EP4056853A1 - Dispositif de pompe et véhicule - Google Patents

Dispositif de pompe et véhicule Download PDF

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Publication number
EP4056853A1
EP4056853A1 EP21863432.7A EP21863432A EP4056853A1 EP 4056853 A1 EP4056853 A1 EP 4056853A1 EP 21863432 A EP21863432 A EP 21863432A EP 4056853 A1 EP4056853 A1 EP 4056853A1
Authority
EP
European Patent Office
Prior art keywords
bearing
rotating shaft
pump
push
groove
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP21863432.7A
Other languages
German (de)
English (en)
Other versions
EP4056853A4 (fr
Inventor
Haoshuang HUA
Xiaojun Cao
Wei Fu
Xiao GE
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Guangdong Welling Auto Parts Co Ltd
Anhui Welling Auto Parts Co Ltd
Original Assignee
Guangdong Welling Auto Parts Co Ltd
Anhui Welling Auto Parts Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN202010913992.2A external-priority patent/CN114135384A/zh
Priority claimed from CN202021898979.6U external-priority patent/CN213743646U/zh
Application filed by Guangdong Welling Auto Parts Co Ltd, Anhui Welling Auto Parts Co Ltd filed Critical Guangdong Welling Auto Parts Co Ltd
Publication of EP4056853A1 publication Critical patent/EP4056853A1/fr
Publication of EP4056853A4 publication Critical patent/EP4056853A4/fr
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C15/0038—Shaft sealings specially adapted for rotary-piston machines or pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0046—Internal leakage control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0088—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps

Definitions

  • An embodiment of the present invention relates to the technical field of pump devices, in particular, to a pump device and a vehicle.
  • the pump device comprises a motor portion and a pump portion, and the rotating shaft of the motor portion can drive the pump portion to rotate, thereby realizing the compression function of the pump device.
  • the rotating shaft will have other structural friction problems with the pump device during high-speed rotation.
  • the oil of the pump portion is usually used to lubricate the rotating shaft.
  • how to ensure that the lubrication requirements of the rotating shaft are met without significantly affecting the displacement of the pump device has become an urgent problem to be solved.
  • one purpose of the embodiment of the present invention is to provide a pump device.
  • Another purpose of the embodiment of the present invention is to provide a vehicle having the above-mentioned pump device.
  • the embodiment of the present invention first aspect provides a pump device, comprising: a casing, comprising a cavity; a motor portion, comprising a rotating shaft rotatable around a central axis of the motor portion; a pump portion, the pump portion is arranged on an axial side of the motor portion and in contact with the rotating shaft, and can be driven by the rotating shaft to rotate; the pump portion comprises a first pressure chamber and a second pressure chamber, the pressure that the first pressure chamber bears is greater than the pressure that the second pressure chamber bears; a first bearing, connected with the casing and sleeved on the rotating shaft, the first bearing being located between the motor portion and the pump portion; a first oil groove, arranged on a first end surface of the first bearing facing the pump portion, and communicating with the first pressure chamber; and a throttle groove, provided on the first end surface, and communicating the first oil groove with a gap between the first bearing and the rotating shaft.
  • the pump device comprises a casing, a motor portion, a pump portion, a first bearing, a first oil groove and a throttle groove.
  • the casing has a cavity, and the motor portion and the pump portion are set in the cavity, to ensure that the motor portion and the pump portion are not affected by the external environment and can operate normally through the casing.
  • the motor portion comprises a rotating shaft that rotates around the central axis of the motor portion, the pump portion is arranged on an axial side of the motor portion, and the pump portion is in contact with the rotating shaft.
  • the pump portion has an interference fit with the rotating shaft, and the pump portion can be driven by the rotating shaft to rotate.
  • the motor portion drives the pump portion to rotate through the rotating shaft.
  • the pump portion comprises a first pressure chamber and a second pressure chamber, the pressure of the first pressure chamber is greater than that of the second pressure chamber, furthermore, the first pressure chamber can be a high pressure chamber, and the second pressure chamber can be a low pressure chamber.
  • the first bearing is connected with the casing, the first bearing is located between the motor portion and the pump portion, the first bearing is sleeved on the rotating shaft, and the first bearing can support the rotating shaft to a certain extent. It is worth noting that the first bearing can provide lubricating support to the rotating shaft. Since the axes of the first bearing and the rotating shaft coincide, in the actual working process, the rotating shaft drives the pump portion to rotate. Therefore, the pump portion will exert a radial force on the rotating shaft, and the rotating shaft will push the first bearing to one side while receiving the radial force. At this time, the rotating shaft is in contact with the first bearing, and the first bearing will provide support for the rotating shaft, the clearance of the rotating shaft can be controlled within a reasonable range, to facilitate the control of the axis of the rotating shaft.
  • the first bearing is a sliding bearing
  • the sliding bearing refers to a bearing that works under sliding friction. Compared with the form of rolling bearing, the sliding bearing works smoothly, reliably and without noise. Under the condition of liquid lubrication, the sliding surface is separated by the lubricating oil without direct contact, which can greatly reduce the friction loss and surface wear. And the gap between the sliding bearing and the rotating shaft is filled with lubricating oil, and the lubricating oil on the sliding surface will form an oil film to realize fluid lubrication.
  • the oil film also has a certain vibration absorption capacity, which improves the service life of the first bearing and the rotating shaft.
