CN114135384A

CN114135384A - Pump device and vehicle

Info

Publication number: CN114135384A
Application number: CN202010913992.2A
Authority: CN
Inventors: 化豪爽; 曹小军; 付威; 葛笑
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: 2022-03-04
Anticipated expiration: 2040-09-03
Also published as: CN114135384B

Abstract

An embodiment of the present invention provides a pump device and a vehicle, wherein the pump device includes a housing, a motor portion, a pump portion, a first bearing, a first oil groove, and a throttle groove. Wherein, the shell has the cavity. The motor part comprises a rotating shaft rotating around the central axis of the motor part. The pump part is arranged at one axial side of the motor part and is in contact 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 located between the motor part and the pump part. First oil groove sets up on the first terminal surface of first bearing towards pump portion, first oil groove and first pressure chamber intercommunication. The throttling groove is arranged on the first end face and communicated with the first oil groove and a gap between the first bearing and the rotating shaft. Through the cooperation use of first oil groove and throttle groove, both can satisfy the lubricated requirement between first bearing and the pivot, thereby be unlikely to the discharge capacity that the first bearing internal flow is too big again and reduce pump unit.

Description

Pump device and vehicle

Technical Field

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

Background

Generally, a pump device includes a motor portion and a pump portion, and a rotating shaft of the motor portion can drive the pump portion to rotate, so as to realize a compression function of the pump device. However, the rotating shaft may have a friction problem with other structures of the pump device during the high-speed rotation process, and in order to reduce the wear of the rotating shaft, the oil in the pump portion is generally used to lubricate the rotating shaft.

Disclosure of Invention

In order to solve at least one of the above technical problems, an object of an embodiment of the present invention is to provide a pump apparatus.

It is a further object of an embodiment of the present invention to provide a vehicle having the above pump apparatus.

To achieve the above object, an embodiment of a first aspect of the present invention provides a pump device including a casing, a motor portion, a pump portion, a first bearing, a first oil groove, and a throttle groove. Wherein, the shell has the cavity. The motor part comprises a rotating shaft rotating around the central axis of the motor part. The pump part is arranged at one axial side of the motor part and is in contact with the rotating shaft, and the pump part can be driven by the rotating shaft to rotate. The pump portion includes a first pressure chamber and a second pressure chamber, and the pressure that the first pressure chamber endures is greater than the pressure that the second pressure chamber endures. The first bearing is connected with the shell and sleeved on the rotating shaft, and the first bearing is located between the motor part and the pump part. First oil groove sets up on the first terminal surface of first bearing towards pump portion, first oil groove and first pressure chamber intercommunication. The throttling groove is arranged on the first end face and communicated with the first oil groove and a gap between the first bearing and the rotating shaft.

According to an embodiment of the pump device provided by the present invention, the pump device includes a housing, a motor portion, a pump portion, a first bearing, a first oil groove, and a throttle groove. The shell is provided with a cavity, and the motor part and the pump part are arranged in the cavity, so that the motor part and the pump part are not influenced by the external environment through the shell and can normally operate. The motor portion includes around the central axis pivoted pivot of motor portion, and the axial one side of motor portion is located to the pump portion, and pump portion contacts with the pivot, specifically, pump portion and pivot interference fit, and pump portion can be driven and rotate by the pivot, can understand that motor portion drives pump portion operation through the pivot. The pump portion includes a first pressure chamber and a second pressure chamber, and the pressure that the first pressure chamber bore is greater than the pressure that the second pressure chamber bore, and further, the first pressure chamber can be high pressure chamber, and the second pressure chamber can be low pressure chamber.

In addition, first bearing links to each other with the casing, and first bearing is located between motor portion and the pump portion, and first bearing cover is established on the pivot, and first bearing can play the effect of support to the pivot to a certain extent. It is worth explaining that, first bearing can provide lubricated support to the pivot, because the axle center coincidence of first bearing and pivot, in actual working process, pivot drive pump portion rotates, therefore pump portion can exert radial direction's power to the pivot, the pivot can promote first bearing one side partially towards when receiving radial force, at this moment, the pivot contacts with first bearing, first bearing will provide supporting role to the pivot to can be with the play control of pivot in reasonable scope, thereby be convenient for the control of pivot axle center.

It should be noted that the first bearing is a sliding bearing, and the sliding bearing refers to a bearing that operates under sliding friction. Compared with a rolling bearing, the sliding bearing is stable and reliable in operation and free of noise, the sliding surface is separated by lubricating oil and does not directly contact under the condition of liquid lubrication, friction loss and surface abrasion can be greatly reduced, a 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 vibration absorption capacity, and the service lives of the first bearing and the rotating shaft are prolonged.

Furthermore, first oil groove is located on the first terminal surface of first bearing towards pump portion, first oil groove and first pressure chamber intercommunication, because the pressure in the first pressure chamber is great, partly fluid can be flowed to first oil groove by first pressure chamber in, later flows into the clearance of pivot and first bearing again, guarantees the lubricating property between first bearing and the pivot.

Further, a throttle groove is formed in the first end face, namely the throttle groove is formed in the first end face, facing the pump portion, of the first bearing, and the throttle groove is used for communicating the first oil groove and a gap between the first bearing and the rotating shaft. That is to say, fluid in the first pressure chamber flows to first oil groove earlier, and rethread throttle groove flows to the clearance between first bearing and the pivot, and the throttle groove can effectually avoid too much fluid to flow in the clearance of first bearing and pivot, and then influences the discharge capacity of pump unit.

Therefore, in order to ensure the fluid lubrication performance between the first bearing and the rotating shaft, namely to provide sufficient lubricating oil for the gap between the first bearing and the rotating shaft, and simultaneously ensure that the displacement of the pump part does not seriously leak, namely the displacement of the pump part is not significantly influenced by the oil used for lubrication, the requirement of lubrication between the first bearing and the rotating shaft can be met through the matching use of the first oil groove and the throttling groove, and the displacement of the pump device is not reduced because the flow in the first bearing is too large.

Specifically, the first oil groove can balance the pressure between the cavities in the high-pressure side of the pump part, so that the pressure of the cavities in the high-pressure side is close, and the noise and the mechanical vibration in the operation process can be reduced.

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

In addition, the technical scheme provided by the invention can also have the following additional technical characteristics:

in above-mentioned technical scheme, further, a part of the inside wall of first bearing deviates from the pivot recess in order to form first lubrication groove, and first lubrication groove communicates with the throttle groove.

In this technical scheme, first lubrication groove is by the partly sunken formation of deviating from the pivot of the inside wall of first bearing, first lubrication groove and throttle groove intercommunication. Because of the pressure difference, the oil in the first pressure cavity sequentially passes through the first oil groove and the throttling groove and then flows into the gap between the first bearing and the rotating shaft, and meanwhile, the oil can be filled in the first lubricating groove. Further, first lubrication groove runs through the setting on first bearing along the axial, and first lubrication groove communicates with the shaft hole of first bearing, and the one end and the throttle groove intercommunication of first lubrication groove, the other end of first lubrication groove extend towards the direction of motor chamber. Furthermore, the number of the first lubricating grooves is at least one, and the first lubricating grooves can be flexibly arranged according to actual lubricating requirements.

In any of the above embodiments, the ratio of the cross-sectional flow area S1 of the throttle groove to the cross-sectional flow area S2 of the first lubrication groove is 0.1 or more and 0.4 or less.

In the technical scheme, the flow cross-sectional area of the throttling groove is controlled to be not more than 0.1 (S1/S2) and not more than 0.4, so that the flow cross-sectional area of the throttling groove is not too large, and the normal compression of the pump part can be ensured not to be influenced by excessive leakage of oil on the high-pressure side in the pump part, namely the oil does not excessively flow into the first lubricating groove through the throttling groove, and the discharge capacity of the pump part is not obviously influenced. Through limiting the cross-sectional area of the first lubricating groove, the cross-sectional area of the first lubricating groove is not too small, so that lubricating oil with sufficient flow can form an oil film between the first bearing and the rotating shaft, and the requirement of fluid lubrication is met.

In any of the above embodiments, the ratio of the cross-sectional flow area S2 of the first lubrication groove to the cross-sectional area S0 of the shaft hole of the first bearing is 0.02 or more and 0.08 or less.

In the technical scheme, the flow cross section of the first lubricating groove is limited to be not less than 0.02 (S2/S0) and not more than 0.08, the flow cross section of the first lubricating groove is not too small, and the lubricating oil can be ensured to have enough flow to form an oil film between the first bearing and the rotating shaft, so that the requirement of fluid lubrication is met. The through-flow cross-sectional area of the first lubricating groove is not too large, so that an oil film formed between the first bearing and the rotating shaft is too thick, and the power consumption of the rotating shaft is increased.

Furthermore, the cross-sectional area of the shaft hole of the first bearing is limited to be within a proper range, so that the oil cannot enter a gap between the rotating shaft and the first bearing due to too small cross-sectional area, and the strength of the first bearing cannot be affected due to too large cross-sectional area of the shaft hole of the first bearing. Specifically, the shaft diameter of the first bearing is greater than or equal to 6mm and less than or equal to 12 mm. According to the relation graph of the shaft diameter of the first bearing and the deformation of the first bearing and the relation graph of the shaft diameter of the first bearing and the power consumption, the comparison shows that when the shaft diameter is smaller than 6mm, the deformation of the bearing is large, and the bearing is not beneficial to supporting a rotating shaft; when the shaft diameter is larger than 12mm, the power consumption of the bearing is increased greatly, so that the shaft diameter of the first bearing meets the range, the power consumption requirement of the bearing is met, and the bearing can be prevented from being deformed too much.

In any of the above technical solutions, further, the pump device further includes a sealing element connected to a side of the first bearing away from the pump portion, the sealing element is sleeved on the rotating shaft, the sealing element, the first bearing and the rotating shaft form a fluid passing cavity, and the fluid passing cavity is communicated with the first lubricating groove.

In this technical scheme, first bearing is connected on the casing, and first bearing can be separated the cavity that the casing encloses for motor chamber and pump chamber to can make spatial arrangement more reasonable. The motor part is located in the motor cavity, and the pump part is located in the pump cavity. Wherein, the sealing member is connected in the one side that first bearing deviates from the pump portion and the sealing member cover is established on the pivot. Specifically, the sealing member can be isolated with the pump chamber with the motor chamber for working medium can not flow into the motor chamber, can not influence the normal use of parts such as stator, rotor, the control part in the motor chamber, need not additionally set up other structures in the motor chamber in order to guarantee that the spare part in the motor chamber receives the corruption, makes pump device's sealing performance better, and the structure is simpler simultaneously, is favorable to reduce cost.

It is worth mentioning that, a part of the first bearing deviates from the pump portion and extends to construct the installation position, and because the installation position and the first bearing are of an integrated structure, compared with a post-processing mode, the mechanical property of the integrated structure is better, so that the connection strength can be improved. In addition, the first bearings can be produced in batches, so that the processing efficiency of products is improved, the processing cost of the products is reduced, the integrity of the pump device is improved, the number of parts is reduced, the installation procedures are reduced, and the installation efficiency is improved. In addition, a part of the first bearing forms a mounting position for mounting the sealing element, so that the mounting accuracy of the sealing element can be ensured, and the bearing is simple to assemble, good in sealing performance and low in cost.

Further, the sealing element, the first bearing and the rotating shaft form a liquid passing cavity, and the liquid passing cavity is communicated with the first lubricating groove. The sealing member, the first bearing and the pivot form cross the sap cavity and can store some lubricating oil, cross the sap cavity and be used for storing the lubricating oil that comes from first lubrication groove, through the joint strength of control sealing member and first bearing, the pressure that sealing member self can bear promptly, cross the sap cavity and can play the cushioning effect, make and cross the sap cavity, first lubrication groove, fluid in the throttle groove can be in pressure equilibrium state, under the prerequisite of guaranteeing sealing member position stability, be favorable to guaranteeing the fluid lubrication performance of pivot and first bearing.

In any of the above technical solutions, further, the pump device further includes a pressure relief groove, the pressure relief groove is disposed on the first bearing, and the pressure relief groove is connected through the liquid chamber and the second pressure chamber.

In this technical scheme, the pressure relief groove is located on first bearing, and the pressure relief groove is used for communicating through sap cavity and second pressure chamber. The pressure relief groove can adopt a through hole form, so that two ends of the through hole can be communicated with the second pressure cavity and the liquid passing cavity, and the pressure in the second pressure cavity is smaller, so that the pressure in the liquid passing cavity can be better released, and the pressure of oil liquid is buffered by the liquid passing cavity.

