention;

FIG. 4 shows a partial enlarged view of one of the pump devices shown in FIG. 2 at B in accordance with the present invention;

FIG. 5 shows a partial enlarged view of one of the pump devices shown in FIG. 1 at C in accordance with the present invention;

FIG. 6 shows a schematic structural view of a casing and a first bearing in a pump apparatus according to an embodiment of the present invention;

fig. 7 shows a schematic structural view of a vehicle in an embodiment according to the present invention.

The correspondence between the reference numerals and the component names in fig. 1 to 7 is:

A 100-pump device is provided with a pump,

110 Housing, 111 pump cap, 112 extension, 113 oil sump, 114 housing, 115 cavity,

120 Motor part, 121 rotating shaft, 122 rotor, 123 stator,

130 Pump section, 131 first gear, 132 root circle, 133 second gear, 134 first pressure chamber, 135 second pressure chamber,

140 First bearings, 141 first lubrication grooves,

150 The thrust lubrication groove,

151, 152A first 152a second 152b,

153, 153A first datum plane,

154, 154A second datum,

155 A third thrust wall of the housing,

161 Oil inlets, 162 oil outlets,

170 Second bearing, 171 oil groove, 172 throttling groove, 173 second lubrication groove, 174 relief groove, 175 buffer cavity,

181, 182 Passing through the liquid cavity,

A control section 190 of the control section,

A vehicle of 200 a type,

210 A vehicle body,

220 Engine, 221 mount.

Detailed Description

In order that the above-recited objects, features and advantages of the present application will be more clearly understood, a more particular description of the application will be rendered by reference to the appended drawings and appended detailed description. It should be noted that, without conflict, the embodiments of the present application and features in the embodiments may be combined with each other.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, but the present invention may be practiced in other ways than those described herein, and therefore the scope of the present invention is not limited to the specific embodiments disclosed below.

Pump apparatus 100 and vehicle 200 provided according to some embodiments of the present invention are described below with reference to fig. 1 to 7.

The XYZ coordinate system is appropriately shown in the drawings as a three-dimensional rectangular coordinate system. In the XYZ coordinate system, the Z-axis direction is a direction parallel to the axial direction of the central axis R of the motor unit 120 shown in fig. 1, that is, the up-down direction of the pump device 100 in fig. 1. The X-axis direction is a direction parallel to the short-side direction of the pump device 100 shown in fig. 1, that is, the left-right direction of the pump device 100 in fig. 1. The Y-axis direction is a direction perpendicular to both the X-axis direction and the Z-axis direction.

In the following description, a direction (Z-axis direction) parallel to the central axis R of the motor unit 120 is abbreviated as an "axial direction", a radial direction centered on the central axis R is abbreviated as a "radial direction", and a circumferential direction centered on the central axis R, that is, a direction around the central axis R is abbreviated as a "circumferential direction".

In addition, in the present specification, "extending in the axial direction" includes, in addition to the case of extending strictly in the axial direction (Z-axis direction), the case of extending in a direction inclined within a range of less than 45 ° with respect to the axial direction. In addition, in the present specification, "extending in the radial direction" includes, in addition to extending strictly in the radial direction, that is, in a direction perpendicular to the axial direction (Z-axis direction), extending in a direction inclined within a range of less than 45 ° with respect to the radial direction.

Example 1

According to a first aspect of the present invention, there is provided a pump device 100, as shown in fig. 1 and 2, which includes a housing 110, a motor part 120, a pump part 130, a first bearing 140, and a thrust lubrication groove 150. Wherein the housing 110 has a cavity 115. The motor part 120 is disposed in the cavity 115, and the motor part 120 includes a rotation shaft 121 rotating around a central axis of the motor part 120. The pump part 130 is disposed at one side of the motor part 120 in the axial direction and contacts the rotation shaft 121, and the pump part 130 can be rotated by the rotation shaft 121. The first bearing 140 is connected to the housing 110 and sleeved on the rotating shaft 121, and the first bearing 140 is located on a side of the pump portion 130 away from the motor portion 120. The thrust lubrication groove 150 is provided on an end surface of the first bearing 140 near the pump portion 130 and communicates with the shaft hole of the first bearing 140.

The pump device 100 provided by the present invention includes a housing 110, a motor portion 120, a pump portion 130, a first bearing 140, and a thrust lubrication groove 150. Specifically, the pump device 100 is an oil pump. Specifically, the oil pump is an electronic oil pump. The housing 110 has a cavity 115, and the motor portion 120 and the pump portion 130 are both accommodated in the housing 110, so that the housing 110 ensures that the motor portion 120 and the pump portion 130 are not affected by external environment, and can operate normally.

Further, the motor part 120 includes a rotation shaft 121 around a central axis of the motor part 120. The pump part 130 is provided at one side of the motor part 120 in the axial direction, and the pump part 130 is in contact with the rotation shaft 121 of the motor part 120. Specifically, the pump portion 130 is in interference fit with the rotating shaft 121, so that the rotating shaft 121 drives the pump portion 130 to rotate, that is, the rotating shaft 121 drives the pump portion 130 to synchronously move.

Further, the first bearing 140 is disposed on a side of the pump portion 130 away from the motor portion 120, the first bearing 140 is sleeved on the rotating shaft 121, the first bearing 140 is a sliding bearing, and the first bearing 140 can provide a supporting effect for the rotating shaft 121. It should be noted that, the first bearing 140 can provide lubrication support for the rotating shaft 121, because the axes of the first bearing 140 and the rotating shaft 121 are coincident, in the actual working process, the rotating shaft 121 drives the pump portion 130 to rotate, so that the pump portion 130 applies a force on the rotating shaft 121 in a radial direction, the rotating shaft 121 receives the radial force and pushes the first bearing 140 to deflect towards one side, at this time, the rotating shaft 121 contacts with the first bearing 140, and the first bearing 140 provides a supporting effect for the rotating shaft 121, so that the play of the rotating shaft 121 can be controlled within a reasonable range, thereby facilitating the control of the axis of the rotating shaft 121.

By plain bearing is meant a bearing that operates under sliding friction. Compared with the form of the double rolling bearing, the sliding bearing works stably, reliably and noiseless, the sliding surface is separated by the lubricating oil without direct contact under the liquid lubrication condition, friction loss and surface abrasion can be greatly reduced, the gap between the sliding bearing and the rotating shaft 121 is filled with the lubricating oil, the lubricating oil on the sliding surface can form a layer of oil film, fluid lubrication is realized, the oil film also has certain shock absorption capability, and the service lives of the first bearing 140 and the rotating shaft 121 are prolonged.

Further, a thrust lubrication groove 150 is provided on an end surface of the first bearing 140 near the pump portion 130, the thrust lubrication groove 150 communicating with the first bearing 140 and the shaft hole of the first bearing 140. The first bearing 140 and the rotating shaft 121 have lubricating oil in a fit clearance, the rotating shaft 121 shears the lubricating oil in the fit clearance between itself and the first bearing 140 in the high-speed rotation process, and the lubricating oil enters the thrust lubrication groove 150 from the fit clearance under the action of the shearing force omega, so that the lubricating oil entering the thrust lubrication groove 150 has certain speed and pressure. The end surface gap between the first bearing 140 and the pump portion 130 is small, and the lubricating oil in the thrust lubricating groove 150 can flow to the end surface gap between the first bearing 140 and the pump portion 130. Meanwhile, since there is relative movement between the pump part 130 and the first bearing 140, a fluid lubrication condition is constituted between the contact end surfaces of the pump part 130 and the first bearing 140, that is, an oil film is formed at the contact end surfaces of the first bearing 140 and the pump part 130, so that the boundary lubrication between the first bearing 140 and the pump part 130 is transited to the fluid lubrication, thereby greatly improving the wear condition of the contact end surfaces of the pump part 130 and the first bearing 140, reducing the power consumption, and further reducing the operation noise of the pump device 100.