  • the first oil groove is arranged on the first end surface of the first bearing facing the pump portion, and the first oil groove communicates with the first pressure chamber. Due to the high pressure in the first pressure chamber, a portion of the oil will flow from the first pressure chamber to the first oil groove, and then flow into the gap between the rotating shaft and the first bearing, to ensure the lubrication performance between the first bearing and the rotating shaft.
  • the throttle groove is arranged on the first end surface, that is, the throttle groove is arranged on the first end surface of the first bearing facing the pump portion, and the throttle groove is used to communicate with the first oil groove and the gap between the first bearing and the rotating shaft. That is, the oil in the first pressure chamber first flows to the first oil groove, and then flows to the gap between the first bearing and the rotating shaft through the throttle groove.
  • the throttle groove can effectively avoid excessive oil flowing into the gap between the first bearing and the rotating shaft, and then affect the displacement of the pump device.
  • the first oil groove can balance the pressure between the cavities in the high pressure side of the pump portion, and then the pressures of the cavities on the high pressure side are similar, thereby reducing the noise and mechanical vibration during operation.
  • the flow cross-sectional area of the throttle groove is smaller than the flow cross-sectional area of the first oil groove, so 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.
  • a portion of an inner side wall of the first bearing is recessed away from the rotating shaft to form a first lubrication groove, which communicates with the throttle groove.
  • the first lubrication groove is formed by the depression of a portion of the inner side wall of the first bearing away from the rotating shaft, and the first lubrication groove communicates with the throttle groove. Due to the pressure difference, the oil in the first pressure chamber flows into the gap between the first bearing and the rotating shaft through the first oil groove and the throttle groove in turn, and can also be filled in the first lubrication groove. As the rotating shaft rotates, the oil in the first lubrication groove will coat the surface of the rotating shaft.
  • the first lubrication groove acts as a short-term storage of lubricating oil, and then a fluid lubricating oil film can be formed between the inner wall of the first bearing and the rotating shaft, which further ensures the reliable lubricity between the rotating shaft and the bearing.
  • the first lubrication groove is arranged axially through the first bearing, the first lubrication groove communicates with the shaft hole of the first bearing, one end of the first lubrication groove communicates with the throttle groove, and another end of the first lubrication groove extends toward the motor cavity.
  • the number of first lubrication grooves is at least one, which can be flexibly set according to actual lubrication requirements.
  • a ratio of a flow cross-sectional area of the throttle groove to a flow cross-sectional area of the first lubrication groove is greater than or equal to 0.1 and less than or equal to 0.4.
  • the flow cross-sectional area of the throttle groove will not be too large, to ensure that the oil on the high pressure side of the pump portion will not leak too much and affect the normal compression of the pump portion. That is, the oil will not flow into the first lubrication groove too much through the throttle groove, and will not have a significant impact on the displacement of the pump portion.
  • the flow cross-sectional area of the first lubrication groove will not be too small. This ensures that sufficient flow of lubricating oil can form an oil film between the first bearing and the rotating shaft to meet the fluid lubrication requirements.
  • a ratio of the flow cross-sectional area S2 of the first lubrication groove to a cross-sectional area SO of a shaft hole of the first bearing is greater than or equal to 0.02 and less than or equal to 0.08.
  • the flow cross-sectional area of the first lubrication groove is limited; the flow cross-sectional area of the first lubrication groove is not too small. It can ensure that the lubricating oil has enough flow rates to form an oil film between the first bearing and the rotating shaft to meet the fluid lubrication requirements.
  • the flow cross-sectional area of the first lubrication groove will not be too large, resulting in an excessively thick oil film formed between the first bearing and the rotating shaft, increasing the power consumption of the rotating shaft.
  • the cross-sectional area of the shaft hole of the first bearing is limited, it is in a suitable range, and it will not affect the oil entering the gap between the rotating shaft and the first bearing because it is too small.
  • the strength of the first bearing itself will not be affected because the cross-sectional area of the shaft hole of the first bearing is too large.
  • the shaft diameter of the first bearing is greater than or equal to 6mm and less than or equal to 12mm. According to the relationship between the shaft diameter of the first bearing and the deformation of the first bearing, and the relationship between the shaft diameter of the first bearing and the power consumption, it can be seen that when the shaft diameter is less than 6mm, the deformation of the bearing is large, which is not conducive to the bearing to support the rotating shaft. When the shaft diameter is greater than 12mm, the power consumption of the bearing increases sharply. Therefore, if the shaft diameter of the first bearing meets the above range, it not only meets the power consumption requirements of the bearing, but also avoids the excessive deformation of the bearing.
  • the pump device further comprises: a sealing member, connected to one side of the first bearing away from the pump portion, the sealing member is sleeved on the rotating shaft, the sealing member, the first bearing and the rotating shaft form a liquid passage chamber, the liquid passage chamber communicates with the first lubrication groove.
  • the first bearing is connected to the casing, and the first bearing can separate the cavity enclosed by the casing into the motor cavity and the pump cavity, which can make the space layout more reasonable.
  • the motor portion is located in the motor cavity
  • the pump portion is located in the pump cavity.
  • the sealing member is connected on one side of the first bearing away from the pump portion and the sealing member is sleeved on the rotating shaft. Specifically, the sealing member can isolate the motor cavity from the pump cavity, the working medium will not flow into the motor cavity, and will not affect the normal use of the stator, rotor, controller and other components in the motor cavity. There is no need to set other structures in the motor cavity to ensure that the components in the motor cavity are not corroded, which makes the sealing performance of the pump device better, and at the same time, the structure is simpler, which is conducive to reducing costs.