Furthermore, the pressure relief groove is arranged on the first bearing, so that a complete lubricating oil path of the first bearing can be formed, that is, the oil in the first pressure chamber (high pressure chamber) enters the first oil groove, then flows into the gap between the first bearing and the rotating shaft and the first lubricating groove through the throttling groove, the rotating shaft and the first bearing are fully lubricated to form an oil film to meet the requirement of fluid lubrication, then the lubricating oil flows into the liquid cavity and further flows into the second pressure cavity (low-pressure cavity) from the pressure relief groove, so that the pressure in the whole lubricating oil path can be ensured not to be too high, the pressure in the liquid passing cavity cannot be too high, the pressure is prevented from being higher than the pressure limit value which can be borne by the sealing element, the reliability of the position of the sealing element is ensured, the sealing element is effectively prevented from being separated from the first bearing under high pressure, lubricating oil is prevented from leaking, and the sealing performance between the motor cavity and the pump cavity cannot be ensured.

In any of the above embodiments, the ratio of the cross-sectional flow area S3 of the pressure relief groove to the cross-sectional flow area S2 of the first lubrication groove is 1 or more and 4 or less.

In the technical scheme, 1 is less than or equal to (S3/S2) is less than or equal to 4. The flow cross-sectional area of the first lubricating groove is limited, so that the flow cross-sectional area of the first lubricating groove is not too small, sufficient flow of lubricating oil is ensured to form an oil film between the first bearing and the rotating shaft, and the requirement of fluid lubrication is met; meanwhile, the through-flow sectional area of the first lubricating groove cannot be too large, so that an oil film formed between the first bearing and the rotating shaft is too thick, and the power consumption of the rotating shaft is increased.

In addition, the flow area of the pressure relief groove is limited, so that the pressure of the oil seal cavity is not too high, the sealing effect of the oil seal is ensured, and the oil seal is prevented from being separated from the first bearing due to the fact that the pressure in the liquid cavity is too high. The invention considers the flow cross section area of the throttling groove, the flow cross section area of the first lubricating groove and the flow cross section area of the pressure relief groove, so that the three satisfy the relational expression, thereby ensuring that the first lubricating groove has sufficient oil flow to ensure the lubrication of the first bearing and the rotating shaft, simultaneously ensuring that the pressure in the liquid passing cavity is low enough, not influencing the sealing connection between the sealing element and the first bearing, and effectively reducing the oil leakage.

In any of the above technical solutions, further, the pump device further includes a buffer chamber, and the buffer chamber is disposed on an end surface of the first bearing facing away from the pump portion.

In this technical scheme, the cushion chamber is located on first bearing deviates from the terminal surface of pumping portion, and specifically, the cushion chamber can be the toper, and the cushion chamber can be the toper chamber promptly to the cushion chamber can reduce the rigidity of first bearing, provides flexible support for the pivot, reduces the face pressure that first bearing deviates from on the axial terminal surface of pumping portion, effectively improves the wearing and tearing condition of first bearing and pivot.

Further, the opening area of the buffer cavity is larger than the bottom wall area of the buffer cavity. The cushion chamber includes first wall, first wall is for being close to the wall of pivot, from the open end of cushion chamber to the diapire of cushion chamber, the increase of interval between first wall and the pivot, can understand, first wall slope sets up and first wall is located the position of cushion chamber open end and is close to the pivot more, the interval of first wall and pivot is less at the opening part, the interval of first wall and pivot is great in the position department that is located the chamber bottom, this also makes and does not form the right angle structure between the tank bottom of first wall and cell body. Because, first bearing adopts aluminum alloy material to make usually, consequently, when the tip of pivot and first bearing contacted, can make first bearing take place to deform, if the diapire junction of first wall and toper chamber is right angle structure, stress concentration's the condition can appear in the junction of the tank bottom of first wall and cell body, and when first bearing received the pressure of pivot, first bearing was easy to be in the connection structure department of the diapire of first wall and cushion chamber and is broken. And when the first wall surface is arranged in an inclined manner relative to the axial direction of the rotating shaft, the first wall surface and the bottom wall of the buffer cavity are not of a right-angle structure, so that the damage rate of the first bearing can be effectively reduced.

In any of the above technical solutions, further, the buffer chamber includes: the second wall, the second wall sets up with first wall is relative, from the open end of cushion chamber to the diapire of cushion chamber, and the interval between second wall and the pivot reduces.

In this technical scheme, the second wall sets up for the axial slope of pivot, and the second wall sets up with first wall relatively, and from the open end of cushion chamber to the diapire of cushion chamber, the interval between second wall and the pivot reduces to the second wall can be the central line axial symmetry setting about the cushion chamber with first wall, and the cushion chamber can be regular toper promptly, and then can be better provide flexible support for the pivot. It can be understood that, in the axial direction deviating from the motor part, the distance between the first wall surface and the rotating shaft is increased, the gap between the second wall surface and the rotating shaft is reduced, the buffer cavity is constructed into an inverted cone shape, and the inverted cone-shaped buffer cavity is beneficial to die drawing in the process of machining the buffer cavity.

Further, the cushion chamber is constructed as annular structure, that is to say, all be provided with the cushion chamber in the week of first bearing, when the pivot rotates, the radial force that first bearing received can change at any time, first bearing can receive the radial force of a plurality of direction changes promptly, and no matter the radial force that first bearing received is to which direction, certain deformation can take place for first bearing in the existence of annular cushion chamber, thereby make pivot and first bearing flexonics, first bearing plays the cushioning effect to the radial force of pivot, avoid pivot and first bearing rigid connection and cause the problem of first bearing easy damage.

In any of the above technical solutions, further, the pump device further includes a second bearing, the second bearing is connected to the housing and sleeved on the rotating shaft, and the second bearing is located on a side of the pump portion away from the first bearing.

In this technical scheme, the second bearing links to each other with the casing, and the second bearing cover is established in the pivot, and the second bearing is located one side that the pump portion deviates from first bearing, and first bearing and second bearing part put in the axial both sides of pump portion promptly, and first bearing is compared in the second bearing and is close to the motor portion more. The first bearing and the second bearing can support the rotating shaft, and the rotating shaft, the first bearing and the second bearing are matched for use, so that the load of the pump part can be shared by the rotating shaft, the first bearing and the second bearing in a balanced manner, and the damage to the rotating shaft caused by the concentrated load on the rotating shaft is avoided.

In particular, the first bearing and the second bearing are sliding bearings. Compared with a double-rolling bearing mode, the sliding bearing is stable and reliable in operation and free of noise, the sliding surface is separated by lubricating oil and does not directly contact under the liquid lubrication condition, friction loss and surface abrasion can be greatly reduced, the lubricating oil is filled in the gap between the sliding bearing and the rotating shaft, the lubricating oil on the sliding surface can form a layer of oil film, fluid lubrication is achieved, the oil film also has certain vibration absorption capacity, 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 clearance 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 and the sliding bearing are matched for use, the embodiment only uses two sliding bearings, so that the supporting structure can be simplified, and the cost can be reduced.

Further, the first bearing has a first bearing surface close to the rotating shaft, the second bearing has a second bearing surface close to the rotating shaft, and the axial height of the second bearing surface is smaller than or equal to that of the first bearing surface, namely not larger than that of the first bearing surface. When the first bearing is equidistant from the pump section and the second bearing is equidistant from the pump section, the load from the pump section is equal on the first bearing and the second bearing. However, the first bearing is closer to the motor part than the second bearing, and during the rotation of the rotor in the motor part, a radial force is generated between the stator and the rotor, and a load is also generated on the rotating shaft, so that the first bearing also needs to bear the load from the motor part, and the first bearing and the second bearing are more suitable for the requirements of different loads at different positions of the rotating shaft by enabling the second bearing surface to be smaller than or equal to the first bearing surface, and the power consumption of the rotating shaft can be reduced to the lowest level on the premise of ensuring the lubrication reliability of the rotating shaft.

In any one of the above technical solutions, further, a portion of the inner side wall of the second bearing is recessed away from the rotating shaft to form a second lubrication groove, and the second lubrication groove is communicated with the first pressure chamber.

In this technical scheme, the second lubrication groove is formed by the partly rotation axis of deviating from of the inside wall of second bearing is sunken, and the second lubrication groove communicates with first pressure chamber. Because there is the pressure differential, fluid in the first pressure chamber flows into the clearance between first bearing and the pivot through the second lubrication groove, and along with the rotation of pivot, fluid in the second lubrication groove can coat in the surface of pivot, and here the second lubrication groove can play the effect of short-term storage lubricating oil to can make and form the fluid lubrication oil film between the inner wall of second bearing and the pivot, further ensure the lubricating property between pivot and the bearing.

In any of the above technical solutions, further, the pump device further includes: and the thrust lubrication groove is arranged on the end face of the second bearing close to the pump part and communicated with the shaft hole of the second bearing.

In the technical scheme, the thrust lubrication groove is formed in the end face, close to the pump portion, of the second bearing, and the thrust lubrication groove is communicated with the shaft hole of the second bearing. The pivot can be sheared with the lubricating oil in the second bearing fit clearance when high-speed rotation, and lubricating oil can get into the lubricated groove of thrust through the second bearing oil groove under the effect of shearing force, forms certain speed and pressure. The end face of the inner gear and the end face of the pump cover move relatively, lubricating oil in the thrust lubricating groove can form an oil film, so that a fluid lubricating condition is formed between the end face of the inner gear and the contact surface of the end face of the pump cover, the lubricating gear reduces noise, thrust can be formed on the gear, and power consumption and abrasion of the thrust surface, namely a sliding surface between the inner gear and the pump cover, can be greatly improved.

Specifically, a thrust lubrication groove is provided on an end face of the second bearing near the pump portion, the thrust lubrication groove communicating with the second bearing and a shaft hole of the second bearing. Lubricating oil has in the fit clearance of second bearing and pivot, and the pivot is at high-speed rotatory in-process, and the pivot can be sheared its self lubricating oil in with the second bearing fit clearance, and lubricating oil can follow the fit clearance under the effect of shearing force omega and get into the thrust lubrication groove in, and the lubricating oil that gets into the thrust lubrication groove this moment has certain speed and pressure. The end face clearance in which the second bearing and the pump portion are in contact is small, and the lubricating oil in the thrust lubrication groove can flow to the end face clearance of the second bearing and the pump portion. Meanwhile, due to the relative motion between the pump part and the second bearing, a fluid lubrication condition is formed between the contact end surfaces of the pump part and the second bearing, namely an oil film is formed at the contact end surfaces of the second bearing and the pump part, so that the transition from boundary lubrication to fluid lubrication is realized between the second bearing and the pump part, the abrasion condition of the contact end surfaces of the pump part and the second bearing can be greatly improved, the power consumption is reduced, and the operation noise of the pump device can be reduced.

Further, the groove opening area of the thrust lubrication groove in the axial direction is larger than the groove bottom area of the thrust lubrication groove.

In this embodiment, the thrust lubrication groove includes two notches that are oriented differently, one notch oriented toward the pump portion and the other notch oriented toward the shaft. The design defines a slot area towards the pump section that is larger than the slot floor area. That is, the thrust lubrication groove is tapered in an axial direction away from the pump portion, i.e., in a direction from top to bottom. That is, 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 certain speed and pressure, on the other hand, because the gap of the end face of the second bearing contacting with the pump part is smaller, the groove wall of the thrust lubrication groove is inclined, so that a convergent wedge-shaped included angle is formed between the thrust lubrication groove and the end face gap, the lubricating oil in the thrust lubrication groove can flow into the end face gap of the pump part and the second bearing along the inclined groove wall, namely, the lubricating oil enters a small opening from a large opening, and it is worth explaining that the large opening refers to the thrust lubrication groove, and the small opening refers to the gap between the second bearing and the pump part. Therefore, the lubrication between the pump part and the second bearing can be enhanced, the lubrication state between the pump part and the second bearing is transited from boundary lubrication to fluid lubrication, and the wear rate between the pump part and the second bearing is effectively reduced.

In addition, in the high-speed rotation process of the rotating shaft and the pump part, the oil film between the contact surfaces of the pump part and the second bearing can generate force F for pushing the pump part to move upwards, so that lubricating oil positioned in the end surfaces of the second bearing and the pump part plays a role in floating sealing, and end surface leakage can be further reduced. According to the relevant literature, the end face leakage of the pump device accounts for 75% -80% of the total leakage of the pump device, so that the improvement of the leakage between the contact end faces in the pump device is of great importance. It is worth noting that the lubricating oil has a certain viscosity.

Further, the thrust lubrication groove includes a thrust wall including at least one thrust segment including a first thrust segment extending near a center of the thrust lubrication groove in an axial direction away from the pump portion.

In this solution, the thrust lubrication groove comprises a thrust wall, which is an inclined wall. The thrust wall extends near the center of the thrust lubrication groove in an axial direction away from the pump portion, i.e., in a top-down direction. The thrust wall includes at least one thrust segment including a first thrust segment extending in an axial direction away from the pump portion, proximate a center of the thrust lubrication groove. At this time, end face gaps formed among the thrust lubrication groove, the pump portion and the end face of the second bearing form a convergent wedge-shaped included angle, so that lubricating oil in the thrust lubrication groove can flow into the end face gap between the pump portion and the second bearing along the inclined first thrust section, namely the lubricating oil enters the small opening from the large opening. It should be noted that the "large port" refers to a thrust lubrication groove, and the "small port" refers to a clearance between the second bearing and the pump portion. Therefore, the lubrication between the pump part and the second bearing can be enhanced, the lubrication state between the pump part and the second bearing is transited from boundary lubrication to fluid lubrication, and the wear rate between the pump part and the second bearing is effectively reduced.