It should be noted that the first bearing 140 may be detachably connected to the housing 110, and of course, the first bearing 140 may be fixedly connected to the housing 110. Specifically, the first bearing 140 and the housing 110 are in an integrated structure, and the mechanical properties of the integrated structure are better, so that the connection strength between the first bearing 140 and the housing 110 can be improved. In addition, the first bearing 140 and the housing 110 may be integrally manufactured for mass production to improve the processing efficiency of the product and reduce the processing cost of the product. Meanwhile, by providing the first bearing 140 and the housing 110 as an integrated structure, the integrity of the pump device 100 is also improved, the number of parts is reduced, the mounting process is reduced, and the mounting efficiency is improved.

Further, as shown in fig. 3, the notch area of the thrust lubrication groove 150 in the axial direction is larger than the groove bottom area of the thrust lubrication groove 150.

In this embodiment, the thrust lubrication groove 150 includes two notches, the orientations of which are different, one toward the pump portion 130 and the other toward the rotation shaft 121. The area of the slot defined toward the pump portion 130 in this design is greater than the area of the slot bottom. That is, the thrust lubrication groove 150 is necked in an axial direction away from the pump portion 130, i.e., in a top-down direction. That is, the groove wall of the thrust lubrication groove 150 is inclined, at this time, since the lubricant entering the thrust lubrication groove 150 has a certain speed and pressure, and since the gap between the end surfaces of the first bearing 140 and the pump portion 130 is small, the groove wall of the thrust lubrication groove 150 is inclined, so that a converging wedge-shaped angle is formed between the thrust lubrication groove 150 and the end surface gap, the lubricant in the thrust lubrication groove 150 flows along the inclined groove wall into the end surface gap between the pump portion 130 and the first bearing 140, that is, the lubricant enters the "small port" from the "large port", which is the gap between the first bearing 140 and the pump portion 130, and it is worth noting that the "large port" refers to the thrust lubrication groove 150. It is thus possible to enhance lubrication between the pump portion 130 and the first bearing 140 so that the lubrication state therebetween is transited from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate therebetween.

In addition, during the high-speed rotation of the rotation shaft 121 and the pump part 130, the oil film between the contact surfaces of the pump part 130 and the first bearing 140 generates a force F pushing the pump part 130 upward, so that the lubricating oil in the end surfaces of the first bearing 140 and the pump part 130 plays a role of floating seal, thereby further reducing the end surface leakage. It has been shown in the relevant literature that the end face leakage of the pump device 100 accounts for 75% to 80% of the total leakage of the pump device 100, and therefore it is important to improve the leakage between the respective contact end faces in the pump device 100. It is worth noting that the lubricating oil has a certain viscosity.

Further, as shown in fig. 3 and 4, the thrust lubrication groove 150 includes a thrust wall 151, the thrust wall 151 includes at least one thrust segment 152, and the at least one thrust segment 152 includes a first thrust segment 152a, the first thrust segment 152a extending near a center of the thrust lubrication groove 150 in an axial direction away from the pump portion 130.

In this embodiment, thrust lubrication groove 150 includes thrust wall 151, thrust wall 151 being an inclined wall. The thrust wall 151 extends near the center of the thrust lubrication groove 150 in an axial direction away from the pump portion 130, i.e., in a top-down direction. The thrust wall 151 comprises at least one thrust segment 152, the at least one thrust segment 152 comprising a first thrust segment 152a, the first thrust segment 152a extending in an axial direction away from the pump portion 130, close to the centre of the thrust lubrication groove 150. At this time, the thrust lubrication groove 150, the pump portion 130 and the end face of the first bearing 140 form a converging wedge-shaped included angle therebetween, so that the lubrication oil in the thrust lubrication groove 150 flows along the inclined first thrust segment 152a into the end face gap between the pump portion 130 and the first bearing 140, i.e. the lubrication oil enters the "small port" from the "large port". It should be noted that "large opening" refers to the thrust lubrication groove 150, and "small opening" refers to the gap between the first bearing 140 and the pump portion 130. It is thus possible to enhance lubrication between the pump portion 130 and the first bearing 140 so that the lubrication state therebetween is transited from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate therebetween.

It should be noted that the first thrust segment 152a may be formed of at least one straight segment and at least one curved segment, the first thrust segment 152a has a first end close to the pump portion 130 and a second end far from the pump portion 130, and the second end of the first thrust segment 152a extends near the center of the thrust lubrication groove 150, that is, the inclined extending trend of the first thrust segment 152a satisfies the above relationship, so that the flow of the lubrication oil is facilitated. The first thrust segment 152a may be formed of a plurality of curved surfaces or may be formed of a plurality of circular arcs.

Further, as shown in fig. 3 and 4, the angle α between the first thrust segment 152a and the axial end face of the first bearing 140 is greater than 0 ° and less than 90 °.

In this embodiment, the axial end surface of the first bearing 140 refers to the axial end surface of the first bearing 140 near the pump portion 130, and the included angle between the first thrust segment 152a and the axial end surface is satisfied, and 0 ° < α < 90 °, so that the first thrust segment 152a can better drain the lubricating oil into the end surface gap between the first bearing 140 and the pump portion 130, ensure that the lubricating oil can pass through the speed and pressure of the lubricating oil itself, and enter the end surface gap through the guiding of the first thrust segment 152a, so that the thrust lubrication groove 150 and the end surface gap form a convergent wedge-shaped included angle, and then the lubricating oil in the thrust lubrication groove 150 flows into the end surface gap between the pump portion 130 and the first bearing 140 along the inclined groove wall, that is, the lubricating oil enters the "small opening" from the "large opening". It is thus possible to enhance lubrication between the pump portion 130 and the first bearing 140 so that the lubrication state therebetween is transited from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate therebetween. Further, the angle α between the first thrust segment 152a and the axial end face of the first bearing 140 is 45 °. It should be noted that, the inclined first thrust section 152a may be machined on the end surface of the first bearing 140 near the pump portion 130 by forming a cutter. Specifically, the thrust lubrication groove 150 may have an inverted triangle shape, a semicircular shape, or the like in longitudinal section (in the axial direction).

Further, as shown in fig. 3 and 4, at least one thrust segment 152 further includes a second thrust segment 152b, the second thrust segment 152b extending axially and being connected between the first thrust segment 152a and the groove bottom of the thrust lubrication groove 150.

In this embodiment, the at least one thrust segment 152 further includes a second thrust segment 152b, the second thrust segment 152b extends axially to connect the first thrust segment 152a and the groove bottom, and the second thrust segment 152b cooperates with the first thrust segment 152a to form the thrust wall 151, so as to ensure that the volume of the thrust lubrication groove 150 meets the lubrication requirement. It should be noted that, during the machining process, a straight groove is machined on the end surface of the first bearing 140 facing the pump portion 130, and then a chamfer is machined, so that the first thrust segment 152a and the second thrust segment 152b can be formed, and the machining difficulty of the thrust lubrication groove 150 can be reduced through the above machining sequence.

Further, the number of the thrust walls 151 is at least two.

In this embodiment, the number of thrust walls 151 is at least two, each thrust wall 151 of the at least two thrust walls 151 includes at least one thrust segment 152. The at least one thrust segment 152 includes a first thrust segment 152a. The at least one thrust segment 152 further includes a second thrust segment 152b. It should be noted that, the structures of the at least two thrust walls 151 may be equal or unequal, and when the number of the thrust walls 151 is three, the structures of the three thrust walls 151 may be partially equal or partially unequal.

Further, as shown in fig. 3 and fig. 4, the at least two thrust walls 151 include a first thrust wall 153, a first end of the first thrust wall 153 is connected to an inner side wall of the first bearing 140, a section where a connection point between the first thrust wall 153 and the inner side wall of the first bearing 140 is located is a first reference plane 153a, and an included angle β1 between the first thrust wall 153 and the first reference plane 153a is greater than or equal to 0 ° and smaller than 90 °.