  • first bearing extends away from the pump portion to construct the installation position. Since the installation position and the first bearing are integral structures, compared with the post-processing method, the integral structure has better mechanical properties, thus can improve connection strength.
  • the first bearing can be mass-produced to improve the processing efficiency of the product, reduce the processing cost of the product, improve the integrity of the pump device, reduce the number of parts, reduce the installation process, and improve the installation efficiency.
  • the installation position for installing the sealing member is formed by a portion of the first bearing, the installation accuracy of the sealing member can be ensured, the assembly is simple, the sealing performance is good, and the cost is low.
  • the sealing member, the first bearing and the rotating shaft form a liquid passage chamber, and the liquid passage chamber communicates with the first lubrication groove.
  • the liquid passage chamber formed by the sealing member, the first bearing and the rotating shaft can store a portion of the lubricating oil, and the liquid passage chamber is used to store the lubricating oil from the first lubrication groove.
  • the connection strength between the sealing member and the first bearing that is, the pressure that the sealing member can bear
  • the liquid passage chamber can play a buffering role
  • the oil in the liquid passage chamber, the first lubrication groove, and the throttle groove can be in a state of pressure equalization.
  • the pump device further comprises: a pressure relief groove, arranged on the first bearing, and communicating with the liquid passage chamber and the second pressure chamber.
  • the pressure relief groove is arranged on the first bearing, and the pressure relief groove is used to communicate with the liquid passage chamber and the second pressure chamber.
  • the pressure relief groove can be in the form of a through hole, both ends of the through hole can communicate with the second pressure chamber and the liquid passage chamber. Since the pressure in the second pressure chamber is small, the pressure in the liquid passage chamber can be better released, and the pressure of the oil is not only buffered by the liquid passage chamber itself.
  • a complete lubricating oil circuit of the first bearing can be formed. That is, the oil in the first pressure chamber (high pressure chamber) enters the first oil groove, and then flows into the gap between the first bearing and the rotating shaft and the first lubrication groove through the throttle groove, to fully lubricate the rotating shaft and the first bearing and form an oil film, to meet fluid lubrication requirements. After that, the lubricating oil will flow into the liquid passage chamber, and further flow from the pressure relief groove into the second pressure chamber (low pressure chamber), to ensure that the pressure in the entire lubricating oil circuit will not be too high.
  • the pressure in the liquid passage chamber will not be too high, avoid the pressure being higher than the limit value of the pressure that the sealing member can bear, ensure the reliability of the position of the sealing member, and effectively prevent the sealing member from detaching from the first bearing under high pressure, resulting in the leakage of lubricating oil, and the sealing performance between the motor cavity and the pump cavity cannot be ensured.
  • a ratio of the flow cross-sectional area of the pressure relief groove to the flow cross-sectional area of the first lubrication groove is greater than or equal to 1 and less than or equal to 4.
  • the flow cross-sectional area of the first lubrication groove will not be too small to ensure that the lubricating oil has enough flow rate, to form an oil film between the first bearing and the rotating shaft, to meet the fluid lubrication requirements.
  • the flow cross-sectional area of the first lubrication groove will not be too large, resulting in an excessively thick oil film formed between the first bearing and the rotating shaft, which increases the power consumption of the rotating shaft.
  • the present invention takes into account the flow cross-sectional area of the throttle groove, the flow cross-sectional area of the first lubrication groove and the flow cross-sectional area of the pressure relief groove, the three satisfy the above-mentioned relationship, this ensures that there is sufficient oil flow in the first lubrication groove to ensure the lubrication of the first bearing and rotating shaft. At the same time, it can ensure that the pressure in the liquid passage chamber is low enough, without affecting the sealing connection between the sealing member and the first bearing, effectively reducing oil leakage.
  • the pump device further comprises: a buffer chamber, arranged on an end surface of the first bearing away from the pump portion.
  • the buffer chamber is arranged on the end surface of the first bearing away from the pump portion, specifically, the buffer chamber can be a tapered-shape. That is, the buffer chamber can be a tapered cavity; the buffer chamber can reduce the rigidity of the first bearing and provide flexible support for the rotating shaft. It can reduce the surface pressure on the axial end surface of the first bearing away from the pump portion, which can effectively improve the wear of the first bearing and the rotating shaft.
  • the buffer chamber comprises: a first wall surface, the first wall surface is a wall surface of the buffer chamber close to the rotating shaft, from an end of an opening of the buffer chamber to a bottom wall of the buffer chamber, a distance between the first wall surface and the rotating shaft increases.
  • the first wall surface is inclined and the position of the first wall surface located at the opening end of the buffer chamber is closer to the rotating shaft, and the distance between the first wall surface and the rotating shaft is smaller at the opening.
  • the distance between the first wall surface and the rotating shaft is larger at the position located at the bottom of the cavity, which also makes a right-angle structure not formed between the first wall surface and the groove bottom of the groove body.
  • the first bearing is usually made of aluminum alloy material, when the rotating shaft is in contact with the end of the first bearing, the first bearing will be deformed. If the connection between the first wall surface and the bottom wall of the conical cavity is a right-angle structure, stress concentration will occur at the connection between the first wall surface and the groove bottom of the groove body. When the first bearing is under the pressure of the rotating shaft, the first bearing is easily broken at the connection structure between the first wall surface and the bottom wall of the buffer chamber. When the first wall surface is inclined relative to the axial direction of the rotating shaft, the structure between the first wall surface and the bottom wall of the buffer chamber is not a right-angle structure, which can effectively reduce the damage rate of the first bearing.