It should be noted that the first thrust section may be formed by at least one straight section and at least one curved section, the first thrust section 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 section extends close to the center of the thrust lubrication groove, that is, the inclined extension trend of the first thrust section satisfies the above relationship to facilitate the flow of the lubricating oil. The first thrust section can be formed by a plurality of sections of curved surfaces or a plurality of sections of circular arcs.

Further, the included angle alpha between the first thrust section and the axial end face of the second bearing is larger than 0 degrees and smaller than 90 degrees.

In this embodiment, the axial end face of the second bearing refers to the axial end face of the second bearing close to the pump portion, the included angle between the first thrust section and the axial end face is satisfied, α is greater than 0 ° and less than 90 °, so that the first thrust section can better guide the lubricating oil to the end face gap between the second bearing and the pump portion, the lubricating oil can enter the end face gap through the speed and the pressure of the lubricating oil itself and the lubricating oil can enter the end face gap through the guide of the first thrust section, 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 portion and the second bearing along the inclined groove wall, that is, the lubricating oil enters the small opening from the large opening. Therefore, the lubrication between the pump part and the second bearing can be enhanced, the lubrication state between the pump part and the second bearing is transited from boundary lubrication to fluid lubrication, and the wear rate between the pump part and the second bearing is effectively reduced. Further, the included angle α between the first thrust segment and the axial end face of the second bearing is 45 °. It is worth mentioning that the inclined first thrust section can be machined on the end face of the second bearing close to the pump part by using a forming cutter. Specifically, the longitudinal section (in the axial direction) of the thrust lubrication groove may be in the shape of an inverted triangle, a semicircle, or the like.

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

In this embodiment, the at least one thrust segment further comprises a second thrust segment extending axially to connect the first thrust segment and the groove bottom, the second thrust segment cooperating with the first thrust segment to form a thrust wall to ensure that the volume of the thrust lubrication groove meets the lubrication requirements. It is worth mentioning that, in the machining process, a straight groove is machined on the end face of the second bearing facing the pump part, and then the chamfer is machined, so that a first thrust section and a second thrust section can be formed, and the machining difficulty of the thrust lubrication groove can be reduced through the machining sequence.

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

In this embodiment, the number of thrust walls is at least two, each of the at least two thrust walls comprising 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.

Further, the at least two thrust walls comprise a first thrust wall, the first end of the first thrust wall is connected with the inner side wall of the second bearing, the tangent plane of the connection point of the first thrust wall and the inner side wall of the second bearing is a first reference plane, and an included angle beta 1 between the first thrust wall and the first reference plane is larger than or equal to 0 degrees and smaller than 90 degrees.

In this embodiment, the first end of the first thrust wall is the start end of the first thrust wall, the second end of the first thrust wall is the stop end of the first thrust wall, the first end is connected to the inner side wall of the second bearing, and the inner side wall of the second bearing is the side wall of the shaft hole of the second bearing. The tangent plane of the connection point of the first end and the second bearing is a first reference plane, and the included angle beta 1 between the first thrust wall and the first reference plane is greater than or equal to 0 degree and smaller than 90 degrees. The pivot is at high-speed rotatory in-process, and the pivot can be sheared its self and the lubricating oil in the second bearing fit clearance, and lubricating oil can be followed in the fit clearance and got into the thrust lubrication groove under the effect of shearing force omega in, and the lubricating oil that gets into the thrust lubrication groove this moment has certain speed and pressure. Because the rotatory direction of first thrust wall deviation pivot, then the lubricating oil in the thrust lubrication groove can take place axle shearing and face shearing, thereby form the negative pressure in the position department that the thrust lubrication groove is close to the shaft hole, so that inhale the lubricating oil between pivot and the second bearing, and the position department pressure that the thrust lubrication groove kept away from the shaft hole is higher, then can flow into the lubricating oil in the thrust lubrication groove along the inclined thrust wall in the terminal surface clearance between second bearing and the pump portion better, thereby can strengthen the lubrication between pump portion and the second bearing, make the lubricated state between the two pass through fluid lubrication by boundary lubrication, thereby effectively reduce the wear rate between the two.

Further, the at least two thrust walls further comprise a second thrust wall, the second thrust wall is opposite to the first thrust wall, the first end of the second thrust wall is connected with the inner side wall of the second bearing, the tangent plane of the connection point of the second thrust wall and the inner side wall of the second bearing is a second reference plane, and the included angle beta 2 between the second thrust wall and the second reference plane is larger than 0 degree and smaller than 90 degrees.

In this embodiment, the at least two thrust walls further include a second thrust wall, a first end of the second thrust wall is a starting end of the second thrust wall, a second end of the second thrust wall is a terminating end of the second thrust wall, the second end is connected to an inner side wall of the second bearing, and the inner side wall of the second bearing is a side wall of a shaft hole of the second bearing. The tangent plane of the connection point of the first end and the second bearing is a second reference plane, and the included angle beta 2 between the second thrust wall and the second reference plane is greater than or equal to 0 degree and smaller than 90 degrees. The pivot is at high-speed rotatory in-process, and the pivot can be sheared its self and the lubricating oil in the second bearing fit clearance, and lubricating oil can be followed in the fit clearance and got into the thrust lubrication groove under the effect of shearing force omega in, and the lubricating oil that gets into the thrust lubrication groove this moment has certain speed and pressure. Because the second thrust wall deviates to the rotating direction of the rotating shaft, the lubricating oil in the thrust lubricating groove can be subjected to shaft shearing and surface shearing, so that negative pressure is formed at the position, close to the shaft hole, of the thrust lubricating groove, the lubricating oil between the rotating shaft and the second bearing is sucked, the pressure at the position, far away from the shaft hole, of the thrust lubricating groove is higher, and the lubricating oil in the thrust lubricating groove can better flow into the end face gap between the second bearing and the pump part along the inclined thrust wall. Therefore, the lubrication between the pump part and the second bearing can be enhanced, the lubrication state between the pump part and the second bearing is transited from boundary lubrication to fluid lubrication, and the wear rate between the pump part and the second bearing is effectively reduced.

Further, 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.

In this embodiment, 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. Namely, the thrust lubrication groove is formed by the first thrust wall, the second thrust wall and the third thrust wall together, so that the shape design of the thrust lubrication groove can be facilitated.

It is worth to 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 second bearing may be straight sections or curved sections.

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 second bearing is an arc segment. Because the position that the third thrust wall corresponds pushes away the position of keeping away from the shaft hole of lubrication groove till, and the lubricating oil pressure that corresponds this position in the lubrication groove of thrust is higher, through making the third thrust wall be the arc wall to can be convenient for the flow of the interior lubricating oil of lubrication groove of thrust, can be so that lubricating oil gets into "osculum" from "macrostoma", the lubrication between reinforcing pump portion and the second bearing, make the lubricated state between the two transition to fluid lubrication by boundary lubrication, thereby effectively reduce the wear rate between the two.

In any of the above technical solutions, the casing further includes a casing and a pump cover, the casing is enclosed outside the motor portion and the pump portion, and the casing is connected to the first bearing. The pump cover is connected to the casing, the pump cover and the casing form a cavity, the pump cover is connected with the second bearing, one part of the pump cover deviates from the pump part and extends to form an extending part, and the extending part is used for forming an oil pool; the shaft hole of second bearing is the axial through-hole, and the one end and the thrust lubrication groove intercommunication of through-hole, the other end of through-hole are used for communicateing the oil bath.

In the technical scheme, the shell comprises a shell and a pump cover connected to the shell, the pump cover and the shell form a cavity, and the shell is arranged around the outer sides of the motor part and the pump part. The casing is connected with the first bearing, and the pump cover is connected with the second bearing. First bearing and casing can be integrated into one piece, and casing and first bearing integrated into one piece, and compared in the mode of post-processing, joint strength is higher, can also save space, reduces the complete machine height, can reduce the degree of difficulty of preparation technology moreover, reduces the cost of manufacture. The pump cover and the second bearing can be integrally formed, more height space is saved, the height of the whole machine can be reduced, and the cost can be reduced.

Further, the extension portion is formed by a part of the pump cover extending away from the pump portion, so that the extension portion and the pump cover are integrally formed, and compared with a post-processing mode, the connection strength is high. The extension is used to form an oil sump that is capable of storing lubricating oil. The shaft hole on the second bearing is a through hole which axially penetrates through, and two ends of the through hole are respectively communicated with the thrust lubrication groove and the oil pool.

Specifically, the pivot is at high-speed rotatory in-process, and the pivot can be sheared its self and the lubricating oil in the second bearing fit clearance, and lubricating oil can follow fit clearance (through-hole) under the effect of shearing force and get into the thrust lubrication groove in, and the lubricating oil that gets into in the thrust lubrication groove this moment has certain speed and pressure. The lubricating oil in the thrust lubrication groove can be subjected to shaft shearing and surface shearing, so that negative pressure is formed at the position, close to the shaft hole, of the thrust lubrication groove, the lubricating oil between the rotating shaft and the second bearing is sucked, the pressure at the position, far away from the shaft hole, of the thrust lubrication groove is higher, and the lubricating oil in the thrust lubrication groove can be pushed into the end face gap between the second bearing and the pump part better. Therefore, the lubrication between the pump part and the second bearing can be enhanced, the lubrication state between the pump part and the second bearing is transited from boundary lubrication to fluid lubrication, and the wear rate between the pump part and the second bearing is effectively reduced.

Further, oil is drawn into the thrust lubrication grooves to lubricate the interface between the pump section and the second bearing, then into the gap between the second bearing and the pump section, and then into the low pressure region sump under the action of pressure differential and gravity.

Specifically, the lubricating oil path of the second bearing is as follows: oil enters a gap between the second bearing and the rotating shaft (the through hole and the second lubricating groove) through the oil pool and then enters the thrust lubricating groove, and under the action of the thrust lubricating groove, the oil enters a gap between the pump part and the end face of the second bearing and enters the low-pressure oil pool under the action of pressure difference and gravity. And a finished lubricating oil path is formed for the second bearing, so that the lubricating performance between the second bearing and the rotating shaft is ensured.

Furthermore, the pump cover and the second bearing are integrally formed, so that compared with a post-processing mode, the connecting strength is higher, the space can be saved, the height of the whole machine is reduced, the difficulty of the preparation process can be reduced, and the manufacturing cost is reduced.

In any of the above technical solutions, the casing further includes a casing and a pump cover, the casing is enclosed outside the motor portion and the pump portion, and the casing is connected to the first bearing. The pump cover is connected to the shell, the pump cover and the shell form a cavity, and the pump cover is connected with the second bearing; the shaft hole of the second bearing is a blind hole with one end opened. The communicating groove is formed in the second bearing and/or the pump cover and communicated with the first pressure cavity and the blind hole.

Furthermore, the shaft hole of the second bearing is a blind hole with one end opened, the communicating groove is formed in the second bearing and/or the pump cover, and the communicating groove is used for communicating the first pressure cavity and the blind hole. Specifically, the lubricating oil path of the second bearing is as follows: the pressurized oil enters the blind hole (a gap between the second bearing and the rotating shaft and a second lubricating groove) from the first pressure cavity (a high pressure cavity) through the communicating groove and then returns to a low pressure area through the gap between the second bearing and the pump part, wherein the low pressure area specifically refers to the oil inlet and the second pressure cavity. And a finished lubricating oil path is formed for the second bearing, so that the lubricating performance between the second bearing and the rotating shaft is ensured.

In any of the above technical solutions, further, the pump portion includes a first rotating member and a second rotating member, and the first rotating member is engaged with the rotating shaft. The second rotates the piece setting in the outside of first rotation piece, and first rotation piece can drive the second rotation piece and rotate, and the first pressure chamber and second pressure chamber are constructed with first rotation piece to the second rotation piece. The pump device also comprises an oil inlet and an oil outlet, the oil inlet is axially arranged on the pump cover and/or the second bearing, and the oil inlet is communicated with the second pressure cavity; the oil outlet is radially arranged on the pump cover and the second bearing, and the oil outlet is communicated with the first pressure cavity of the pump part.

In this technical scheme, pump portion includes first rotation piece and second rotation piece, and first rotation piece cooperatees with the pivot, and the second rotation piece sets up in the outside of first rotation piece, and first rotation piece can drive the second rotation piece and rotate, can understand that the pivot can drive the second rotation piece operation through first rotation piece. The first pressure chamber and the second pressure chamber are formed by providing the first rotating member and the second rotating member, and the first pressure chamber is a high pressure chamber and the second pressure chamber is a low pressure chamber.