In this embodiment, the first end of the first thrust wall 153 is the starting end of the first thrust wall 153, the second end of the first thrust wall 153 is the terminating end of the first thrust wall 153, the first end is connected to the inner side wall of the first bearing 140, and the inner side wall of the first bearing 140 is the side wall of the shaft hole of the first bearing 140. The tangential plane where the connection point between the first end and the first bearing 140 is located is a first reference plane 153a, and an included angle β1 between the first thrust wall 153 and the first reference plane 153a is greater than or equal to 0 ° and smaller than 90 °. In the high-speed rotation process of the rotating shaft 121, the rotating shaft 121 shears the lubricating oil in the fit clearance between itself and the first bearing 140, and the lubricating oil enters the thrust lubrication groove 150 from the fit clearance under the action of the shearing force ω, and at this time, the lubricating oil entering the thrust lubrication groove 150 has a certain speed and pressure. Since the first thrust wall 153 is biased to the direction in which the rotation shaft 121 rotates, the lubrication oil in the thrust lubrication groove 150 may undergo shaft shearing and surface shearing, so that negative pressure is formed at a position of the thrust lubrication groove 150 close to the shaft hole, so as to suck the lubrication oil between the rotation shaft 121 and the first bearing 140, and the pressure at a position of the thrust lubrication groove 150 away from the shaft hole is higher, so that the lubrication oil in the thrust lubrication groove 150 may flow into the end surface gap between the first bearing 140 and the pump portion 130 along the inclined thrust wall 151, i.e., the lubrication oil may enter the "small port" from the "large port". It is thus possible to enhance lubrication between the pump portion 130 and the first bearing 140 so that the lubrication state therebetween is transited from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate therebetween.

Further, as shown in fig. 3 and fig. 4, the at least two thrust walls 151 further include a second thrust wall 154, the second thrust wall 154 is disposed opposite to the first thrust wall 153, a first end of the second thrust wall 154 is connected to an inner side wall of the first bearing 140, a section where a connection point between the second thrust wall 154 and the inner side wall of the first bearing 140 is located is a second reference plane 154a, and an included angle β2 between the second thrust wall 154 and the second reference plane 154a is greater than 0 ° and smaller than 90 °.

In this embodiment, the at least two thrust walls 151 further include a second thrust wall 154, a first end of the second thrust wall 154 is a starting end of the second thrust wall 154, a second end of the second thrust wall 154 is a terminating end of the second thrust wall 154, the second end is connected to an inner side wall of the first bearing 140, and the inner side wall of the first bearing 140 is a side wall of the shaft hole of the first bearing 140. The tangential plane where the connection point between the first end and the first bearing 140 is located is a second reference plane 154a, and an included angle β2 between the second thrust wall 154 and the second reference plane 154a is greater than or equal to 0 ° and smaller than 90 °. In the high-speed rotation process of the rotating shaft 121, the rotating shaft 121 shears the lubricating oil in the fit clearance between itself and the first bearing 140, and the lubricating oil enters the thrust lubrication groove 150 from the fit clearance under the action of the shearing force ω, and at this time, the lubricating oil entering the thrust lubrication groove 150 has a certain speed and pressure. Since the second thrust wall 154 is biased to the direction in which the rotation shaft 121 rotates, the lubrication oil in the thrust lubrication groove 150 may undergo shaft shearing and surface shearing, so that negative pressure is formed at a position of the thrust lubrication groove 150 close to the shaft hole, so as to suck the lubrication oil between the rotation shaft 121 and the first bearing 140, and the pressure is higher at a position of the thrust lubrication groove 150 away from the shaft hole, so that the lubrication oil in the thrust lubrication groove 150 may flow into the end surface gap between the first bearing 140 and the pump portion 130 along the inclined thrust wall 151, i.e., the lubrication oil may enter the "small port" from the "large port". It is thus possible to enhance lubrication between the pump portion 130 and the first bearing 140 so that the lubrication state therebetween is transited from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate therebetween.

It should be noted that the included angle β1 and the included angle β2 may be equal or different, as long as the first thrust wall 153 and the second thrust wall 154 deviate in the rotation direction of the rotation shaft 121. Specifically, when the shaft 121 rotates counterclockwise, the first thrust wall 153 and/or the counterclockwise deflect.

Further, a second end of the second thrust wall 154 is connected to a second end of the first thrust wall 153.

In this embodiment, the second end of the second thrust wall 154 is connected to the second end of the first thrust wall 153, that is, the connection point between the second thrust wall 154 and the first thrust wall 153, the connection point between the first end of the first thrust wall 153 and the first bearing 140, and the connection point between the first end of the second thrust wall 154 and the first bearing 140 form a triangular thrust groove. That is, the first thrust wall 153 and/or the second thrust wall 154 are biased in the direction in which the rotation shaft 121 rotates, so that the lubrication oil in the thrust lubrication groove 150 is subjected to shaft shearing and surface shearing, thereby better flowing the lubrication oil in the thrust lubrication groove 150 along the inclined thrust wall 151 into the end surface gap between the first bearing 140 and the pump portion 130.

Further, as shown in fig. 3 and4, the at least two thrust walls 151 further include a third thrust wall 155, and the third thrust wall 155 is connected to the second end of the first thrust wall 153 and the second end of the second thrust wall 154, respectively.

In this embodiment, the at least two thrust walls 151 further include a third thrust wall 155, the third thrust wall 155 being connected to the second end of the first thrust wall 153 and the second end of the second thrust wall 154, respectively. That is, the thrust lubrication groove 150 is formed of the first thrust wall 153, the second thrust wall 154, and the third thrust wall 155 together, so that the shape design of the thrust lubrication groove 150 can be facilitated.

It should be noted that, the projections of the first thrust wall 153, the second thrust wall 154 and the third thrust wall 155 on the axial end face of the first bearing 140 may be straight sections or curved sections.

Further, the third thrust wall 155 of the thrust lubrication groove 150 is an arc-shaped wall.

In this embodiment, the third thrust wall 155 is an arc-shaped wall, i.e., the projection of the third thrust wall 155 on the axial end face of the first bearing 140 is an arc segment. Since the third thrust wall 155 is located at a position away from the shaft hole of the lubrication groove 150, the pressure of the lubrication oil in the third thrust wall 155 is higher, so that the flow of the lubrication oil in the thrust lubrication groove 150 can be facilitated by making the third thrust wall 155 an arc-shaped wall, that is, the lubrication oil can be facilitated to enter the small port from the large port, the lubrication between the pump portion 130 and the first bearing 140 is enhanced, the lubrication state between the pump portion 130 and the first bearing 140 is changed from boundary lubrication to fluid lubrication, and the wear rate between the pump portion and the first bearing is effectively reduced.

Example two

On the basis of the first embodiment, as shown in fig. 2, the specific structure of the pump portion 130 is explained, further, the pump portion 130 includes a first gear 131, the first gear 131 is matched with the rotating shaft 121, a plurality of tooth roots of the first gear 131 form root circles 132, the root circles 132 extend in the axial direction to form an inner circular surface, and the thrust lubrication groove 150 is located in the inner circular surface.

In this embodiment, the pump portion 130 includes a first gear 131, the first gear 131 is in interference fit with the rotating shaft 121, and the rotating shaft 121 rotates to drive the first gear 131 to rotate. The plurality of roots of the first gear 131 form a root circle 132. Note that the root circle 132 refers to a circle formed by the root of the tooth slot of the gear. The root circles 132 extend in the axial direction to form an inner circular surface, and thrust lubrication grooves 150 are provided on the first bearing 140 and are located in the inner circular surface. When the first bearing 140 is in contact with the pump part 130, the thrust lubrication groove 150 on the first bearing 140 can be completely located under the first gear 131, that is, there is no case where a part of the thrust lubrication groove 150 is not covered by the first gear 131, preventing leakage of the lubrication oil.