  • the buffer chamber comprises: a second wall surface, the second wall surface is arranged face the first wall surface, from an opening end of the buffer chamber to a bottom wall of the buffer chamber, a distance between the second wall surface and the rotating shaft decreases.
  • the second wall surface is inclined relative to the axial direction of the rotating shaft, the second wall surface faces the first wall surface, and the distance between the second wall surface and the rotating shaft decreases from the end of the opening of the buffer chamber to the bottom wall of the buffer chamber. Therefore, the second wall surface and the first wall surface can be arranged axially symmetrically with respect to the center line of the buffer chamber. That is, the buffer chamber can have a regular cone shape, which can better provide flexible support for the rotating shaft. It can be understood that, in the axial direction away from the motor portion, the distance between the first wall surface and the rotating shaft increases, the gap between the second wall surface and the rotating shaft decreases, and the buffer chamber is constructed as an inverted cone shape. In the process of processing the buffer chamber, the inverted tapered buffer chamber is conducive to drafting.
  • the buffer chamber is constructed as an annular structure, that is, the buffer chambers are arranged in the circumferential direction of the first bearing.
  • the radial force on the first bearing may change at any time. That is, the first bearing will be subjected to radial forces that change in multiple directions, and no matter which direction the radial force received by the first bearing faces, the existence of the annular buffer chamber enables the first bearing to deform to a certain extent. Therefore, the rotating shaft and the first bearing are connected flexibly, and the first bearing has a buffering effect on the radial force of the rotating shaft, avoiding the problem that the first bearing is easily damaged due to the rigid connection between the rotating shaft and the first bearing.
  • the pump device further comprises: a second bearing, the second bearing is connected with the casing and sleeved on the rotating shaft, and the second bearing is located on one side of the pump portion away from the first bearing.
  • the second bearing is connected with the casing, and the second bearing is sleeved on the rotating shaft, and the second bearing is located on one side of the pump portion away from the first bearing, that is, the first bearing and the second bearing are located on both sides of the pump portion in the axial direction. And the first bearing is closer to the motor portion than the second bearing.
  • the first bearing and the second bearing can support the rotating shaft.
  • the first bearing and the second bearing are sliding bearings.
  • the sliding bearings work smoothly, reliably and without noise.
  • the sliding surfaces are separated by lubricating oil without direct contact, which can greatly reduce friction loss and surface wear.
  • the gap between the sliding bearing and the rotating shaft is filled with lubricating oil, and the lubricating oil on the sliding surface will form an oil film to realize fluid lubrication.
  • the oil film also has a certain ability to absorb vibration, which improves the service life of the first bearing, the second bearing and the rotating shaft.
  • Two sliding bearings support the rotating shaft, the clearance of the rotating shaft is small, and the position of the axis of the rotating shaft can be controlled within a reasonable range.
  • only two sliding bearings are used in this embodiment, which can not only simplify the support structure, but also reduce the cost.
  • 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
  • the axial height of the second bearing surface is less than or equal to the axial height of the first bearing surface, that is, not greater than it.
  • the first bearing and the second bearing are more suitable for different loads at different positions of the rotating shaft. And on the premise of ensuring the lubrication reliability of the rotating shaft, the power consumption of the rotating shaft can be reduced to a minimum level.
  • a portion of an inner side wall of the second bearing is recessed away from the rotating shaft to form a second lubrication groove, which communicates with the first pressure chamber.
  • the second lubrication groove is formed by the depression of a portion of the inner side wall of the second bearing away from the rotating shaft, and the second lubrication groove communicates with the first pressure chamber. Due to the pressure difference, the oil in the first pressure chamber flows into the gap between the first bearing and the rotating shaft through the second lubrication groove. As the rotating shaft rotates, the oil in the second lubrication groove will coat the surface of the rotating shaft.
  • the second lubrication groove can play a role of short-term storage of lubricating oil; a fluid lubricating oil film can be formed between the inner wall of the second bearing and the rotating shaft, to further ensure the lubricating performance between the rotating shaft and the bearing.
  • the pump device further comprises: an anti-push lubrication groove, provided on an end surface of the second bearing close to the pump portion, and communicating with a shaft hole of the second bearing.
  • the anti-push lubrication groove is arranged on the end surface of the second bearing close to the pump portion, and the anti-push lubrication groove communicates with the shaft hole of the second bearing.
  • the anti-push lubrication groove is arranged on the end surface of the second bearing close to the pump portion, and the anti-push lubrication groove communicates with the second bearing and the shaft hole of the second bearing.
  • the rotating shaft will shear the lubricating oil in the matching gap between itself and the second bearing.
  • the lubricating oil will enter the anti-push lubrication groove from the matching gap, and the lubricating oil entering the anti-push lubrication groove has a certain speed and pressure at this time.
  • the end surface clearance between the second bearing and the pump portion is small, and the lubricating oil in the anti-push lubrication groove can flow to the end surface clearance between the second bearing and the pump portion.
  • the condition of fluid lubrication is formed between the contact end surfaces of the pump portion and the second bearing. That is, an oil film is formed at the contact end surface between the second bearing and the pump portion, the boundary lubrication between the second bearing and the pump portion is transitioned to fluid lubrication, the wear of the contact end surface between the pump portion and the second bearing can be greatly improved, and the power consumption can be reduced. In addition, it can reduce the running noise of the pump device.