It should be noted that the first rotating member is an internal gear, the second rotating member is an external gear, and the pump portion is a gear pump. Specifically, in the gear pump meshing process, a front pair of teeth are not meshed yet, a rear pair of teeth are meshed, each inner tooth surface is in contact with an outer tooth surface to form a closed cavity, the volume of the closed cavity can be changed along with the rotation of an inner gear, and if an unloading channel cannot be communicated, an oil trapping volume can be formed. Because the compressibility of the liquid is very small, when the trapped oil volume is reduced from large to small, the liquid in the trapped oil volume is extruded, the pressure is increased sharply, and the working pressure of the gear pump is greatly exceeded. Meanwhile, liquid trapped in the oil volume is forcibly extruded from all gaps capable of being leaked, so that the rotating shaft and the bearing can bear large impact load, the power loss is increased, the oil is heated, noise and vibration are caused, the working stability of the gear pump is reduced, and the service life of the gear pump is prolonged. When the trapped oil volume is changed from small to large, vacuum is formed, so that air dissolved in liquid is separated out to generate bubbles, and the harm of cavitation, noise, vibration, flow, pressure pulsation and the like is brought. The method for eliminating the oil trapping phenomenon is characterized in 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 through the unloading grooves when the closed volume is increased.

Specifically, the inner gear is meshed with the tooth profile of the conjugate curve of the outer gear, and each tooth is contacted with each other to drive the outer gear to rotate in the same direction. The inner gear divides the inner cavity of the outer 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 centers of the inner gear and the outer gear, a certain vacuum is formed in an area with increased volume, the oil inlet is arranged at the position, the pressure of the area with decreased volume is increased, and the oil outlet is correspondingly arranged at the position.

Furthermore, the pump device also comprises an oil inlet and an oil outlet, wherein the oil inlet is axially arranged on the pump cover and/or the second bearing, and the oil inlet is communicated with the second pressure cavity. Because the second pressure chamber is the low pressure chamber, and there is the pressure differential with the chamber outsidely, consequently fluid can enter into the second pressure intracavity through the oil inlet. The oil outlet is radially arranged on the pump cover and the second bearing, and the oil outlet is communicated with the first pressure cavity. Because first pressure chamber is the high-pressure chamber, and there is the pressure differential with the chamber outsidely, consequently the fluid of first pressure intracavity can flow out through the oil-out. Namely, the main oil passage of the pump device is: negative pressure that second pressure chamber and oil inlet department can produce under the effect of negative pressure, the fluid in the oil bath is attracted to the oil inlet, and then gets into second pressure chamber (low-pressure chamber), and the fluid that gets into the second pressure chamber gets into the high-pressure chamber pressurization under the effect of first rotation piece and second rotation piece, and the fluid after the pressurization is discharged through the oil-out.

It is worth to state that, regarding the design principle of oil inlet and oil outlet: in the process of ensuring the rotation of the gear, the oil inlet is communicated with the tooth spaces of the first rotating part and the second rotating part as early as possible, before the internal gear and the external gear form the maximum volume, the gear volume cavity is always communicated with the oil inlet, and the oil filling time is prolonged as far as possible, so that the volume cavity between the internal gear and the external gear is filled with oil, and the oil absorption is ensured. The oil outlet is communicated with high-pressure oil between the teeth as early as possible to reduce the compression work between the teeth, and is closed as late as possible to fully utilize the inertia of fluid to exhaust the oil between the teeth, so that the volume efficiency of the internal gear type oil pump is improved. However, it should be noted that the inner and outer gears cannot be communicated with the oil inlet when forming the maximum volume, thereby avoiding affecting the volumetric efficiency of the pump device at low speed.

In any of the above technical solutions, further, the motor part further includes a rotor and a stator, the rotor is connected with the rotating shaft; the stator sleeve is arranged on the outer side of the rotor, the stator comprises a stator core and a stator winding, and the stator winding is arranged on the stator core. The pump device further comprises a control part, the control part is arranged on one side, away from the pump part, of the motor part, the control part is connected to the shell and located in the cavity, and the end part of the stator winding is electrically connected with the control part.

In this technical solution, the motor part further includes a rotor and a stator. Wherein, rotor and pivot link to each other, can ground, and rotor and pivot can coaxial setting, and the cooperation mode of rotor and pivot can be interference fit, can also ground, but rotor and pivot disalignment set up but both transmission are connected, carry out nimble setting according to actual conditions. The stator sleeve is arranged on the outer side of the rotor, the stator comprises a stator core and a stator winding, and the stator winding is arranged on the stator core.

In addition, pump unit still includes control part, and control part sets up the one side that deviates from pump portion at motor part, and control part setting is kept away from the position of pump portion at motor part promptly, because the position vibration that is close to pump portion in the course of the work is comparatively obvious, and the load that receives is great, therefore control part keeps away from pump portion, can play the effect of protection to control part to a certain extent, improves control part's life.

Further, the control part is connected to the shell and located in the cavity, and the end of the stator winding is electrically connected with the control part.

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, the rotor rotates under the action of the excitation magnetic field, the first rotating part in the pump part is driven to rotate through the rotating shaft, and the second rotating part moves. When the first rotating member and the second rotating member in the pump portion rotate, due to the eccentric movement of the second rotating member, the volume of a compression chamber formed between the first rotating member and the second rotating member changes, so that the working medium entering the compression chamber is pressed out to the oil outlet to generate flowing power.

An embodiment of a second aspect of the invention provides a vehicle comprising: the pump apparatus of any of the above embodiments.

An embodiment of the vehicle according to the invention, which comprises the pump device, further the vehicle may be a special vehicle, and the vehicle has all the advantages of the pump device.

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.

In the above technical solution, a vehicle includes: a vehicle body in which the pump device is disposed; and the engine is arranged in the vehicle body and comprises a mounting seat, and the mounting seat is connected with the extension part of the pump device.

In this technical solution, a vehicle includes a vehicle body and an engine. The pump device and the engine are both arranged in the vehicle body, the engine comprises a mounting seat, and the mounting seat is connected with the extension part of the pump device, so that the engine and the pump device can be connected through the matching of the mounting seat and the extension part.

The vehicle includes any one of the pump devices in the first aspect, so that the beneficial effects of any one of the embodiments are achieved, and are not described herein again.

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

Drawings

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

FIG. 2 shows an enlarged partial view at A of the pump apparatus shown in FIG. 1 according to one embodiment of the present invention;

FIG. 3 illustrates a schematic partial structural view of a pump apparatus according to an embodiment of the present invention;

FIG. 4 shows a schematic structural diagram of a pump device according to another embodiment of the present invention;

FIG. 5 shows a schematic diagram of a pump cap and a second bearing of a pump device according to an embodiment of the invention;

fig. 6 shows a schematic structural diagram of a vehicle according to an embodiment of the present invention.

Wherein, the correspondence between the reference numbers and the part names in fig. 1 to 6 is:

100 of the pump means,

110 shell, 111 cavity, 112 shell, 113 pump cover, 114 extension part, 115 oil pool,

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

130 pump section, 131 first pressure chamber, 132 second pressure chamber, 133 first rotating member, 134 second rotating member,

140 first bearing, 141 first oil groove, 142 throttling groove, 143 first lubrication groove, 144 relief groove,

150, 151, through the liquid chamber,

160 buffer chamber, 161 first wall, 162 second wall,

170 second bearing, 171 second lubrication groove, 172 thrust lubrication groove,

an oil inlet 181, an oil outlet 182,

190 a control part for controlling the operation of the motor,

200 of the vehicles are driven by the motor vehicle,

210 of the vehicle body, and a vehicle body,

220 motor, 221 mounting seat.

Detailed Description

In order that the above objects, features and advantages of the embodiments of the present invention can be more clearly understood, embodiments of the present invention will be described in further detail below with reference to the accompanying drawings and detailed description. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.

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

A pump apparatus 100 and a vehicle 200 provided according to some embodiments of the present invention are described below with reference to fig. 1 to 6.

Example one

An embodiment of the first aspect of the present invention provides a pump apparatus 100, as shown in fig. 1, 2 and 3, including a housing 110, a motor portion 120, a pump portion 130, a first bearing 140, a first oil groove 141, and a throttle groove 142. Wherein, the housing 110 has a cavity 111. The motor part 120 includes a rotation shaft 121 rotating around a central axis of the motor part 120. The pump portion 130 is disposed at one axial side of the motor portion 120 and contacts the rotating shaft 121, and the pump portion 130 can be driven by the rotating shaft 121 to rotate. The pump section 130 includes a first pressure chamber 131 and a second pressure chamber 132, and the first pressure chamber 131 receives a pressure greater than the second pressure chamber 132. The first bearing 140 is connected to the housing 110 and sleeved on the rotating shaft 121, and the first bearing 140 is located between the motor part 120 and the pump part 130. A first oil groove 141 is provided on a first end surface of the first bearing 140 toward the pump portion 130, the first oil groove 141 communicating with the first pressure chamber 131. A throttle groove 142 is provided on the first end surface, and the throttle groove 142 communicates the first oil groove 141 and the gap between the first bearing 140 and the rotating shaft 121.

According to an embodiment of the pump apparatus 100 provided by the present invention, the pump apparatus 100 includes a housing 110, a motor portion 120, a pump portion 130, a first bearing 140, a first oil groove 141, and a throttle groove 142. The casing 110 has a cavity 111, and the motor part 120 and the pump part 130 are disposed in the cavity 111, so that the casing 110 ensures that the motor part 120 and the pump part 130 are not affected by the external environment and can normally operate. The motor part 120 includes a rotating shaft 121 rotating around a central axis of the motor part 120, the pump part 130 is disposed at one axial side of the motor part 120, and the pump part 130 is in contact with the rotating shaft 121, specifically, the pump part 130 is in interference fit with the rotating shaft 121, the pump part 130 can be driven by the rotating shaft 121 to rotate, and it can be understood that the motor part 120 drives the pump part 130 to operate through the rotating shaft 121. The pump portion 130 includes a first pressure chamber 131 and a second pressure chamber 132, the first pressure chamber 131 is subjected to a pressure greater than that of the second pressure chamber 132, and further, the first pressure chamber 131 may be a high pressure chamber, and the second pressure chamber 132 may be a low pressure chamber.

In addition, the first bearing 140 is connected to the housing 110, the first bearing 140 is located between the motor portion 120 and the pump portion 130, the first bearing 140 is sleeved on the rotating shaft 121, and the first bearing 140 can support the rotating shaft 121 to a certain extent. It should be noted that the first bearing 140 can provide lubrication support for the rotating shaft 121, and since the axes of the first bearing 140 and the rotating shaft 121 coincide, in an actual operation process, the rotating shaft 121 drives the pump portion 130 to rotate, so that the pump portion 130 can apply a force to the rotating shaft 121 in a radial direction, the rotating shaft 121 can push the first bearing 140 to deflect towards one side while receiving the radial force, at this time, the rotating shaft 121 contacts with the first bearing 140, and the first bearing 140 can provide a support effect for the rotating shaft 121, so that a play of the rotating shaft 121 can be controlled within a reasonable range, and thus, control of the axis of the rotating shaft 121 is facilitated.

It should be noted that the first bearing 140 is a sliding bearing, and the sliding bearing refers to a bearing operating under sliding friction. Compared with the rolling bearing, the sliding bearing has stable and reliable operation and no noise, the sliding surface is separated by the lubricating oil and does not directly contact under the condition of liquid lubrication, the friction loss and the 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 to realize fluid lubrication, the oil film also has certain vibration absorption capacity, and the service life of the first bearing 140 and the rotating shaft 121 is prolonged.

Further, as shown in fig. 3, the first oil groove 141 is disposed on a first end surface of the first bearing 140 facing the pump portion 130, the first oil groove 141 is communicated with the first pressure chamber 131, and due to a relatively large pressure in the first pressure chamber 131, a part of the oil flows from the first pressure chamber 131 to the first oil groove 141, and then flows into a gap between the rotating shaft 121 and the first bearing 140, so as to ensure the lubricating performance between the first bearing 140 and the rotating shaft 121.

Further, as shown in fig. 3, a throttle groove 142 is provided on the first end surface, that is, the throttle groove 142 is provided on the first end surface of the first bearing 140 facing the pump section 130, and the throttle groove 142 is used to communicate the first oil groove 141 and the gap between the first bearing 140 and the rotating shaft 121. That is, the oil in the first pressure chamber 131 flows to the first oil groove 141 first, and then flows to the gap between the first bearing 140 and the rotating shaft 121 through the throttling groove 142, and the throttling groove 142 can effectively prevent the excessive oil from flowing into the gap between the first bearing 140 and the rotating shaft 121, thereby affecting the displacement of the pump device 100.