Further, the pump portion 130 further includes a second gear 133, the second gear 133 is disposed outside the first gear 131, the first gear 131 can drive the second gear 133 to rotate, the second gear 133 and the first gear 131 form a first pressure chamber 134 and a second pressure chamber 135, and the pressure born by the first pressure chamber 134 is greater than the pressure born by the second pressure chamber 135.

In this embodiment, the pump portion 130 is a gear pump. Specifically, in the gear pump, the front pair of teeth is not yet disengaged and the rear pair of teeth is already engaged, each inner tooth surface is in contact with the outer tooth surface to form a closed cavity, the volume of the closed cavity 115 changes along with the rotation of the first gear 131, and if the unloading channel cannot be communicated, a trapped oil volume is formed. Since the compressibility of the liquid is small, when the trapped oil volume is reduced from large, the liquid present in the trapped oil volume is squeezed, and the pressure is sharply increased, greatly exceeding the operating pressure of the gear pump. Meanwhile, the liquid in the trapped oil volume is forced to be extruded from all the leakable gaps, so that the rotating shaft 121 and the first bearing 140 can bear large impact load, power loss is increased, oil is heated, noise and vibration are caused, and the working stability and service life of the gear pump are reduced. When the volume of the trapped oil is changed from small to large, vacuum is formed, so that air dissolved in the liquid is separated to generate bubbles, and the damages such as cavitation, noise, vibration, flow and pressure pulsation are brought. The method for eliminating the oil trapping phenomenon adopts the method that unloading grooves are formed in two end covers of a gear, so that the unloading grooves are communicated with an oil pressing cavity when the closed volume is reduced, and the unloading grooves are communicated with an oil suction cavity when the closed volume is increased.

Specifically, the first gear 131 is meshed with the conjugate curve tooth profile of the second gear 133, and each tooth is contacted with each other, so that the second gear 133 is driven to rotate in the same direction. The first gear 131 divides the inner cavity of the second gear 133 into a plurality of working chambers, the volumes of the working chambers change with the rotation of the rotor 122 due to the center offset of the second gear 133, the area with increased volume forms a certain vacuum, the oil inlet 161 is arranged at the position, the pressure of the area with reduced volume is increased, and the oil outlet 162 is correspondingly arranged at the position.

Example III

On the basis of the foregoing embodiment, the specific structure of the housing 110 is described in this embodiment, and further, the housing 110 includes the pump cover 111, the pump cover 111 is disposed on the side of the pump portion 130 facing away from the motor portion 120, and the pump cover 111 is connected to the first bearing 140.

In this embodiment, the housing 110 includes a pump cover 111, the pump cover 111 being disposed on a side of the pump portion 130 facing away from the motor portion 120, the pump cover 111 being coupled to the first bearing 140. The first bearing 140 may be detachably connected to the pump cover 111, and of course, the first bearing 140 and the pump cover 111 may be fixedly connected. Specifically, the first bearing 140 and the pump cover 111 are of an integrated structure, and the mechanical properties of the integrated structure are better, so that the connection strength between the first bearing 140 and the pump cover 111 can be improved. In addition, the first bearing 140 and the pump cover 111 can be integrally manufactured for mass production, so that the processing efficiency of the product is improved, and the processing cost of the product is reduced. Meanwhile, by providing the first bearing 140 and the pump cover 111 as an integrated structure, the integrity of the pump device 100 is also improved, the number of parts is reduced, the mounting process is reduced, and the mounting efficiency is improved.

Further, as shown in fig. 1 and 2, the pump device 100 further includes an oil inlet 161, where the oil inlet 161 is axially formed on the pump cover 111 and/or the first bearing 140, and the oil inlet 161 is in communication with the second pressure chamber 135. The pump device 100 further comprises an oil outlet 162, the oil outlet 162 being radially open on the pump cover 111 and the first bearing 140, the oil outlet 162 being in communication with the first pressure chamber 134. Wherein the end of the thrust lubrication groove 150 extends away from the shaft bore, and the end of the thrust lubrication groove 150 is located between the oil inlet 161 and the oil outlet 162.

In this embodiment, regarding the design principle of the oil inlet 161 and the oil outlet 162, in the process of ensuring the rotation of the first gear 131 and the second gear 133, the teeth between the oil inlet 161 and the first gear 131 and the teeth between the second gear 133 are communicated as soon as possible, and before the first gear 131 and the second gear 133 form the maximum volume, the volume cavity of the gear is always communicated with the oil inlet 161, and the oil filling time is prolonged as much as possible, so that the volume cavity between the first gear and the second gear is filled with oil, thereby ensuring the oil absorption. The oil outlet 162 is also connected with the interdental high pressure oil as early as possible to reduce the interdental overcompression work, and is closed as late as possible to fully utilize the inertia of the fluid to drain the interdental oil, thereby improving the volumetric efficiency of the internal gear type oil pump. It should be noted, however, that the first gear 131 and the second gear 133, when forming the maximum volume, cannot communicate with the oil inlet 161, avoiding affecting the volumetric efficiency of the pump device 100 at low speeds.

Further, the pump device 100 further comprises an oil inlet 161 and an oil outlet 162. The oil inlet 161 is axially formed on the pump cover 111 and/or the first bearing 140, and two ends of the oil inlet 161 are respectively communicated with the oil pool 113 and the second pressure cavity 135 (low pressure cavity) of the pump portion 130, so that oil flows out of the oil pool 113 and flows into the second pressure cavity 135 through the oil inlet 161.

Further, the oil outlet 162 is radially formed on the pump cover 111 and the first bearing 140, and the oil outlet 162 is communicated with the first pressure chamber 134 (high pressure chamber) of the pump portion 130, and the oil in the pump portion 130 enters the second pressure chamber 135 through the oil inlet 161, flows into the first pressure chamber 134, and flows out of the oil outlet 162.

Further, the number of the thrust lubrication grooves 150 is plural, and the plurality of thrust lubrication grooves 150 are arranged on the first bearing 140 at intervals.

In this embodiment, the number of the thrust lubrication grooves 150 is plural, and when the number of the thrust lubrication grooves 150 is two, the two thrust lubrication grooves 150 are symmetrically disposed on the first bearing 140 around the axis of the first bearing 140. When the number of the thrust lubrication grooves 150 is three, the three thrust lubrication grooves 150 are uniformly arranged on the first bearing 140. By uniformly disposing the plurality of thrust lubrication grooves 150 on the first bearing 140, lubrication oil can be guided and drained uniformly.

Further, as shown in fig. 1, a portion of the pump cover 111 extends away from the pump portion 130 to constitute an extension 112, the extension 112 being used to form the oil pool 113. The pump device 100 further includes a first lubrication groove 141, where the first lubrication groove 141 is disposed through the first bearing 140 in an axial direction, and the first lubrication groove 141 communicates with the shaft hole of the first bearing 140, the thrust lubrication groove 150, and the oil sump 113, respectively.

In this embodiment, the shaft hole of the first bearing 140 is a through hole that is axially perforated, the extension portion 112 is formed by a portion of the pump cover 111 extending away from the pump portion 130, and the extension portion 112 forms an oil pool 113, the oil pool 113 is used for storing lubricating oil, and the through hole is capable of communicating the oil pool 113 with the thrust lubrication groove 150. Specifically, during the high-speed rotation of the rotating shaft 121, the rotating shaft 121 shears the lubricating oil in the clearance between itself and the first bearing 140, the lubricating oil enters the clearance between the rotating shaft 121 and the first bearing 140 from the oil sump 113, the lubricating oil enters the thrust lubrication groove 150 from the clearance under the action of the shearing force ω, the oil in the clearance between the first bearing 140 and the rotating shaft 121 forms a layer of oil film and plays a lubrication role, and then the oil is pumped into the thrust lubrication groove 150 to lubricate the contact surface between the first gear 131 and the first bearing 140, and passes through the clearance between the first bearing 140, the pump cover 111 and the pump portion 130, and then enters the low-pressure area oil sump 113 under the action of the pressure difference and the gravity.