  • the notch area of the anti-push lubrication groove in the axial direction is larger than the groove bottom area of the anti-push lubrication groove.
  • the anti-push lubrication groove comprises two notches with different orientations, one towards the pump portion and another towards the rotating shaft.
  • the area of the notch toward the pump portion is defined to be larger than the area of the groove bottom. That is, in the axial direction away from the pump portion, that is, in the top-down direction, the anti-push lubrication groove has a constricted shape, that is, the groove wall of the anti-push lubrication groove has an inclined shape.
  • the lubricating oil entering the anti-push lubrication groove has a certain speed and pressure
  • the groove wall of the anti-push lubrication groove has an inclined shape. Then, there is a convergent wedge-shaped angle between the anti-push lubrication groove and the end surface clearance, and the lubricating oil in the anti-push lubrication groove will flow along the inclined groove wall to the end surface clearance between the pump portion and the second bearing, that is, the lubricating oil from "big port" to "small port”.
  • the "big port” refers to the anti-push lubrication groove
  • the "small port” refers to the gap between the second bearing and the pump portion.
  • the oil film between the contacting surfaces between the pump portion and the second bearing will generate a force F that pushes the pump portion upward, and then the lubricating oil located in the end surfaces of the second bearing and the pump portion acts as a floating seal, which can further reduce the leakage of the end surfaces.
  • the end surface leakage of the pump device accounts for 75% ⁇ 80% of the total leakage of the pump device. Therefore, it is very important to improve the leakage between the contacting end surfaces of the pump device. It is worth noting that lubricating oil has a certain viscosity.
  • the anti-push lubrication groove comprises an anti-push wall
  • the anti-push wall comprises at least one anti-push segment
  • at least one anti-push segment comprises a first anti-push segment
  • the first anti-push segment extends close to the center of the anti-push lubrication groove.
  • the anti-push lubrication groove comprises an anti-push wall; the anti-push wall is an inclined wall. In the axial direction away from the pump portion, that is, in the top-down direction, the anti-push wall extends close to the center of the anti-push wall.
  • the anti-push wall comprises at least one anti-push segment, at least one anti-push segment comprises a first anti-push segment, and the first anti-push segment extends in the axial direction away from the pump portion and close to the center of the anti-push lubrication groove.
  • the first anti-push segment can be composed of at least one straight segment and at least one curved segment, and the first anti-push segment has a first end close to the pump portion and a second end away from the pump portion. The second end of the first anti-push segment extends close to the center of the anti-push lubrication groove. That is, if the inclined extension trend of the first anti-push segment satisfies the above-mentioned relationship, the flow of lubricating oil can be facilitated.
  • the first anti-push segment can be composed of multi-segment curved surfaces or multi-segment arcs.
  • angle ⁇ between the first anti-push segment and the axial end surface of the second bearing is greater than 0° and less than 90°.
  • the axial end surface of the second bearing refers to the axial end surface of the second bearing close to the pump portion.
  • the angle between the first anti-push segment and the axial end surface satisfies 0° ⁇ 90°. Therefore, the first anti-push segment can better drain the lubricating oil into the end surface clearance between the second bearing and the pump portion, ensuring that the lubricating oil can enter the end surface clearance through its own velocity and pressure, and is guided by the first anti-push segment, a converging wedge-shaped angle is formed between the anti-push lubrication groove and the end surface clearance.
  • the lubricating oil in the anti-push lubrication groove will flow along the inclined groove wall to the end surface clearance of the pump portion and the second bearing, that is, the lubricating oil enters the "small port” from the "big port”. Therefore, the lubrication between the pump portion and the second bearing can be enhanced, the lubrication state between the two transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate between the two.
  • the angle ⁇ between the first anti-push segment and the axial end surface of the second bearing is 45°. It is worth noting that the inclined first anti-push segment can be machined on the end surface of the second bearing close to the pump portion by using the forming tool.
  • the longitudinal section (along the axial direction) of the anti-push lubrication groove can be an inverted triangle, a semicircle, etc.
  • At least one anti-push segment further comprises a second anti-push segment, which extends axially and connects between the first anti-push segment and the groove bottom of the anti-push lubrication groove.
  • the at least one anti-push segment further comprises a second anti-push segment, and the second anti-push segment extends along the axial direction to be connected between the first anti-push segment and the bottom of the groove.
  • the second anti-push segment cooperates with the first anti-push segment to form an anti-push wall, thereby ensuring that the volume of the anti-push lubrication groove meets the lubrication requirements. It is worth noting that, during the machining process, a straight groove is machined on the end surface of the second bearing toward the pump portion, and then chamfering is machined, the first anti-push segment and the second anti-push segment can be formed. Through the above processing sequence, the processing difficulty of anti-push lubrication groove can be reduced.
  • the number of anti-push walls is at least two.
  • the number of anti-push walls is at least two, and each anti-push wall in the at least two anti-push walls comprises at least one anti-push segment. At least one anti-push segment comprises a first anti-push segment. At least one anti-push segment further comprises a second anti-push segment. It is worth noting that the structures of at least two anti-push walls can be equal or unequal. When the number of anti-push walls is three, the structures of the three anti-push walls can be partially equal and partially unequal.
  • At least two anti-push walls include a first anti-push wall, and the first end of the first anti-push wall is connected to the inner side wall of the second bearing.
  • the tangent plane where the connection point between the first anti-push wall and the inner side wall of the second bearing is located is the first reference plane.