Therefore, in order to ensure the fluid lubrication performance between the first bearing 140 and the rotating shaft 121, that is, to provide sufficient lubricating oil to the gap between the first bearing 140 and the rotating shaft 121, and to ensure that the displacement of the pump section 130 does not leak seriously, that is, the displacement of the pump section 130 is not significantly affected by the oil used for lubrication, the first oil groove 141 and the throttle groove 142 are used in cooperation, so that the lubrication requirement between the first bearing 140 and the rotating shaft 121 can be met, and the displacement of the pump device 100 is not reduced due to the excessive flow in the first bearing 140.

Specifically, the first oil groove 141 may balance pressure between the respective pockets in the high pressure side of the pump portion 130 such that the high pressure side pockets are at a similar pressure, thereby reducing noise and mechanical vibration during operation.

Further, as shown in fig. 3, the flow cross-sectional area of the throttle groove 142 is smaller than the flow cross-sectional area of the first oil groove 141, so that the flow rate of the lubricating oil in the gap between the first bearing 140 and the rotating shaft 121 can be controlled by the throttle groove 142.

Further, as shown in fig. 1 to 3, a portion of the inner side wall of the first bearing 140 is recessed away from the rotating shaft 121 to form a first lubrication groove 143, and the first lubrication groove 143 communicates with the throttle groove 142.

In this embodiment, the first lubrication groove 143 is formed by a portion of the inner side wall of the first bearing 140 recessed away from the rotating shaft 121, the first lubrication groove 143 communicating with the throttle groove 142. Due to the pressure difference, the oil in the first pressure chamber 131 sequentially passes through the first oil groove 141 and the throttling groove 142 and then flows into the gap between the first bearing 140 and the rotating shaft 121, and meanwhile, the oil can be filled in the first lubricating groove 143, and along with the rotation of the rotating shaft 121, the oil in the first lubricating groove 143 can be coated on the surface of the rotating shaft 121, and here, the first lubricating groove 143 plays a role of temporarily storing the lubricating oil, so that a fluid lubricating oil film can be formed between the inner wall of the first bearing 140 and the rotating shaft 121, and the reliable lubricating property between the rotating shaft 121 and the bearing is further ensured. Further, a first lubrication groove 143 is provided to penetrate the first bearing 140 in the axial direction, the first lubrication groove 143 communicates with the shaft hole of the first bearing 140, one end of the first lubrication groove 143 communicates with the throttle groove 142, and the other end of the first lubrication groove 143 extends in the direction of the motor chamber. Further, the number of the first lubrication grooves 143 is at least one, and the number may be flexibly set according to actual lubrication requirements.

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

In this embodiment, the flow cross-sectional area of the throttle groove 142 is controlled to be 0.1 ≦ (S1/S2) ≦ 0.4, and the flow cross-sectional area of the throttle groove 142 is not excessively large, so that it is ensured that the oil on the high pressure side in the pump section 130 does not leak excessively to affect the normal compression of the pump section 130, that is, the oil does not excessively flow into the first lubrication groove 143 through the throttle groove 142, and does not significantly affect the displacement of the pump section 130. By limiting the cross-sectional flow area of the first lubrication groove 143, the cross-sectional flow area of the first lubrication groove 143 is not too small, so that a sufficient flow of the lubricating oil can be ensured to form an oil film between the first bearing 140 and the rotating shaft 121, and the requirement of fluid lubrication can be met.

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

In this embodiment, 0.02 ≦ (S2/S0 ≦ 0.08), the flow cross-sectional area of the first lubrication groove 143 is defined, and the flow cross-sectional area of the first lubrication groove 143 is not too small, so that a sufficient flow rate of the lubricating oil can be ensured to form an oil film between the first bearing 140 and the rotating shaft 121, and the fluid lubrication requirement can be satisfied. The cross-sectional area of the first lubrication groove 143 is not too large, which results in an excessively thick oil film formed between the first bearing 140 and the rotating shaft 121, and increases power consumption of the rotating shaft 121.

Further, the cross-sectional area of the shaft hole of the first bearing 140 is limited to be within a suitable range, which does not affect the oil entering into the gap between the rotating shaft 121 and the first bearing 140 because of being too small, and similarly, does not affect the strength of the first bearing 140 itself because of too large cross-sectional area of the shaft hole of the first bearing 140. Specifically, the shaft diameter of the first bearing 140 is 6mm or more and 12mm or less. According to the relationship graph of the shaft diameter of the first bearing 140 and the deformation of the first bearing 140 and the relationship graph of the shaft diameter of the first bearing 140 and the power consumption, the comparison shows that when the shaft diameter is smaller than 6mm, the deformation of the bearing is large, which is not beneficial to the support of the bearing on the rotating shaft 121; when the shaft diameter is larger than 12mm, the power consumption of the bearing is increased greatly, so that the shaft diameter of the first bearing 140 meets the range, the power consumption requirement of the bearing is met, and the bearing can be prevented from being deformed too much.

Further, as shown in fig. 1, fig. 2 and fig. 4, the pump device 100 further includes a sealing member 150 connected to a side of the first bearing 140 facing away from the pump portion 130, the sealing member 150 is sleeved on the rotating shaft 121, the sealing member 150, the first bearing 140 and the rotating shaft 121 form a fluid passing cavity 151, and the fluid passing cavity 151 is communicated with the first lubricating groove 143.

In this embodiment, the first bearing 140 is connected to the housing 110, and the first bearing 140 may divide the cavity 111 enclosed by the housing 110 into a motor cavity and a pump cavity, so that the spatial arrangement may be more reasonable. The motor portion 120 is located within the motor cavity and the pump portion 130 is located within the pump cavity. The sealing member 150 is connected to a side of the first bearing 140 away from the pump portion 130, and the sealing member 150 is sleeved on the rotating shaft 121. Specifically, the sealing member 150 can isolate the motor cavity from the pump cavity, so that the working medium cannot flow into the motor cavity, normal use of the parts such as the stator 123, the rotor 122 and the control part 190 in the motor cavity is not affected, and other structures are not required to be additionally arranged in the motor cavity to ensure that the parts in the motor cavity are corroded, so that the sealing performance of the pump device 100 is better, and meanwhile, the structure is simpler and is favorable for reducing the cost.

It should be noted that, as shown in fig. 1, fig. 2 and fig. 4, a portion of the first bearing 140 extends away from the pump portion 130 to form a mounting position, and since the mounting position and the first bearing 140 are of an integral structure, compared with a post-processing method, the mechanical property of the integral structure is better, so that the connection strength can be improved. In addition, the first bearings 140 may be mass-produced to improve the processing efficiency of the product, reduce the processing cost of the product, improve the integrity of the pump apparatus 100, reduce the number of parts, reduce the number of mounting processes, and improve the mounting efficiency. In addition, the installation position for installing the sealing member 150 is formed by a part of the first bearing 140, so that the installation accuracy of the sealing member 150 can be ensured, the assembly is simple, the sealing performance is good, and the cost is low.

Further, as shown in fig. 2, the seal 150, the first bearing 140, and the rotation shaft 121 form a liquid passing chamber 151, and the liquid passing chamber 151 communicates with the first lubrication groove 143. The liquid passing cavity 151 formed by the sealing element 150, the first bearing 140 and the rotating shaft 121 can store a part of lubricating oil, the liquid passing cavity 151 is used for storing the lubricating oil from the first lubricating groove 143, the liquid passing cavity 151 can play a role in buffering by controlling the connection strength of the sealing element 150 and the first bearing 140, namely the pressure which can be borne by the sealing element 150, so that the oil in the liquid passing cavity 151, the first lubricating groove 143 and the throttling groove 142 can be in a pressure balanced state, and the fluid lubricating performance of the rotating shaft 121 and the first bearing 140 can be favorably ensured on the premise of ensuring the position stability of the sealing element 150.

Further, as shown in fig. 1, 2, 3, and 4, the pump apparatus 100 further includes a pressure relief groove 144, the pressure relief groove 144 is provided on the first bearing 140, and the pressure relief groove 144 communicates the liquid passage chamber 151 and the second pressure chamber 132.

In this embodiment, a pressure relief groove 144 is provided on the first bearing 140, and the pressure relief groove 144 is used to connect through the fluid chamber 151 and the second pressure chamber 132. The pressure relief groove 144 may be in the form of a through hole, so that two ends of the through hole can communicate with the second pressure chamber 132 and the fluid passing chamber 151, and the pressure in the fluid passing chamber 151 can be better released due to the lower pressure in the second pressure chamber 132, and the pressure of the oil can be buffered by the fluid passing chamber 151 itself.

Further, by providing the pressure relief groove 144 on the first bearing 140, a complete lubrication oil path of the first bearing 140 can be formed, that is, the oil in the first pressure chamber 131 (high pressure chamber) enters the first oil groove 141, then flows into the gap between the first bearing 140 and the rotating shaft 121 and the first lubrication groove 143 through the throttling groove 142, fully lubricates the rotating shaft 121 and the first bearing 140 to form an oil film to meet the requirement of fluid lubrication, and then flows into the fluid passing chamber 151, and further flows into the second pressure chamber 132 (low pressure chamber) from the pressure relief groove 144, so that the pressure in the whole lubrication oil path can be ensured not to be too high, that is, the pressure in the fluid passing chamber 151 can not be too high, the pressure is prevented from being higher than the pressure limit value that the sealing element 150 can bear, the reliability of the position of the sealing element 150 is ensured, and the sealing element 150 can be effectively prevented from being separated from the first bearing 140 under high pressure, resulting in leakage of the lubricating oil and failure to ensure the sealing performance between the motor chamber and the pump chamber.

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

In this example, 1 ≦ (S3/S2). ltoreq.4. The flow cross-sectional area of the first lubricating groove 143 is limited, so that the flow cross-sectional area of the first lubricating groove 143 is not too small, and a sufficient flow rate of lubricating oil is ensured to form an oil film between the first bearing 140 and the rotating shaft 121, thereby meeting the requirement of fluid lubrication; meanwhile, the cross-sectional area of the first lubrication groove 143 is not too large, which results in an excessively thick oil film formed between the first bearing 140 and the rotating shaft 121 and increases the power consumption of the rotating shaft 121.

In addition, by limiting the flow area of the pressure relief groove 144, the pressure of the oil seal cavity is ensured not to be too high, the sealing effect of the oil seal is ensured, and the oil seal is prevented from being separated from the first bearing 140 due to the too high pressure in the excess liquid cavity 151. In consideration of the flow cross-sectional area of the throttling groove 142, the flow cross-sectional area of the first lubricating groove 143 and the flow cross-sectional area of the pressure relief groove 144, the three satisfy the relational expression, so that sufficient oil flow in the first lubricating groove 143 can be ensured to ensure the lubrication of the first bearing 140 and the rotating shaft 121, and meanwhile, the pressure in the liquid passing cavity 151 can be ensured to be low enough, the sealing connection between the sealing element 150 and the first bearing 140 cannot be influenced, and the oil leakage can be effectively reduced.

Determining the flow rate of the lubricating oil in the lubricating oil path of the first bearing 140 to be not less than 3ml/S according to simulation data, determining the shaft diameter of the first bearing 140 to be 8mm, and determining the through-flow cross-sectional area S2 of the first lubricating groove 143 to be 1.57mm after checking the strength of the bearing through simulation²Is the optimal choice. Then, the structure of the flow cross-sectional area S1 of the throttle groove 142 and the flow cross-sectional area S3 of the pressure relief groove 144 were designed differently to obtain the simulation data shown in the following table 1:

TABLE 1

Serial number	S1/mm²	S2/mm²	S3/mm²	Oil flow (ml/s) in the first lubrication groove 143	Pressure (kPa) in the liquid passing chamber 151
						1	2	1.57	3.14	14.4	214
2	1.1	1.57	3.14	9.3	122
						3	0.4	1.57	3.14	7.3	112
4	0.01	1.57	3.14	1.8	91.3
						5	0.4	1.57	1.57	5.9	159
6	0.4	1.57	6.28	9.1	108

From the simulation data in table 1, it can be determined that the solution in sequence number 3 is the optimal solution, i.e., the cross-sectional flow area S1 of the throttle groove 142Is 0.4mm²The cross-sectional flow area S2 of the first lubrication groove 143 is 1.57mm²The cross-sectional area S3 of the pressure relief groove 144 is 3.14mm²At this time, the oil flow in the first lubricating groove 143 is 7.3ml/s, which satisfies the lubricating requirement and does not reduce the displacement of the pump device 100 because the oil flow in the first bearing 140 is too large, and meanwhile, the pressure in the fluid passing cavity 151 is 112kPa, which is not too high, so that the serious leakage of the oil can be avoided.

Example two

In addition to the first embodiment, the present embodiment explains the specific structure of the first bearing 140, and as shown in fig. 2, the pump device 100 further includes a buffer chamber 160, and the buffer chamber 160 is disposed on an end surface of the first bearing 140 facing away from the pump portion 130.