Further, as shown in fig. 1, a first lubrication groove 141 is provided penetrating the first bearing 140 in the axial direction, and the first lubrication groove 141 communicates with the shaft hole of the first bearing 140. I.e. a portion of the inner side wall of the first bearing 140 is recessed away from the rotation shaft 121 to define a first lubrication groove 141. Lubricating oil enters a gap between the rotating shaft 121 and the first bearing 140 and the first lubricating groove 141 from the oil pool 113, the first lubricating groove 141 can be filled with and stores the lubricating oil, and the lubricating oil in the first lubricating groove 141 is coated on the rotating shaft 121 along with the rotation of the rotating shaft 121, so that the inner wall of the first bearing 140 is lubricated, the reliable lubrication between the rotating shaft 121 and the first bearing 140 is further ensured, and the minimum oil film thickness of fluid lubrication between the first bearing 140 and the rotating shaft 121 is ensured. It should be noted that the number of the first lubrication grooves 141 is at least one.

Further, as shown in fig. 1, 5 and 6, the housing 110 further includes a casing 114 and a second bearing 170, the casing 114 is connected to the pump cover 111, and the casing 114 is enclosed outside the motor part 120 and the pump part 130. The second bearing 170 is connected to the casing 114 and sleeved on the rotating shaft 121, and the second bearing 170 is located between the motor part 120 and the pump part 130.

In this embodiment, the first bearing 140 and the second bearing 170 are both sleeved on the rotating shaft 121, so that the first bearing 140 and the second bearing 170 can play a role in supporting the rotating shaft 121. The support is a lubrication support, the axes of the first bearing 140, the second bearing 170 and the rotating shaft 121 are coincident, and in the working process, the rotating shaft 121 drives the pump part 130 to rotate, so that the pump part 130 can apply a radial force to the rotating shaft 121, the radial force can push the bearing to deflect towards one side, the first bearing 140 and the second bearing 170 can play a role in supporting the rotating shaft 121, the play of the rotating shaft 121 is controlled within a reasonable range, the large play is avoided, and meanwhile, the position of the axis of the rotating shaft 121 can be controlled.

It should be noted that, compared with the form of the double rolling bearing, the sliding bearing works stably, reliably and noiseless, under the condition of liquid lubrication, the sliding surface is separated by the lubricating oil without direct contact, friction loss and surface abrasion can be greatly reduced, the gap between the sliding bearing and the rotating shaft 121 is filled with the lubricating oil, the lubricating oil on the sliding surface forms a layer of oil film, fluid lubrication is realized, the oil film also has a certain shock absorbing capability, and the service lives of the first bearing 140, the second bearing 170 and the rotating shaft 121 are prolonged. The two sliding bearings support the rotating shaft 121, the play of the rotating shaft 121 is small, and the position degree of the axis of the rotating shaft 121 can be controlled within a reasonable range; compared with the form that the double rolling bearing is matched with the sliding bearing, only two sliding bearings are used, so that the supporting structure can be simplified, and the cost can be reduced.

Example IV

On the basis of the foregoing embodiment, as shown in fig. 5 and 6, it is proposed that the pump apparatus 100 further includes a second bearing 170, where the second bearing 170 is disposed on one side of the pump portion 130 near the motor portion 120, that is, the first bearing 140 and the second bearing 170 are respectively located on two sides of the pump portion 130 in the axial direction, and in operation, the rotation shaft 121 needs to drive the pump portion 130 to rotate, so that the load of the rotation shaft 121 is mainly concentrated on the pump portion 130, and by the cooperation of the rotation shaft 121, the first bearing 140 and the second bearing 170, the load from the pump portion 130 can be shared by the three portions of the rotation shaft 121, the first bearing 140 and the second bearing 170, so that damage to the rotation shaft 121 due to the concentration of the load on the rotation shaft 121 during long-time operation can be avoided to a certain extent.

Further, the first bearing 140 has a first bearing 140 face near the rotation shaft 121, the second bearing 170 has a second bearing 170 face near the rotation shaft 121, and the axial height of the second bearing 170 face is smaller than or equal to the axial height of the first bearing 140 face, that is, not larger than. When the distance between the first bearing 140 and the pump portion 130 and the distance between the second bearing 170 and the pump portion 130 are equal, the loads from the pump portion 130 carried on the first bearing 140 and the second bearing 170 are equal. However, since the second bearing 170 is closer to the motor part 120 than the first bearing 140, during the rotation of the rotor 122 in the motor part 120, a radial force is generated between the stator 123 and the rotor 122, and a load is also generated on the rotating shaft 121, so that the second bearing 170 is required to bear the load from the motor part 120, by making the surface of the second bearing 170 equal to or greater than the surface of the first bearing 140, the first bearing 140 and the second bearing 170 are more suitable for the requirements of different loads at different positions of the rotating shaft 121, and on the premise of ensuring the lubrication reliability of the rotating shaft 121, the power consumption of the rotating shaft 121 can be reduced to the minimum level.

Further, the sum of the axial heights of the first bearing 140 face and the second bearing 170 face is equal to or greater than the axial height of the pump portion 130.

In this embodiment, the first bearing 140 face and the second bearing 170 face are large enough to enable the first bearing 140 and the second bearing 170 to share more load, reducing the load applied by the pump section 130 to the shaft 121. And the first bearing 140 and the second bearing 170 can be more reliable when supporting the rotating shaft 121, and the supporting surface is not damaged due to too small.

Further, the ratio of the axial height of the second bearing surface to the axial diameter Df of the second bearing 170 is 1.25 or more and 1.38 or less; and/or the ratio of the axial height of the first bearing surface to the axial diameter of the first bearing 140 is 1.13 or more and 1.38 or less.

In this embodiment, it is possible to obtain a map of the relation between the second bearing 170 width-to-diameter ratio and the oil film thickness, in which the second bearing 170 width-to-diameter ratio is positively correlated with the oil film thickness, and when the second bearing 170 width-to-diameter ratio is 1.25 or more, the oil film thickness formed at the second bearing surface is in a suitable range, that is, 1.4 μm or more, which is the minimum oil film thickness for fluid lubrication, so that the lubrication reliability performance of the rotating shaft 121 can be ensured, and the power consumption of the rotating shaft 121 can be reduced to the minimum level. In addition, the second bearing 170 has a ratio of 1.38 or less, which prevents the oil film thickness from being excessively large, and when the oil film thickness exceeds 2 μm, the PV value is excessively large, which may cause an increase in power consumption of the bearing, although fluid lubrication may be satisfied. Taking both lubrication and power consumption into consideration, the requirements of both lubrication and power consumption can be well balanced by having the aspect ratio of the second bearing 170 satisfy the above relationship.

Further, as can be seen from the graph of the relation between the width-to-diameter ratio of the first bearing 140 and the oil film thickness, the width-to-diameter ratio of the first bearing 140 is positively correlated with the oil film thickness, and when the width-to-diameter ratio of the first bearing 140 is 1.13 or more, the oil film thickness formed at the first bearing surface is in a proper range, that is, 1.4 μm or more of the minimum oil film thickness of the fluid lubrication, so that the lubrication reliability of the rotating shaft 121 can be ensured, and the power consumption of the rotating shaft 121 can be reduced to the minimum level. In addition, the first bearing 140 has a width to diameter ratio of 1.38 or less, which prevents the oil film thickness from being excessively large, and when the oil film thickness exceeds 2 μm, although fluid lubrication can be satisfied, the PV value is excessively large, which causes an increase in power consumption of the bearing. In consideration of both lubrication and power consumption, the requirements of both lubrication and power consumption can be well balanced by making the aspect ratio of the first bearing 140 satisfy the above relation.