  • the angle ⁇ 1 between the first anti-push wall and the first reference plane is greater than or equal to 0° and less than 90°.
  • the first end of the first anti-push wall is the start end of the first anti-push wall
  • the second end of the first anti-push wall is the termination end of the first anti-push wall.
  • the first end is connected with the inner side wall of the second bearing
  • the inner side wall of the second bearing is the side wall of the shaft hole of the second bearing.
  • the tangent plane where the connection point between the first end and the second bearing is located is the first reference plane
  • the angle ⁇ 1 between the first anti-push wall and the first reference plane is greater than or equal to 0° and less than 90°.
  • the rotating shaft will shear the lubricating oil in the matching gap between itself and the second bearing, and the lubricating oil will enter the anti-push lubrication groove from the matching gap under the action of the shearing force ⁇ .
  • the lubricating oil entering the anti-push lubrication groove has a certain speed and pressure. Since the first anti-push wall is biased towards the rotating direction of the rotating shaft, the lubricating oil in the anti-push lubrication groove will have shaft shearing and surface shearing.
  • a negative pressure is formed at the position of the anti-push lubrication groove close to the shaft hole, to suck the lubricating oil between the rotating shaft and the second bearing.
  • the pressure in the anti-push lubrication groove is higher at the position away from the shaft hole, the lubricating oil in the anti-push lubrication groove will flow into the end surface clearance between the second bearing and the pump portion along the inclined anti-push wall. Therefore, the lubrication between the pump portion and the second bearing can be enhanced, the lubrication state between the two transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate between the two.
  • the at least two anti-push walls also include a second anti-push wall, the second anti-push wall is set opposite to the first anti-push wall, and the first end of the second anti-push wall is connected to the inner side wall of the second bearing.
  • the tangent plane where the connection point between the second anti-push wall and the inner side wall of the second bearing is located is the second reference plane, and the angle ⁇ 2 between the second anti-push wall and the second reference plane is greater than 0° and less than 90°.
  • the at least two anti-push walls also include the second anti-push wall, and the first end of the second anti-push wall is the starting end of the second anti-push wall.
  • the second end of the second anti-push wall is the termination end of the second anti-push wall, the second 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 between the first end and the second bearing is the second reference plane, and the angle ⁇ 2 between the second anti-push wall and the second reference plane is greater than or equal to 0° and less than 90°.
  • the rotating shaft will shear the lubricating oil in the matching gap between itself and the second bearing, and the lubricating oil will enter the anti-push lubrication groove from the matching gap under the action of the shearing force ⁇ .
  • the lubricating oil entering the anti-push lubrication groove has a certain speed and pressure. Since the second anti-push wall is biased towards the rotating direction of the rotating shaft, the lubricating oil in the anti-push lubrication groove will have shaft shearing and surface shearing.
  • a negative pressure is formed at the position of the anti-push lubrication groove close to the shaft hole, to suck the lubricating oil between the rotating shaft and the second bearing.
  • the pressure in the anti-push lubrication groove is higher at the position away from the shaft hole, the lubricating oil in the anti-push lubrication groove will flow into the end surface clearance between the second bearing and the pump portion along the inclined anti-push wall. Therefore, the lubrication between the pump portion and the second bearing can be enhanced, the lubrication state between the two transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate between the two.
  • the at least two anti-push walls also include a third anti-push wall, and the third anti-push wall is respectively connected with the second end of the first anti-push wall and the second end of the second anti-push wall.
  • the at least two anti-push walls also include a third anti-push wall, and the third anti-push wall is respectively connected with the second end of the first anti-push wall and the second end of the second anti-push wall. That is, the anti-push lubrication groove is composed of the first anti-push wall, the second anti-push wall and the third anti-push wall, which can facilitate the shape design of the anti-push lubrication groove.
  • the projection of the first anti-push wall, the second anti-push wall and the third anti-push wall on the axial end surface of the second bearing can be a straight segment or a curved segment.
  • the third anti-push wall of the anti-push lubrication groove is an arc-shaped wall.
  • the third anti-push wall is an arc-shaped wall, that is, the projection of the third anti-push wall on the axial end surface of the second bearing is an arc-shaped segment. Since the position corresponding to the third anti-push wall is the position away from the shaft hole in the anti-push lubrication groove, the lubricating oil pressure in the anti-push lubrication groove corresponding to this position is higher.
  • the third anti-push wall an arc-shaped wall, the flow of lubricating oil in the anti-push lubrication groove can be facilitated, it can facilitate lubricating oil from the "big port” into the "small port”, and can enhance the lubrication between the pump portion and the second bearing, the lubrication state between the two transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate between the two.
  • the casing comprises: a machine shell, surrounding the motor portion and the pump portion and connected with the first bearing; and a pump cover, the pump cover is connected on the machine shell, the pump cover and the machine shell form the cavity, the pump cover is connected to the second bearing, a portion of the pump cover extends away from the pump portion to form an extension portion being used for forming an oil pool, a shaft hole of the second bearing is an axial through hole, one end of the through hole is communicated with the anti-push lubrication groove, and another end of the through hole is used to communicate with the oil pool.
  • the casing comprises a machine shell and a pump cover connected on the machine shell, the pump cover and the machine shell form a cavity, and the machine shell surrounds outside the motor portion and the pump portion.
  • the machine shell is connected with the first bearing
  • the pump cover is connected with the second bearing.
  • the first bearing and the machine shell can be integrally formed, and the machine shell and the first bearing can be integrally formed.