In this embodiment, the buffer cavity 160 is disposed on an end surface of the first bearing 140 facing away from the pump portion 130, and specifically, the buffer cavity 160 may be tapered, that is, the buffer cavity 160 may be a tapered cavity, so that the buffer cavity 160 can reduce the rigidity of the first bearing 140, provide a flexible support for the rotating shaft 121, reduce a surface pressure on an axial end surface of the first bearing 140 facing away from the pump portion 130, and effectively improve the wear condition of the first bearing 140 and the rotating shaft 121.

Further, the opening area of the buffer chamber 160 is larger than the bottom wall area of the buffer chamber 160. The buffer cavity 160 includes a first wall 161, the first wall 161 is a wall close to the rotating shaft 121, and a distance between the first wall 161 and the rotating shaft 121 increases from an opening end of the buffer cavity 160 to a bottom wall of the buffer cavity 160, it can be understood that the first wall 161 is obliquely disposed and a position of the first wall 161 at the opening end of the buffer cavity 160 is closer to the rotating shaft 121, a distance between the first wall 161 and the rotating shaft 121 is smaller at the opening, and a distance between the first wall 161 and the rotating shaft 121 is larger at a position at the bottom of the cavity, so that a right-angle structure is not formed between the first wall 161 and a bottom of the groove body. Because the first bearing 140 is usually made of an aluminum alloy material, when the end of the first bearing 140 contacts the rotating shaft 121, the first bearing 140 is deformed, if the joint of the first wall 161 and the bottom wall of the tapered cavity is in a right-angle structure, stress concentration may occur at the joint of the first wall 161 and the bottom wall of the groove body, and when the first bearing 140 is pressed by the rotating shaft 121, the first bearing 140 is easily broken at the joint of the first wall 161 and the bottom wall of the buffer cavity 160. When the first wall 161 is inclined relative to the axial direction of the rotating shaft 121, the first wall 161 and the bottom wall of the buffer chamber 160 are not in a right-angle structure, so that the damage rate of the first bearing 140 can be effectively reduced.

Further, the buffer chamber 160 includes a second wall 162, the second wall 162 is disposed opposite to the first wall 161, and a distance between the second wall 162 and the rotation shaft 121 decreases from the opening end of the buffer chamber 160 to the bottom wall of the buffer chamber 160.

In this embodiment, the second wall 162 is disposed obliquely with respect to the axial direction of the rotating shaft 121, the second wall 162 is disposed opposite to the first wall 161, and the distance between the second wall 162 and the rotating shaft 121 decreases from the opening end of the buffer cavity 160 to the bottom wall of the buffer cavity 160, so that the second wall 162 and the first wall 161 may be disposed axisymmetrically with respect to the center line of the buffer cavity 160, that is, the buffer cavity 160 may be tapered regularly, thereby better providing a flexible support for the rotating shaft 121. It can be understood that, in the axial direction away from the motor part 120, the distance between the first wall 161 and the rotating shaft 121 increases, the gap between the second wall 162 and the rotating shaft 121 decreases, and the buffer cavity 160 is configured in an inverted cone shape, so that the inverted cone-shaped buffer cavity 160 facilitates the die drawing during the machining process of the buffer cavity 160.

Further, the buffer cavity 160 is configured as an annular structure, that is, the buffer cavity 160 is disposed in the circumferential direction of the first bearing 140, when the rotating shaft 121 rotates, the radial force applied to the first bearing 140 may change at any time, that is, the first bearing 140 may be applied with a plurality of radial forces that change in different directions, and no matter which direction the radial force applied to the first bearing 140 faces, the existence of the annular buffer cavity 160 enables the first bearing 140 to deform to some extent, so that the rotating shaft 121 and the first bearing 140 are flexibly connected, and the first bearing 140 plays a role in buffering the radial force of the rotating shaft 121, thereby avoiding the problem that the rotating shaft 121 and the first bearing 140 are rigidly connected to cause easy damage to the first bearing 140.

EXAMPLE III

On the basis of the foregoing embodiments, the present embodiment explains the supporting structure of the rotating shaft 121 in the pump device 100, and further, as shown in fig. 1, fig. 4 and fig. 5, the pump device 100 further includes a second bearing 170, the second bearing 170 is connected to the housing 110 and is sleeved on the rotating shaft 121, and the second bearing 170 is located on a side of the pump portion 130 away from the first bearing 140.

In this embodiment, the second bearing 170 is connected to the housing 110, the second bearing 170 is sleeved on the rotating shaft 121, the second bearing 170 is located on a side of the pump portion 130 away from the first bearing 140, that is, the first bearing 140 and the second bearing 170 are partially located on two sides of the pump portion 130 in the axial direction, and the first bearing 140 is closer to the motor portion 120 than the second bearing 170. The first bearing 140 and the second bearing 170 can support the rotating shaft 121, and through the cooperative use of the rotating shaft 121, the first bearing 140 and the second bearing 170, the load of the pump portion 130 can be shared by the rotating shaft 121, the first bearing 140 and the second bearing 170 in a balanced manner, so that the rotating shaft 121 is prevented from being damaged due to the load concentrated on the rotating shaft 121.

Specifically, the first bearing 140 and the second bearing 170 are sliding bearings. Compared with the form of a double rolling bearing, the sliding bearing has stable and reliable work and no noise, the sliding surface is separated by lubricating oil and is not in direct contact under the condition of liquid lubrication, the friction loss and the 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 to realize fluid lubrication, the oil film also has certain vibration absorption capacity, and the service life of the first bearing 140, the second bearing 170 and the rotating shaft 121 is 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 and the sliding bearing are matched for use, the embodiment only uses two sliding bearings, so that the supporting structure can be simplified, and the cost can be reduced.

Further, the first bearing 140 has a first bearing surface close to the rotation shaft 121, and the second bearing 170 has a second bearing surface close to the rotation shaft 121, and the axial height of the second bearing surface is smaller than or equal to the axial height of the first bearing surface, i.e., not greater than. When the first bearing 140 is equidistant from the pump section 130 and the second bearing 170 is equidistant from the pump section 130, the loads from the pump section 130 carried on the first bearing 140 and the second bearing 170 are equal. However, since the first bearing 140 is closer to the motor portion 120 than the second bearing 170, during the rotation of the rotor 122 in the motor portion 120, a radial force is generated between the stator 123 and the rotor 122, which also generates a load on the rotating shaft 121, and therefore, the first bearing 140 also needs to bear the load from the motor portion 120, and by making the second bearing surface less than or equal to the first bearing surface, 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 lowest level.

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

In this embodiment, the second lubrication groove 171 is formed by a portion of the inner side wall of the second bearing 170 recessed away from the rotary shaft 121, and the second lubrication groove 171 communicates with the first pressure chamber 131. Due to the pressure difference, the oil in the first pressure chamber 131 flows into the gap between the first bearing 140 and the rotating shaft 121 through the second lubrication groove 171, and along with the rotation of the rotating shaft 121, the oil in the second lubrication groove 171 is coated on the surface of the rotating shaft 121, where the second lubrication groove 171 can play a role of temporarily storing the lubricating oil, so that a fluid lubricating oil film can be formed between the inner wall of the second bearing 170 and the rotating shaft 121, and the lubricating performance between the rotating shaft 121 and the bearing is further ensured.

Example four

On the basis of the foregoing embodiment, the present embodiment explains the specific structure of the second bearing 170, and further, as shown in fig. 5, the pump device 100 further includes a thrust lubrication groove 172 provided on an end surface of the second bearing 170 near the pump portion 130, the thrust lubrication groove 172 communicating with the shaft hole of the second bearing 170.

In this embodiment, a thrust lubrication groove 172 is provided on an end surface of the second bearing 170 near the pump portion 130, and the thrust lubrication groove 172 communicates with the shaft hole of the second bearing 170. The rotating shaft 121 shears the lubricating oil in the fit clearance with the second bearing 170 when rotating at a high speed, and the lubricating oil enters the thrust lubrication groove 172 through the oil groove of the second bearing 170 under the action of the shearing force to form a certain speed and pressure. Relative motion exists between the end face of the internal gear and the end face of the pump cover 113, and lubricating oil in the thrust lubricating groove 172 can form an oil film, so that a fluid lubricating condition is formed between the end face of the internal gear and the contact surface of the end face of the pump cover 113, the lubricating gear reduces noise, a thrust force can be formed on the gear, and the power consumption and abrasion of the thrust surface, namely the sliding surface between the internal gear and the pump cover 113, can be greatly improved.

Specifically, a thrust lubrication groove 172 is provided on an end face of the second bearing 170 near the pump portion 130, the thrust lubrication groove 172 communicating with the second bearing 170 and the shaft hole of the second bearing 170. Lubricating oil is arranged in a fit clearance between the second bearing 170 and the rotating shaft 121, the rotating shaft 121 can shear the lubricating oil in the fit clearance between the rotating shaft 121 and the second bearing 170 in the high-speed rotating process, the lubricating oil can enter the thrust lubrication groove 172 from the fit clearance under the action of a shearing force omega, and the lubricating oil entering the thrust lubrication groove 172 has certain speed and pressure. The end-face clearance in which the second bearing 170 and the pump portion 130 contact is small, and the lubricating oil in the thrust lubricating groove 172 can flow toward the end-face clearance of the second bearing 170 and the pump portion 130. Meanwhile, because there is relative motion between the pump portion 130 and the second bearing 170, a condition of fluid lubrication is formed between the contact end surfaces of the pump portion 130 and the second bearing 170, that is, an oil film is formed at the contact end surfaces of the second bearing 170 and the pump portion 130, so that transition from boundary lubrication to fluid lubrication is performed between the second bearing 170 and the pump portion 130, thereby greatly improving the wear condition of the contact end surfaces of the pump portion 130 and the second bearing 170, reducing power consumption, and further reducing the operation noise of the pump device 100.

Further, the notch area of the thrust lubrication groove 172 in the axial direction is larger than the groove area of the thrust lubrication groove 172.

In this embodiment, thrust lubrication groove 172 includes two notches oriented differently, one toward pump portion 130 and one toward shaft 121. The design defines a slot area towards the pump section 130 that is larger than the slot floor area. That is, in the axial direction away from the pump portion 130, i.e., in the top-down direction, the thrust lubrication groove 172 is in a throat shape. That is, the groove wall of the thrust lubrication groove 172 is inclined, at this time, on one hand, since the lubricant entering the thrust lubrication groove 172 has a certain speed and pressure, and on the other hand, since the gap between the end face where the second bearing 170 and the pump portion 130 are in contact is small, the groove wall of the thrust lubrication groove 172 is inclined, so that a convergent wedge-shaped included angle is formed between the thrust lubrication groove 172 and the end face gap, the lubricant in the thrust lubrication groove 172 flows into the end face gap between the pump portion 130 and the second bearing 170 along the inclined groove wall, that is, the lubricant enters a "small opening" from a "large opening", it is worth to be noted that the "large opening" refers to the thrust lubrication groove 172, and the "small opening" refers to the gap between the second bearing 170 and the pump portion 130. Lubrication between pump portion 130 and second bearing 170 may thereby be enhanced such that the lubrication state therebetween transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the rate of wear therebetween.

In addition, during high-speed rotation of the rotating shaft 121 and the pump section 130, the oil film between the contact surfaces of the pump section 130 and the second bearing 170 generates a force that pushes the pump section 130 upward, so that the lubricating oil in the end surfaces of the second bearing 170 and the pump section 130 functions as a floating seal, and thus the end surface leakage can be further reduced. It is shown in the relevant literature that end face leakage from the pump apparatus 100 accounts for 75% to 80% of the total leakage from the pump apparatus 100, and therefore, it is important to improve leakage between the respective contacting end faces in the pump apparatus 100. It is worth noting that the lubricating oil has a certain viscosity.

Further, the thrust lubrication groove 172 includes a thrust wall including at least one thrust segment including a first thrust segment extending near a center of the thrust lubrication groove 172 in an axial direction away from the pump portion 130.

In this embodiment, the thrust lubrication groove 172 includes a thrust wall, which is a sloped wall. The thrust wall extends near the center of the thrust lubrication groove 172 in an axial direction away from the pump portion 130, i.e., in a top-down direction. The thrust wall includes at least one thrust segment including a first thrust segment extending in an axial direction away from the pump portion 130, near a center of the thrust lubrication groove 172. At this time, the thrust lubrication groove 172, the end face gap formed between the end faces of the pump portion 130 and the second bearing 170, and a convergent wedge-shaped included angle formed between the two, the lubricant in the thrust lubrication groove 172 will flow into the end face gap between the pump portion 130 and the second bearing 170 along the inclined first thrust section, that is, the lubricant enters the small opening from the large opening. It should be noted that "large opening" refers to the thrust lubrication groove 172, and "small opening" refers to the clearance between the second bearing 170 and the pump portion 130. Lubrication between pump portion 130 and second bearing 170 may thereby be enhanced such that the lubrication state therebetween transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the rate of wear therebetween.