Specifically, the load of the pump unit 130 is applied to the shaft 121, the pressure generated by the shaft 121 against the bearing is P, the rotation speed of the shaft 121 is V, the PV value is related to the height of the bearing, and from the calculation aspect, the thicker the oil film thickness is, the higher the bearing height is, the PV value is increased, and the power consumption of the bearing is increased.

Further, the shaft diameter of the first bearing 140 is 6mm or more and 12mm or less; the shaft diameter of the second bearing 170 is 6mm or more and 12mm or less.

In this embodiment, as can be seen from the graph of the shaft diameter of the bearing (the first bearing 140, the second bearing 170) and the bearing deformation amount, and the graph of the shaft diameter of the bearing and the power consumption, when the shaft diameter is smaller than 6mm, the bearing deformation amount is larger, which is unfavorable for the bearing to support the rotating shaft 121; when the shaft diameter is larger than 12mm, the power consumption of the bearing increases sharply, so that the shaft diameter of the first bearing 140 satisfies Df which is smaller than or equal to 6mm and smaller than or equal to 12mm, and the shaft diameter of the first bearing 140 satisfies Ds which is smaller than or equal to 6mm and smaller than or equal to 12mm, thereby satisfying the requirement of the power consumption of the bearing and avoiding overlarge deformation of the bearing.

Example five

On the basis of the third embodiment, as shown in fig. 5 and 6, the specific structure of the second bearing 170 is described in this embodiment, and further, the pump apparatus 100 further includes an oil groove 171 and a throttle groove 172, the oil groove 171 being provided on a first end surface of the second bearing 170 facing the pump portion 130, the oil groove 171 communicating with the first pressure chamber 134 of the pump portion 130. A throttle groove 172 is provided on the first end surface, the throttle groove 172 communicating the oil groove 171 and the gap between the second bearing 170 and the rotating shaft 121.

In this embodiment, the oil groove 171 is provided at the high pressure side of the pump part 130, and the oil groove 171 can balance the pressure between the respective chambers in the high pressure side so that the pressures of the respective chambers at the high pressure side are similar, whereby noise and mechanical vibration during operation can be reduced. The throttling groove 172 is provided on the first end surface, that is, the throttling groove 172 is provided on the first end surface of the first bearing 140 facing the pump portion 130, and the throttling groove 172 is used to communicate the oil groove 171 and the gap between the second bearing 170 and the rotating shaft 121. That is, the oil in the first pressure chamber 134 flows to the oil groove 171, and then flows to the gap between the second bearing 170 and the rotating shaft 121 through the throttling groove 172, so that the throttling groove 172 can effectively prevent too much oil from flowing into the gap between the second bearing 170 and the rotating shaft 121 at the same time, and further the displacement of the pump is affected. In order to ensure the fluid lubrication performance between the second bearing 170 and the rotating shaft 121, that is, to provide sufficient lubrication oil to the gap between the second bearing 170 and the rotating shaft 121, and at the same time, to ensure that the displacement of the pump portion 130 is not seriously leaked, that is, the displacement is not significantly affected by the oil used for lubrication, through the cooperation of the oil groove 171 and the throttle groove 172, the lubrication requirement between the second bearing 170 and the rotating shaft 121 can be achieved, and the oil flow used for lubrication is not too large, so that the displacement of the pump device 100 is reduced.

Further, the pump device 100 further includes a second lubrication groove 173, the second lubrication groove 173 is provided to penetrate the second bearing 170 in the axial direction, and the second lubrication groove 173 communicates with the shaft hole of the second bearing 170 and the throttle groove 172, respectively.

In this embodiment, a second lubrication groove 173 is provided penetrating the second bearing 170 in the axial direction, the second lubrication groove 173 communicating with the shaft hole of the second bearing 170. That is, the second lubrication groove 173 is concavely formed by a portion of the inner sidewall of the second bearing 170 facing away from the rotation shaft 121, and the second lubrication groove 173 communicates with the throttle groove 172. Because of the pressure difference, the oil in the first pressure chamber 134 sequentially flows into the gap between the second bearing 170 and the rotating shaft 121 through the oil groove 171 and the throttling groove 172, and simultaneously can fill the second lubrication groove 173, and as the rotating shaft 121 rotates, the oil in the second lubrication groove 173 can be coated on the surface of the rotating shaft 121, and the second lubrication groove 173 plays a role of temporarily storing the lubricating oil, so that a fluid lubrication film is formed between the inner wall of the second bearing 170 and the rotating shaft 121, and the reliable lubrication between the rotating shaft 121 and the second bearing 170 is further ensured.

Further, as shown in fig. 5 and 6, the pump device 100 further includes a sealing member 181 connected to a side of the second bearing 170 facing away from the pump portion 130, the sealing member 181 is sleeved on the rotating shaft 121, the sealing member 181, the second bearing 170 and the rotating shaft 121 form a liquid passing cavity 182, and the liquid passing cavity 182 is communicated with the second lubrication groove 173.

In this embodiment, the second bearing 170 is connected to the casing 114, and the second bearing 170 may divide the cavity 115 enclosed by the casing 114 into a motor cavity and a pump cavity, so that the spatial arrangement may be more reasonable. The motor portion 120 is located within a motor cavity and the pump portion 130 is located within a pump cavity. The pump device 100 further comprises a sealing member 181, the sealing member 181 is connected to the second bearing 170 and is located in the motor cavity, and the sealing member 181 is sleeved on the rotating shaft 121. Further, by means of the sealing member 181, the cavity 115 can be divided into a relatively sealed motor cavity and a pump cavity, so that working medium (lubricating oil) cannot flow into the motor cavity, normal use of the stator 123, the rotor 122, the control part 190 and other components in the motor cavity cannot be affected, other structures are not required to be additionally arranged in the motor cavity to ensure that parts in the motor cavity are corroded, the sealing performance of the pump device 100 is better, and meanwhile, the structure is simpler, so that cost is reduced.

Further, the seal 181, the second bearing 170 and the rotation shaft 121 form a liquid passing chamber 182, and the liquid passing chamber 182 communicates with the second lubrication groove 173. The liquid passing cavity 182 formed by the sealing element 181, the second bearing 170 and the rotating shaft 121 can store a part of lubricating oil, the part of lubricating oil can also flow into the second lubricating groove 173, and the liquid passing cavity 182 can play a certain buffering role by controlling the connection strength of the sealing element 181 and the first bearing 140, namely the pressure born by the sealing element 181, so that the oil in the liquid passing cavity 182, the second lubricating groove 173 and the throttling groove 172 can be in a pressure relatively balanced state, thereby being beneficial to ensuring the fluid lubricating performance of the rotating shaft 121 and the second bearing 170.

Further, the pump device 100 further includes a relief groove 174, the relief groove 174 is disposed on the second bearing 170, and the relief groove 174 communicates with the liquid chamber 182 and the second pressure chamber 135 of the pump portion 130.

In this embodiment, relief groove 174 is provided on second bearing 170, and relief groove 174 is configured to communicate with fluid chamber 182 and second pressure chamber 135. The pressure relief groove 174 may be in a through hole form, so that two ends of the through hole can be respectively communicated with the second pressure cavity 135 and the liquid passing cavity 182, and the pressure in the liquid passing cavity 182 can be better released due to the smaller pressure born by the second pressure cavity 135, so that the pressure of the oil is buffered by the liquid passing cavity 182.