  • the connection strength is higher; it can save space, reduce the height of the whole machine, and can reduce the difficulty of the preparation process and reduce the production cost.
  • the pump cover and the second bearing can be integrally formed, saving more height space, not only reducing the height of the whole machine, but also reducing the cost.
  • the extension portion is formed by an extension structure of a portion of the pump cover away from the pump portion. Therefore, the extension portion and the pump cover are integrally formed, and the connection strength is higher than the post-processing method.
  • the extension portion is used to form an oil pool, which can store the lubricating oil.
  • the shaft hole on the second bearing is an axial through hole, and the two ends of the through hole are connected to the anti-push lubrication groove and the oil pool respectively.
  • the rotating shaft will shear the lubricating oil in the matching gap between itself and the second bearing.
  • the lubricating oil will enter the anti-push lubrication groove from the matching gap (through hole) under the action of shearing force.
  • the lubricating oil entering the anti-push lubrication groove has a certain speed and pressure.
  • the lubricating oil in the anti-push lubrication groove will undergo shaft shearing and surface shearing, thereby forming a negative pressure in the anti-push lubrication groove close to the shaft hole, to suck the lubricating oil between the rotating shaft and the second bearing.
  • the pressure in the anti-push lubrication groove is higher at the position away from the shaft hole, and the lubricating oil in the anti-push lubrication groove can be better pushed into the end surface clearance between the second bearing and the pump portion. Therefore, the lubrication between the pump portion and the second bearing can be enhanced, the lubrication state between the two transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate between the two.
  • the oil is drawn into the anti-push lubrication groove to lubricate the contact surface between the pump portion and the second bearing, and then enters the gap between the second bearing and the pump portion, and then enters the oil pool of the low pressure area under the action of pressure difference and gravity.
  • the lubricating oil circuit of the second bearing is as follows: the oil enters the gap between the second bearing and the rotating shaft through the oil pool (through hole, second lubrication groove) and then enters the anti-push lubrication groove. Under the action of the anti-push lubrication groove, the oil enters the end surface clearance between the pump portion and the second bearing, and enters the low pressure oil pool under the action of pressure difference and gravity.
  • the pump cover and the second bearing are integrally formed.
  • the connection strength is higher; it can save space, reduce the height of the whole machine, and can reduce the difficulty of the preparation process and reduce the production cost.
  • the casing comprises: a machine shell, surrounding the motor portion and the pump portion, and the machine shell is connected with the first bearing; and a pump cover, the pump cover is connected on the machine shell, the pump cover and the machine shell form the cavity, and the pump cover is connected to the second bearing, the shaft hole of the second bearing is a blind hole with one end open; and a communication groove, arranged on the second bearing and/or the pump cover, and communicating the first pressure chamber and the blind hole.
  • the casing comprises a machine shell and a pump cover connected on the machine shell, the pump cover and the machine shell form a cavity, and the machine shell surrounds outside the motor portion and the pump portion.
  • the machine shell is connected with the first bearing
  • the pump cover is connected with the second bearing.
  • the first bearing and the machine shell can be integrally formed, and the machine shell and the first bearing are integrally formed.
  • the connection strength is higher; it can save space, reduce the height of the whole machine, and can reduce the difficulty of the preparation process and reduce the production cost.
  • the pump cover and the second bearing can be integrally formed, saving more height space, not only reducing the height of the whole machine, but also reducing the cost.
  • the shaft hole of the second bearing is a blind hole with one end open, and the communication groove is arranged on the second bearing and/or the pump cover, and the communication groove is used to communicate with the first pressure chamber and the blind hole.
  • the lubricating oil circuit of the second bearing is: the pressurized oil enters the blind hole (the gap between the second bearing and the rotating shaft, the second lubrication groove) from the first pressure chamber (high pressure chamber) through the communication groove and then returns to the low pressure area through the gap between the second bearing and the pump portion, where the low pressure area specifically refers to the oil inlet and the second pressure chamber.
  • the pump portion comprises: a first rotation member, matched with the rotating shaft; and a second rotation member, the second rotation member is arranged on an outside of the first rotation member, and the first rotation member can drive the second rotation member to rotate, the second rotation member and the first rotation member form the first pressure chamber and the second pressure chamber
  • the pump device further comprises: an oil inlet, arranged on the pump cover and/or the second bearing along an axial direction, and the oil inlet communicating with the second pressure chamber; an oil outlet, arranged on the pump cover and the second bearing along an radial direction, and the oil outlet communicating with the first pressure chamber of the pump portion.
  • the pump portion comprises a first rotation member and a second rotation member, the first rotation member is matched with the rotating shaft, the second rotation member is arranged outside the first rotation member, and the first rotation member can drive the second rotation member to rotate. It can be understood that the rotating shaft can drive the second rotation member to run through the first rotation member.
  • the first pressure chamber and the second pressure chamber are formed by setting the first rotation member and the second rotation member, and the first pressure chamber is a high pressure chamber, and the second pressure chamber is a low pressure chamber.
  • the first rotation member is an inner gear
  • the second rotation member is an outer gear
  • the pump portion is a gear pump.
  • the former pair of teeth has not yet been disengaged, and the latter pair of teeth has entered meshing, and each inner tooth surface is in contact with the outer tooth surface to form a closed cavity, with the rotation of the inner gear, the volume of the closed cavity will change, and if the unloading channel cannot be connected, the trapped oil volume will be formed. Due to the small compressibility of the liquid, when the trapped oil volume changes from large to small, the liquid in the trapped oil volume is squeezed, and the pressure rises sharply, which greatly exceeds the working pressure of the gear pump.