It should be noted that the first thrust segment may be formed of at least one straight segment and at least one curved segment, the first thrust segment 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 extends close to the center of the thrust lubrication groove 172, that is, the inclined extension trend of the first thrust segment satisfies the above relationship, i.e., the flow of the lubricating oil is facilitated. The first thrust section can be formed by a plurality of sections of curved surfaces or a plurality of sections of circular arcs.

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

In this embodiment, the axial end face of the second bearing 170 refers to the axial end face of the second bearing 170 close to the pump part 130, the included angle between the first thrust section and the axial end face is satisfied, and α is greater than 0 ° and less than 90 °, so that the first thrust section can better guide the lubricant into the end face gap between the second bearing 170 and the pump part 130, ensure that the lubricant can enter the end face gap through the speed and pressure of the lubricant itself and guided by the first thrust section, and form a convergent wedge-shaped included angle between the thrust lubrication groove 172 and the end face gap, so that the lubricant in the thrust lubrication groove 172 can flow into the end face gap between the pump part 130 and the second bearing 170 along the inclined groove wall, that is, the lubricant enters a small opening from the large opening. Lubrication between pump portion 130 and second bearing 170 may thereby be enhanced such that the lubrication state therebetween transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the rate of wear therebetween. Further, the angle α between the first thrust segment and the axial end face of the second bearing 170 is 45 °. It is noted that the inclined first thrust segment may be machined on the end face of the second bearing 170 adjacent the pump section 130 using a profiled cutting tool. Specifically, the thrust lubrication groove 172 may have an inverted triangular shape, a semicircular shape in a longitudinal section (in the axial direction), or the like.

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

In this embodiment, the at least one thrust segment further comprises a second thrust segment extending axially to connect the first thrust segment and the groove bottom, the second thrust segment cooperating with the first thrust segment to form a thrust wall to ensure that the volume of the thrust lubrication groove 172 meets the lubrication requirements. It should be noted that, in the machining process, a straight groove is machined on the end surface of the second bearing 170 facing the pump portion 130, and then the chamfer is machined, so that the first thrust segment and the second thrust segment can be formed, and the difficulty in machining the thrust lubrication groove 172 can be reduced by the above-mentioned machining sequence.

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

Further, the at least two thrust walls include a first thrust wall, a first end of the first thrust wall is connected with the inner side wall of the second bearing 170, a tangent plane where a connection point of the first thrust wall and the inner side wall of the second bearing 170 is located is a first reference plane, and an included angle β 1 between the first thrust wall and the first reference plane is greater than or equal to 0 degrees and smaller than 90 degrees.

In this embodiment, the first end of the first thrust wall is the start end of the first thrust wall, the second end of the first thrust wall is the stop end of the first thrust wall, the first end is connected to the inner sidewall of the second bearing 170, and the inner sidewall of the second bearing 170 is the sidewall of the shaft hole of the second bearing 170. The tangent plane of the connection point of the first end and the second bearing 170 is a first reference plane, and the included angle beta 1 between the first thrust wall and the first reference plane is greater than or equal to 0 degree and smaller than 90 degrees. During the high-speed rotation of the rotating shaft 121, the rotating shaft 121 shears the lubricating oil in the fit clearance between itself and the second bearing 170, the lubricating oil enters the thrust lubrication groove 172 from the fit clearance under the action of the shearing force ω, and the lubricating oil entering the thrust lubrication groove 172 has a certain speed and pressure. Because the first thrust wall deviates to the direction of rotation of the rotating shaft 121, shaft shearing and surface shearing of the lubricating oil in the thrust lubrication groove 172 occur, so that negative pressure is formed at the position of the thrust lubrication groove 172 close to the shaft hole to suck the lubricating oil between the rotating shaft 121 and the second bearing 170, and the pressure of the position of the thrust lubrication groove 172 far from the shaft hole is higher, so that the lubricating oil in the thrust lubrication groove 172 can better flow into the end-face gap between the second bearing 170 and the pump part 130 along the inclined thrust wall, so that the lubrication between the pump part 130 and the second bearing 170 can be enhanced, the lubrication state between the two is transited from boundary lubrication to fluid lubrication, and the wear rate between the two is effectively reduced.

Further, the at least two thrust walls further include a second thrust wall, 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 second bearing 170, the tangent plane of the connection point of the second thrust wall and the inner side wall of the second bearing 170 is a second reference plane, and the included angle β 2 between the second thrust wall and the second reference plane is greater than 0 degree and smaller than 90 degrees.

In this embodiment, the at least two thrust walls further include a second thrust wall, a first end of the second thrust wall is a start end of the second thrust wall, a second end of the second thrust wall is a stop end of the second thrust wall, the second end is connected to an inner sidewall of the second bearing 170, and the inner sidewall of the second bearing 170 is a sidewall of the shaft hole of the second bearing 170. The tangent plane of the connection point of the first end and the second bearing 170 is a second reference plane, and the included angle beta 2 between the second thrust wall and the second reference plane is greater than or equal to 0 degree and smaller than 90 degrees. During the high-speed rotation of the rotating shaft 121, the rotating shaft 121 shears the lubricating oil in the fit clearance between itself and the second bearing 170, the lubricating oil enters the thrust lubrication groove 172 from the fit clearance under the action of the shearing force ω, and the lubricating oil entering the thrust lubrication groove 172 has a certain speed and pressure. Since the second thrust wall is biased toward the direction in which the rotary shaft 121 rotates, shaft shearing and surface shearing of the lubricant in the thrust lubrication groove 172 occur, so that negative pressure is generated at a position of the thrust lubrication groove 172 close to the shaft hole to suck the lubricant between the rotary shaft 121 and the second bearing 170, and the pressure is higher at a position of the thrust lubrication groove 172 far from the shaft hole, so that the lubricant in the thrust lubrication groove 172 can better flow into the end-face gap between the second bearing 170 and the pump part 130 along the inclined thrust wall. Lubrication between pump portion 130 and second bearing 170 may thereby be enhanced such that the lubrication state therebetween transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the rate of wear therebetween.

In this embodiment, 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. That is, the thrust lubrication groove 172 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 172 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 second bearing 170 may be straight sections or curved sections.

Further, the third thrust wall of the thrust lubrication groove 172 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 on the axial end face of the second bearing 170 is an arc segment. Because the position that the third thrust wall corresponds is the position of keeping away from the shaft hole of thrust lubrication groove 172, the lubricating oil pressure that corresponds this position in thrust lubrication groove 172 is higher, through making the third thrust wall be the arc wall to can be convenient for the flow of lubricating oil in thrust lubrication groove 172, can be so that lubricating oil gets into "osculum" from "macrostoma", the lubrication between reinforcing pump portion 130 and second bearing 170 for the lubricated state between the two passes through fluid lubrication by boundary lubrication, thereby effectively reduce the wear rate between the two.

EXAMPLE five

On the basis of the foregoing embodiment, the present embodiment explains a lubricating oil path of the second bearing 170, and further, as shown in fig. 4, the casing 110 includes a casing 112 and a pump cover 113, the casing 112 is enclosed outside the motor portion 120 and the pump portion 130, and the casing 112 is connected to the first bearing 140. A pump cover 113 is connected to the casing 112, the pump cover 113 and the casing 112 form a cavity 111, the pump cover 113 is connected to the second bearing 170, a part of the pump cover 113 extends away from the pump portion 130 to form an extension portion 114, and the extension portion 114 is used for forming an oil pool 115; the shaft hole of the second bearing 170 is a through hole which axially penetrates, one end of the through hole is communicated with the thrust lubrication groove 172, and the other end of the through hole is used for communicating the oil sump 115.

In this embodiment, the casing 110 includes a casing 112 and a pump cover 113 connected to the casing 112, the pump cover 113 and the casing 112 form a cavity 111, and the casing 112 is enclosed outside the motor portion 120 and the pump portion 130. The casing 112 is connected to the first bearing 140, and the pump cover 113 is connected to the second bearing 170. First bearing 140 and casing 112 can be integrated into one piece, and casing 112 and first bearing 140 integrated into one piece, compare in the mode of post-processing, and joint strength is higher, can also save space, reduces the complete machine height, can reduce the degree of difficulty of preparation technology moreover, reduces the cost of manufacture. The pump cover 113 and the second bearing 170 may be integrally formed, so that more height space is saved, the height of the whole machine can be reduced, and the cost can be reduced.

Further, the extension portion 114 is formed by a structure in which a portion of the pump cover 113 extends away from the pump portion 130, and thus, the extension portion 114 and the pump cover 113 are integrally formed, and the connection strength is high compared to a post-processing manner. The extension 114 serves to form an oil sump 115, and the oil sump 115 can store lubricating oil. The shaft hole of the second bearing 170 is a through hole passing through in the axial direction, and two ends of the through hole are respectively communicated with the thrust lubrication groove 172 and the oil sump 115.

Specifically, during the high-speed rotation of the rotating shaft 121, the rotating shaft 121 shears the lubricant oil in the fit clearance between itself and the second bearing 170, the lubricant oil enters the thrust lubrication groove 172 from the fit clearance (through hole) under the action of the shearing force, and the lubricant oil entering the thrust lubrication groove 172 has a certain speed and pressure. The lubrication oil in thrust lubrication groove 172 undergoes shaft shearing and surface shearing, so that a negative pressure is formed at a position where thrust lubrication groove 172 is close to the shaft hole to suck the lubrication oil between rotating shaft 121 and second bearing 170, and the pressure is higher at a position where thrust lubrication groove 172 is far from the shaft hole, so that the lubrication oil in thrust lubrication groove 172 can be better pushed into the end-face gap between second bearing 170 and pump portion 130. Lubrication between pump portion 130 and second bearing 170 may thereby be enhanced such that the lubrication state therebetween transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the rate of wear therebetween.

Further, oil is drawn into thrust lubrication groove 172 to lubricate the interface between pump section 130 and second bearing 170, then into the gap between second bearing 170 and pump section 130, and then into low pressure region sump 115 under the action of pressure differential and gravity.

Specifically, the lubricating oil path of the second bearing 170 is: the oil enters the gap between the second bearing 170 and the rotating shaft 121 (through hole, second lubrication groove 171) through the oil sump 115 and then enters the thrust lubrication groove 172, and under the action of the thrust lubrication groove 172, the oil enters the end face gap between the pump portion 130 and the second bearing 170 and enters the low-pressure oil sump 115 under the action of pressure difference and gravity. By forming a completed lubrication oil path for the second bearing 170, it is advantageous to ensure lubrication performance between the second bearing 170 and the rotating shaft 121.

Further, the pump cover 113 and the second bearing 170 are integrally formed, so that compared with a post-processing mode, the connection strength is higher, the space can be saved, the height of the whole machine can be reduced, the difficulty of the preparation process can be reduced, and the manufacturing cost can be reduced.

EXAMPLE six

On the basis of the foregoing embodiment, the present embodiment explains another lubrication oil path of the second bearing 170, and further, as shown in fig. 1, the casing 110 includes a casing 112 and a pump cover 113, the casing 112 is enclosed outside the motor portion 120 and the pump portion 130, and the casing 112 is connected to the first bearing 140. The pump cover 113 is connected to the casing 112, the pump cover 113 and the casing 112 form a cavity 111, and the pump cover 113 is connected to the second bearing 170; the shaft hole of the second bearing 170 is a blind hole with one end opened. The communication groove is formed in the second bearing 170 and/or the pump cover 113, and the communication groove communicates the first pressure chamber 131 with the blind hole.

Further, the shaft hole of the second bearing 170 is a blind hole with an open end, and a communication groove is formed in the second bearing 170 and/or the pump cover 113, and is used for communicating the first pressure chamber 131 with the blind hole. Specifically, the lubricating oil path of the second bearing 170 is: the pressurized oil enters the blind hole (the gap between the second bearing 170 and the rotating shaft 121, the second lubrication groove 171) from the first pressure chamber 131 (the high pressure chamber) through the communication groove, and then returns to the low pressure region through the gap between the second bearing 170 and the pump portion 130, wherein the low pressure region specifically refers to the oil inlet 181 and the second pressure chamber 132. By forming a completed lubrication oil path for the second bearing 170, it is advantageous to ensure lubrication performance between the second bearing 170 and the rotating shaft 121.

EXAMPLE seven

On the basis of the foregoing embodiments, the present embodiment explains the specific structure of the pump portion 130, and further, as shown in fig. 1 and 4, the pump portion 130 includes a first rotating member 133 and a second rotating member 134, and the first rotating member 133 is engaged with the rotating shaft 121. The second rotating member 134 is disposed outside the first rotating member 133, the first rotating member 133 can drive the second rotating member 134 to rotate, and the first and

second pressure chambers

131 and 132 are formed by the second rotating member 134 and the first rotating member 133. The pump device 100 further comprises an oil inlet 181 and an oil outlet 182, the oil inlet 181 is axially arranged on the pump cover 113 and/or the second bearing 170, and the oil inlet 181 is communicated with the second pressure cavity 132; an oil outlet 182 opens radially on the pump cover 113 and the second bearing 170, the oil outlet 182 communicating with the first pressure chamber 131 of the pump portion 130.