Further, by providing the oil groove 171, the throttling groove 172, the second lubrication groove 173, the liquid passing cavity 182 and the pressure relief groove 174 on the second bearing 170, a complete lubrication oil path of the second bearing 170, that is, high-pressure oil liquid returns from the oil groove 171, through the throttling groove 172, the second lubrication groove 173 and the liquid passing cavity 182, to the second pressure cavity 135 with lower pressure through the pressure relief groove 174, so that the pressure in the liquid passing cavity 182 is not too high, the pressure is prevented from being higher than the pressure limit value which can be borne by the sealing element 181, the reliability of the position of the sealing element 181 is ensured, the sealing element 181 is effectively prevented from being separated from the second bearing 170, the leakage of the lubricating oil is caused, and the sealing performance between the motor cavity and the pump cavity cannot be ensured.

Example six

On the basis of the foregoing embodiment, as shown in fig. 5 and 6, the structure of the second bearing 170 is further described in this embodiment, and further, the pump apparatus 100 further includes a buffer chamber 175, where the buffer chamber 175 is disposed on an end surface of the second bearing 170 facing away from the pump portion 130.

In this embodiment, the buffer chamber 175 is disposed on the end surface of the second bearing 170 facing away from the pump portion 130, specifically, the buffer chamber 175 may be tapered, that is, the buffer chamber 175 may be a tapered chamber, so that the buffer chamber 175 can reduce the rigidity of the second bearing 170, provide flexible support for the rotating shaft 121, reduce the surface pressure of the second bearing 170 facing away from the axial end surface of the pump portion 130, and effectively improve the wear condition of the second bearing 170 and the rotating shaft 121.

Further, the opening area of the buffer chamber 175 is larger than the bottom wall area of the buffer chamber 175, so that the buffer chamber 175 can be provided as a conical chamber, and the flexible support can be provided for the rotating shaft 121, thereby being convenient for maintenance and demoulding.

Further, the buffer chamber 175 includes a first wall surface, the first wall surface is a wall surface close to the rotation shaft 121, from the opening end of the buffer chamber 175 to the bottom wall of the buffer chamber 175, the distance between the first wall surface and the rotation shaft 121 increases, which can be understood that the first wall surface is obliquely arranged, the position of the first wall surface at the opening end of the buffer chamber 175 is closer to the rotation shaft 121, the distance between the first wall surface and the rotation shaft 121 is smaller at the opening, and the distance between the first wall surface and the rotation shaft 121 is larger at the position at the bottom of the chamber, so that a right angle structure is not formed between the first wall surface and the bottom of the groove. Since the second bearing 170 is generally made of an aluminum alloy material, when the rotating shaft 121 contacts with the end portion of the second bearing 170, the second bearing 170 is deformed, and if the connection portion between the first wall surface and the bottom wall of the conical cavity is in a right-angle structure, stress concentration occurs at the connection portion between the first wall surface and the bottom wall of the groove body, and when the second bearing 170 is under the pressure of the rotating shaft 121, the second bearing 170 is easily broken at the connection portion between the first wall surface and the bottom wall of the buffer cavity 175. When the first wall surface is inclined with respect to the axial direction of the rotating shaft 121, the first wall surface is not in a right angle structure with the bottom wall of the buffer chamber 175, so that the damage rate of the second bearing 170 can be effectively reduced.

Further, the buffer chamber 175 includes a second wall surface, the second wall surface is far away from the wall surface of the rotating shaft 121 relative to the first wall surface, the second wall surface is inclined relative to the axial direction of the rotating shaft 121, the distance between the second wall surface and the rotating shaft 121 is larger at the opening of the buffer chamber 175, and the distance between the second wall surface and the rotating shaft 121 is smaller at the bottom wall of the buffer chamber 175. It can be appreciated that in the axial direction away from the motor portion 120, the distance between the first wall surface and the rotating shaft 121 increases, the distance between the second wall surface and the rotating shaft 121 decreases, and the buffer chamber 175 is configured in an inverted cone shape, so that the inverted cone-shaped buffer chamber 175 is beneficial to drawing during processing of the buffer chamber 175.

Further, the buffer chambers 175 are configured in an annular structure, that is, the buffer chambers 175 are disposed in the circumferential direction of the second bearing 170, when the rotation shaft 121 rotates, the radial force applied to the second bearing 170 may be changed at any time, that is, the radial force applied to the second bearing 170 may be changed in multiple directions, and no matter which direction the radial force applied to the second bearing 170 is directed, the existence of the annular buffer chambers 175 enables the second bearing 170 to be deformed, so that the rotation shaft 121 and the second bearing 170 are flexibly connected, the radial force of the second bearing 170 acts as a buffer to the rotation shaft 121, and the problem that the second bearing 170 is easily damaged due to rigid connection of the rotation shaft 121 and the second bearing 170 is avoided.

Example seven

On the basis of the foregoing embodiment, as shown in fig. 1, the present embodiment describes a specific structure of the motor part 120, and further, the motor part 120 further includes a rotor 122 and a stator 123, and the rotor 122 is connected to the rotating shaft 121. The stator 123 is sleeved outside the rotor 122, and the stator 123 comprises a stator core and a stator winding, wherein the stator winding is arranged on the stator core. The pump device 100 further comprises a control part 190, the control part 190 being arranged on the side of the motor part 120 facing away from the pump part 130, the control part 190 being connected to the housing 110 and being located in the cavity 115, the ends of the stator windings being electrically connected to the control part 190.

In this embodiment, the motor portion 120 further includes a rotor 122 and a stator 123. Wherein, rotor 122 links to each other with pivot 121, and rotor 122 and pivot 121 can be coaxial setting, and rotor 122 and pivot 121's cooperation mode can be interference fit, and rotor 122 and pivot 121 are not coaxial setting but both transmission connection, carry out nimble setting according to the actual conditions still can be, rotor 122. The stator 123 is sleeved outside the rotor 122, and the stator 123 comprises a stator core and a stator winding, wherein the stator winding is arranged on the stator core. In addition, the pump device 100 further includes a control portion 190, where the control portion 190 is disposed on a side of the motor portion 120 away from the pump portion 130, that is, the control portion 190 is disposed at a position of the motor portion 120 away from the pump portion 130, and since the vibration at a position close to the pump portion 130 is relatively obvious and the load is relatively large during operation, the control portion 190 is far away from the pump portion 130, which can protect the control portion 190 to a certain extent, and thus the service life of the control portion 190 is prolonged. Further, a control portion 190 is connected to the housing 110 and located in the cavity 115, and the ends of the stator windings, typically copper wires, are electrically connected to the control portion 190.

Specifically, during the operation of the pump device 100, the control part 190 controls the current of the stator winding in the stator 123 to change according to a certain rule, so as to control the stator 123 to generate a changed excitation magnetic field, and the rotor 122 rotates under the action of the excitation magnetic field, so that the rotating shaft 121 drives the first gear 131 in the pump part 130 to rotate, and further the second gear 133 moves. When the first gear 131 and the second gear 133 in the pump part 130 are rotated, the volume of the compression chamber formed between the first gear 131 and the second gear 133 is changed due to the eccentric movement of the second gear 133, so that the working medium introduced into the compression chamber is pushed out to the oil outlet 162 to generate flowing power.

Example eight

According to a second aspect of the present invention there is provided a vehicle 200 comprising a pump device 100 provided by any of the designs described above.

The vehicle 200 provided by the present invention includes the pump device 100 provided by any of the above designs, so that the vehicle has all the advantages of the pump device 100, which are not described herein.

It should be noted that the vehicle 200 may be a new energy vehicle. The new energy automobile comprises a pure electric automobile, a range-extended electric automobile, a hybrid electric automobile, a fuel cell electric automobile, a hydrogen engine automobile and the like. Of course, the vehicle 200 may be a conventional fuel vehicle.

In a particular embodiment, as shown in FIG. 7, a vehicle 200 includes a body 210 and an engine 220. The pump device 100 and the engine 220 are both arranged in the vehicle body 210, the engine 220 comprises a mounting seat 221, the mounting seat 221 is connected with the extension part 112 of the pump device 100, so that an oil pool 113 is formed through the cooperation of the mounting seat 221 and the extension part 112, and the oil pool 113 can be communicated with an oil source of the engine 220 to realize oil way communication.

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

Specifically, the pump device 100 includes a housing 110, a motor portion 120, a pump portion 130, a first bearing 140, and a thrust lubrication groove 150. Wherein the housing 110 has a cavity 115. The motor part 120 is disposed in the cavity 115, and the motor part 120 includes a rotation shaft 121 rotating around a central axis of the motor part 120. The pump part 130 is disposed at one side of the motor part 120 in the axial direction and contacts the rotation shaft 121, and the pump part 130 can be rotated by the rotation shaft 121. The first bearing 140 is connected to the housing 110 and sleeved on the rotating shaft 121, and the first bearing 140 is located on a side of the pump portion 130 away from the motor portion 120. The thrust lubrication groove 150 is provided on an end surface of the first bearing 140 near the pump portion 130 and communicates with the shaft hole of the first bearing 140.

The pump device 100 provided by the present invention includes a housing 110, a motor portion 120, a pump portion 130, a first bearing 140, and a thrust lubrication groove 150. The housing 110 has a cavity 115, and the motor portion 120 and the pump portion 130 are both accommodated in the housing 110, so that the housing 110 ensures that the motor portion 120 and the pump portion 130 are not affected by external environment, and can operate normally.

In the present invention, the term "plurality" means two or more, unless explicitly defined otherwise. The terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; "coupled" may be directly coupled or indirectly coupled through intermediaries. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.

In the description of the present specification, the terms "one embodiment," "some embodiments," "particular embodiments," and the like, mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A pump apparatus, comprising:

A housing having a cavity;

the motor part is arranged in the cavity and comprises a rotating shaft rotating around the central axis of the motor part;

The pump part is arranged on one axial side of the motor part and is contacted with the rotating shaft, and the pump part can be driven by the rotating shaft to rotate;

the first bearing is connected with the shell and sleeved on the rotating shaft, the first bearing is positioned at one side of the pump part, which is away from the motor part, and the first bearing comprises a sliding bearing;

The thrust lubrication groove is arranged on the end surface of the first bearing close to the pump part and is communicated with the shaft hole of the first bearing;

The thrust lubrication groove comprises a thrust wall comprising at least one thrust section comprising a first thrust section extending near the centre of the thrust lubrication groove in an axial direction away from the pump section;

the number of the thrust walls is at least two, and the at least two thrust walls comprise:

the first end of the first thrust wall is connected with the inner side wall of the first bearing, a tangent plane where a connecting point of the first thrust wall and the inner side wall of the first bearing is located is a first reference plane, and an included angle beta 1 between the first thrust wall and the first reference plane is more than or equal to 0 degrees and less than 90 degrees;

the at least two thrust walls further include:

The second thrust wall is arranged opposite to the first thrust wall, the first end of the second thrust wall is connected with the inner side wall of the first bearing, a tangent plane where a connecting point of the second thrust wall and the inner side wall of the first bearing is located is a second reference plane, and an included angle beta 2 between the second thrust wall and the second reference plane is larger than 0 degrees and smaller than 90 degrees;

The second end of the second thrust wall is connected with the second end of the first thrust wall; or (b)

The at least two thrust walls further include:

And the third thrust wall is respectively connected with the second end of the first thrust wall and the second end of the second thrust wall.

2. A pump apparatus according to claim 1, wherein,

The notch area of the thrust lubrication groove in the axial direction is larger than the groove bottom area of the thrust lubrication groove.

3. A pump apparatus according to claim 2, wherein,

And an included angle alpha between the first thrust section and the axial end surface of the first bearing is more than or equal to 0 degrees and less than 90 degrees.

4. The pump apparatus of claim 2, wherein the at least one thrust segment further comprises:

and the second thrust section axially extends and is connected between the first thrust section and the bottom of the thrust lubrication groove.

5. A pump apparatus according to claim 2, wherein,

The third thrust wall of the thrust lubrication groove is an arc-shaped wall.

6. A pump apparatus according to any one of claims 1 to 5,

The pump section includes:

the first gear is matched with the rotating shaft, a plurality of tooth roots of the first gear form root circles, the root circles extend in the axial direction to form an inner circular surface, and the thrust lubrication groove is located in the inner circular surface.

7. The pump apparatus of claim 6, wherein the pump apparatus comprises a pump unit,

The pump section further includes:

the second gear is arranged outside the first gear, the first gear can drive the second gear to rotate, the second gear and the first gear form a first pressure cavity and a second pressure cavity, and the pressure born by the first pressure cavity is larger than the pressure born by the second pressure cavity;

The housing includes:

the pump cover is arranged on one side, away from the motor part, of the pump part and is connected with the first bearing;

The pump device further includes:

The oil inlet is axially formed in the pump cover and/or the first bearing, and is communicated with the second pressure cavity;

the oil outlet is radially arranged on the pump cover and the first bearing, and is communicated with the first pressure cavity;

the tail end of the thrust lubrication groove extends away from the shaft hole of the first bearing, and the tail end of the thrust lubrication groove is located between the oil inlet and the oil outlet.

8. A pump apparatus according to any one of claims 1 to 5,

The number of the thrust lubrication grooves is multiple, and the thrust lubrication grooves are arranged on the first bearing at intervals.

9. The pump apparatus of claim 7, wherein the pump apparatus comprises a pump unit,

A portion of the pump cap extends away from the pump portion to form an extension for forming an oil sump;

The pump device further includes:

the first lubrication groove is arranged on the first bearing in a penetrating way along the axial direction, and the first lubrication groove is respectively communicated with the shaft hole of the first bearing, the thrust lubrication groove and the oil pool.

10. The pump apparatus of claim 7, wherein the pump apparatus comprises a pump unit,

The housing further includes:

the shell is connected with the pump cover and is arranged on the outer sides of the motor part and the pump part in a surrounding mode;

The pump device further includes:

and the second bearing is connected with the shell and sleeved on the rotating shaft, and the second bearing is positioned between the motor part and the pump part.

11. The pump apparatus of claim 10, wherein the pump apparatus further comprises:

An oil groove provided on a first end surface of the second bearing toward the pump portion, the oil groove communicating with a first pressure chamber of the pump portion;

And the throttling groove is arranged on the first end face and is communicated with the oil groove and a gap between the second bearing and the rotating shaft.

12. The pump apparatus of claim 11, wherein the pump apparatus further comprises:

The second lubrication groove is arranged on the second bearing in a penetrating way along the axial direction and is respectively communicated with the shaft hole of the second bearing and the throttling groove.

13. The pump apparatus of claim 12, wherein the pump apparatus further comprises:

The sealing piece is connected to one side, away from the pump part, of the second bearing, the sealing piece is sleeved on the rotating shaft, the sealing piece, the second bearing and the rotating shaft form a liquid passing cavity, and the liquid passing cavity is communicated with the second lubrication groove.

14. The pump apparatus of claim 13, wherein the pump apparatus further comprises:

The pressure relief groove is arranged on the second bearing and is communicated with the liquid passing cavity and the second pressure cavity of the pump part.

15. The pump apparatus according to any one of claims 10 to 14, further comprising:

And the buffer cavity is arranged on the end face of the second bearing, which is away from the pump part.

16. The pump apparatus according to any one of claims 9 to 14, wherein the motor portion further includes:

the rotor is connected with the rotating shaft;

The stator is sleeved outside the rotor and comprises a stator core and a stator winding, and the stator winding is arranged on the stator core;

The pump device further includes:

And the control part is arranged on one side of the motor part, which is away from the pump part, and is connected to the shell and positioned in the cavity, and the end part of the stator winding is electrically connected with the control part.

17. A vehicle, characterized by comprising: a pump arrangement as claimed in any one of claims 1 to 16.