In this embodiment, the pump portion 130 includes a first rotating member 133 and a second rotating member 134, the first rotating member 133 is engaged with the rotating shaft 121, the second rotating member 134 is disposed outside the first rotating member 133, and the first rotating member 133 can drive the second rotating member 134 to rotate, it is understood that the rotating shaft 121 can drive the second rotating member 134 to rotate through the first rotating member 133. The first pressure chamber 131 and the second pressure chamber 132 are configured by providing the first rotating member 133 and the second rotating member 134, and the first pressure chamber 131 is a high pressure chamber and the second pressure chamber 132 is a low pressure chamber.

It should be noted that the first rotating member 133 is an internal gear, the second rotating member 134 is an external gear, and the pump portion 130 is a gear pump. Specifically, in the gear pump meshing process, the front pair of teeth are not meshed, the rear pair of teeth are meshed, each inner tooth surface is in contact with the outer tooth surface to form a closed cavity, the volume of the closed cavity 111 changes along with the rotation of an inner gear, and if the unloading channel cannot be communicated, an oil trapping volume is formed. Because the compressibility of the liquid is very small, when the trapped oil volume is reduced from large to small, the liquid in the trapped oil volume is extruded, the pressure is increased sharply, and the working pressure of the gear pump is greatly exceeded. Meanwhile, liquid trapped in the oil volume is forcibly extruded from all gaps capable of being leaked, so that the rotating shaft 121 and the bearing can bear large impact load, power loss is increased, oil is heated, noise and vibration are caused, and the working stability and the service life of the gear pump are reduced. When the trapped oil volume is changed from small to large, vacuum is formed, so that air dissolved in liquid is separated out to generate bubbles, and the harm of cavitation, noise, vibration, flow, pressure pulsation and the like is brought. The method for eliminating the oil trapping phenomenon is characterized in 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 through the unloading grooves when the closed volume is increased.

Specifically, the inner gear is meshed with the tooth profile of the conjugate curve of the outer gear, and each tooth is contacted with each other to drive the outer gear to rotate in the same direction. The inner gear divides the inner cavity of the outer gear into a plurality of working cavities, the volumes of the working cavities change along with the rotation of the rotor 122 due to the offset of the centers of the inner gear and the outer gear, a certain vacuum is formed in an area with the increased volume, the oil inlet 181 is arranged at the position, the pressure of the area with the decreased volume is increased, and the oil outlet 182 is correspondingly arranged at the position.

Further, the pump apparatus 100 further includes an oil inlet 181 and an oil outlet 182, the oil inlet 181 is axially opened on the pump cover 113 and/or the second bearing 170, and the oil inlet 181 is communicated with the second pressure chamber 132. Since the second pressure chamber 132 is a low pressure chamber and there is a pressure difference with the outside of the chamber, oil enters the second pressure chamber 132 through the oil inlet 181. An oil outlet 182 is opened in the radial direction on the pump cover 113 and the second bearing 170, and the oil outlet 182 communicates with the first pressure chamber 131. Since the first pressure chamber 131 is a high pressure chamber and there is a pressure difference with the outside of the chamber, the oil in the first pressure chamber 131 flows out through the oil outlet 182. That is, the main oil passages of the pump apparatus 100 are: the second pressure chamber 132 and the oil inlet 181 can generate negative pressure, under the action of the negative pressure, the oil in the oil pool 115 is attracted to the oil inlet 181, and then enters the second pressure chamber 132 (low pressure chamber), the oil entering the second pressure chamber 132 enters the high pressure chamber to be pressurized under the action of the first rotating member 133 and the second rotating member 134, and the pressurized oil is discharged through the oil outlet 182.

It is worth to be noted that, regarding the design principle of the oil inlet 181 and the oil outlet 182: in the process of ensuring the rotation of the gear, the oil inlet 181 is communicated with the teeth of the first rotating member 133 and the second rotating member 134 as early as possible, before the internal gear and the external gear form the maximum volume, the gear volume cavity is always communicated with the oil inlet 181, and the oil filling time is prolonged as far as possible, so that the volume cavity between the internal gear and the external gear is filled with oil, thereby ensuring the oil absorption. The oil outlet 182 is also communicated with the high-pressure oil between the teeth as early as possible to reduce the compression work between the teeth, and is closed as late as possible to fully utilize the inertia of the fluid to exhaust the oil between the teeth, thereby improving the volumetric efficiency of the internal gear type oil pump. However, it should be noted that the inner and outer gears cannot communicate with the oil inlet 181 when they form the maximum volume, thereby avoiding affecting the volumetric efficiency of the pump device 100 at low speed.

Example eight

On the basis of the foregoing embodiments, the present embodiment explains the specific structure of the motor part 120, and further, as shown in fig. 1 and fig. 4, the motor part 120 further includes a rotor 122 and a stator 123, the rotor 122 is connected to the rotating shaft 121; the stator 123 is sleeved outside the rotor 122, and the stator 123 includes a stator core and a stator winding, and the stator winding is disposed on the stator core. The pump device 100 further comprises a control part 190, the control part 190 is arranged on a side of the motor part 120 facing away from the pump part 130, the control part 190 is connected to the casing 110 and located in the cavity 111, and an end of the stator winding is electrically connected to the control part 190.

In this embodiment, the motor part 120 further includes a rotor 122 and a stator 123. Wherein, rotor 122 and pivot 121 link to each other, can ground, and rotor 122 and pivot 121 can coaxial setting, and the cooperation mode of rotor 122 and pivot 121 can be interference fit, and can also ground, rotor 122 and pivot 121 coaxial setting but both transmission are connected, carry out nimble setting according to actual conditions. The stator 123 is sleeved outside the rotor 122, and the stator 123 includes a stator core and a stator winding, and the stator winding is disposed on the stator core.

In addition, the pump device 100 further includes a control portion 190, 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 position close to the pump portion 130 vibrates significantly and receives a large load during operation, the control portion 190 is away from the pump portion 130, the control portion 190 can be protected to a certain extent, and the service life of the control portion 190 is prolonged.

Further, the control part 190 is connected to the housing 110 and located in the cavity 111, and the end of the stator winding is electrically connected to the control part 190.

Specifically, during the operation of the pump device 100, the control unit 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 changing excitation magnetic field, and the rotor 122 rotates under the action of the excitation magnetic field, so as to drive the first rotating member 133 in the pump portion 130 to rotate through the rotating shaft 121, and further to enable the second rotating member 134 to move. When the first rotating member 133 and the second rotating member 134 in the pump portion 130 rotate, due to the eccentric motion of the second rotating member 134, the volume of a compression chamber formed between the first rotating member 133 and the second rotating member 134 changes, so that the working medium entering the compression chamber is pressed out to the oil outlet 182 to generate flowing power.

Example nine

As shown in fig. 6, a second aspect embodiment of the present invention proposes a vehicle 200 including: the pump apparatus 100 according to any of the above embodiments. The vehicle 200 according to the present invention has the pump device 100 according to any of the embodiments described above, and further has the beneficial effects of any of the embodiments described above, which are not repeated herein.

It is worth mentioning that the vehicle 200 may be a new energy automobile. 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 also be a conventional fuel-powered vehicle.

In one particular embodiment, 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 extending portion 114 of the pump device 100, an oil pool 115 is formed through the matching of the mounting seat 221 and the extending portion 114, the oil pool 115 can be communicated with an oil source of the engine 220, and oil path communication is achieved.

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

In the present invention, the terms "first", "second", and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance; the term "plurality" means two or more unless expressly limited otherwise. The terms "mounted," "connected," "fixed," and the like are to be construed broadly, and for example, "connected" may be a fixed connection, a removable connection, or an integral connection; "coupled" may be direct or indirect through an intermediary. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the description of the present invention, it is to be understood that the terms "upper", "lower", "left", "right", "front", "rear", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the referred device or unit must have a specific direction, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present invention.

In the description herein, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means 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 invention. In this specification, the schematic representations of the terms used above 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 is only a preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes will occur to those skilled in the art. Any modification, equivalent replacement, or improvement 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;

a motor part including a rotating shaft rotating around a central axis of the motor part;

the pump part is arranged on one axial side of the motor part and is in contact with the rotating shaft, the pump part can be driven by the rotating shaft to rotate, the pump part comprises a first pressure cavity and a second pressure cavity, and the pressure borne by the first pressure cavity is greater than the pressure borne by the second pressure cavity;

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

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

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

2. Pump apparatus according to claim 1,

a portion of an inner sidewall of the first bearing is recessed away from the shaft to form a first lubrication groove that communicates with the throttle groove.

3. Pump apparatus according to claim 2,

the ratio of the cross-sectional flow area of the throttling groove to the cross-sectional flow area of the first lubricating groove is greater than or equal to 0.1 and less than or equal to 0.4.

4. Pump apparatus according to claim 2,

the ratio of the cross-sectional area of the first lubricating groove to the cross-sectional area of the shaft hole of the first bearing is greater than or equal to 0.02 and less than or equal to 0.08.

5. The pump apparatus of claim 2, further comprising:

the sealing member is connected first bearing deviates from one side of pump portion, the sealing member cover is established in the pivot, the sealing member first bearing with the pivot forms the liquid chamber, cross the liquid chamber with first lubrication groove intercommunication.

6. The pump apparatus of claim 5, further comprising:

and the pressure relief groove is arranged on the first bearing and is communicated with the liquid passing cavity and the second pressure cavity.

7. The pump arrangement according to claim 6,

the ratio of the cross-sectional flow area of the pressure relief groove to the cross-sectional flow area of the first lubrication groove is greater than or equal to 1 and less than or equal to 4.

8. The pump apparatus of claim 1, further comprising:

a buffer chamber arranged on an end face of the first bearing facing away from the pump portion.

9. The pump arrangement according to claim 8,

the opening area of the buffer cavity is larger than the bottom wall area of the buffer cavity.

10. The pump arrangement of claim 8, wherein the buffer chamber comprises:

the first wall surface is the wall surface that the buffer cavity is close to the pivot, certainly the open end of buffer cavity extremely the diapire of buffer cavity, first wall surface with the interval increase between the pivot.

11. The pump arrangement of claim 10, wherein the buffer chamber comprises:

the second wall surface is opposite to the first wall surface, and the distance between the second wall surface and the rotating shaft is reduced from the opening end of the buffer cavity to the bottom wall of the buffer cavity.

12. The pump arrangement according to any one of claims 1 to 11, further comprising:

the second bearing, the second bearing with the casing links to each other and the cover is established in the pivot, the second bearing is located the pump portion deviates from one side of first bearing.

13. The pump arrangement according to claim 12,

a portion of the inner sidewall of the second bearing is recessed away from the shaft to form a second lubrication groove that communicates with the first pressure chamber.

14. The pump apparatus of claim 12, further comprising:

and the thrust lubrication groove is arranged on the end face of the second bearing close to the pump part and communicated with the shaft hole of the second bearing.

15. The pump arrangement according to claim 14,

the housing includes:

the shell is arranged around the outer sides of the motor part and the pump part and connected with the first bearing;

the pump cover is connected to the shell, the cavity is formed by the pump cover and the shell, the pump cover is connected with the second bearing, one part of the pump cover extends away from the pump part to form an extension part, and the extension part is used for forming an oil pool;

the shaft hole of the second bearing is a through hole which penetrates through the shaft hole in the axial direction, one end of the through hole is communicated with the thrust lubrication groove, and the other end of the through hole is communicated with the oil pool.

16. The pump arrangement according to claim 13,

the housing includes:

the pump cover is connected to the shell, the pump cover and the shell form the cavity, and the pump cover is connected with the second bearing;

the shaft hole of the second bearing is a blind hole with one open end;

and the communicating groove is formed in the second bearing and/or the pump cover and is communicated with the first pressure cavity and the blind hole.

17. Pump arrangement according to claim 15 or 16,

the pump section includes:

the first rotating piece is matched with the rotating shaft;

the second rotating part is arranged on the outer side of the first rotating part, the first rotating part can drive the second rotating part to rotate, the second rotating part and the first rotating part construct the first pressure cavity and the second pressure cavity,

the pump device further includes:

the oil inlet is axially arranged on the pump cover and/or the second bearing and is communicated with the second pressure cavity;

and the oil outlet is radially arranged on the pump cover and the second bearing and is communicated with the first pressure cavity of the pump part.

18. Pump arrangement according to any one of claims 1 to 11,

the motor section further includes:

the rotor is connected with the rotating shaft;

the stator is sleeved on the outer side of 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:

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

19. A vehicle, characterized by comprising: a pump device according to any one of claims 1 to 18.