  • the liquid in the trapped oil volume is also forcibly squeezed out from all leakable gaps, that the rotating shaft and bearing will bear a large impact load. This will increase power loss and cause oil to heat up causing noise and vibrations that reduce the smoothness and life of the gear pump.
  • a vacuum is formed, which causes the air dissolved in the liquid to separate out and generate bubbles, which bring about hazards such as cavitation, noise, vibration, flow and pressure pulsation.
  • the method of eliminating the trapped oil is to open the unloading groove on both ends of the gear, when the closed volume decreases, the unloading groove communicates with the oil pressure chamber, and when the closed volume increases; it communicates with the oil suction chamber through the unloading groove.
  • the inner gear meshes with the tooth profile of the conjugate curve of the outer gear, and each tooth is in contact with each other, driving the outer gear to rotate in the same direction.
  • the inner gear divides the inner cavity of the outer gear into multiple working chambers. Due to the offset of the center of the inner and outer gears, the volumes of the multiple working chambers change with the rotation of the rotor, and a certain vacuum is formed in the area where the volume increases.
  • the oil inlet is set at this position, the pressure increases in the area where the volume decreases, and the oil outlet is set here accordingly.
  • the pump device further comprises an oil inlet and an oil outlet, the oil inlet is arranged on the pump cover and/or the second bearing along an axial direction, and the oil inlet communicates with the second pressure chamber. Since the second pressure chamber is a low pressure chamber, there is a pressure difference with the outside of the chamber, so the oil will enter the second pressure chamber through the oil inlet.
  • the oil outlet is arranged on the pump cover and the second bearing along an radial direction, and the oil outlet communicates with the first pressure chamber. Since the first pressure chamber is a high pressure chamber, there is a pressure difference with the outside of the chamber, so the oil in the first pressure chamber will flow out through the oil outlet.
  • the main oil circuit of the pump device is: the negative pressure that can be generated at the second pressure chamber and the oil inlet and under the action of the negative pressure, the oil in the oil pool is attracted to the oil inlet, and then enters the second pressure chamber (low pressure chamber), and then the oil entering the second pressure chamber enters the high pressure chamber under the action of the first rotation member and the second rotation member to be pressurized, and the pressurized oil is discharged through the oil outlet.
  • the design principle of the oil inlet and the oil outlet in the process of ensuring the rotation of the gear, the oil inlet and the teeth of the first rotation member and the second rotation member are connected as soon as possible, before the inner gear and the outer gear form the maximum volume, the gear volume cavity is always communicated with the oil inlet, and the oil filling time should be prolonged as much as possible, the volume cavity between the inner and outer teeth is filled with oil, thereby ensuring the oil absorption.
  • the oil outlet should also be connected to the high-pressure oil between the teeth as soon as possible, to reduce the excessive compression work between the teeth, and close as late as possible to make full use of the inertia of the fluid to drain the oil between the teeth, thereby improving the volumetric efficiency of the inner gear oil pump.
  • the inner and outer gears form the maximum volume, they cannot communicate with the oil inlet to avoid affecting the volumetric efficiency of the pump device at low speed.
  • the motor portion further comprises: a rotor, connected with the rotating shaft; and a stator, sleeved on an outside of the rotor, the stator comprising a stator core and a stator winding, and the stator winding is arranged on the stator core
  • the pump device further comprises: a controller, arranged on one side of the motor portion away from the pump portion, and connected on the casing and located in the cavity, and one end of the stator winding being electrically connected to the controller.
  • the motor portion further comprises a rotor and a stator.
  • the rotor and the rotating shaft are connected, in some embodiments, the rotor and the rotating shaft can be coaxially arranged, and the matching mode of the rotor and the rotating shaft can be interference fit.
  • the rotor and rotating shaft can be set on different shafts, but the two are connected by transmission, which can be flexibly set according to the actual situation.
  • the stator is sleeved on the outer side of the rotor, the stator comprises the stator core and the stator winding, and the stator winding is set on the stator core.
  • the pump device further comprises a controller, and the controller is arranged on one side of the motor portion away from the pump portion, that is, the controller is arranged at a position of the motor portion away from the pump portion. Since the vibration near the pump portion is more obvious during the working process, and the load is larger, the controller is far away from the pump portion, which can protect the controller to a certain extent and improve the service life of the controller.
  • controller is connected on the casing and located in the cavity, and the end of the stator winding is electrically connected to the controller.
  • the controller controls the current of the stator winding in the stator to change according to a certain law, thereby controlling the stator to generate a changing excitation magnetic field.
  • the rotor rotates under the action of the excitation magnetic field, thereby driving the first rotation member in the pump portion to rotate through the rotating shaft, thereby making the second rotation member move.
  • the volume of the compression cavity formed between the first rotation member and the second rotation member changes.
  • the working medium entering the compression chamber is pressed out to the oil outlet to generate flow power.
  • the embodiment of the second aspect of the present invention provides a vehicle, including a pump device in any one of the above-mentioned embodiments.
  • the vehicle including the pump device, furthermore, the vehicle can be a special vehicle, and the vehicle has all the advantages of the pump device.
  • the vehicle can be a traditional fuel vehicle or a new energy vehicle.
  • New energy vehicles include pure electric vehicles, extended-range electric vehicles, hybrid electric vehicles, fuel cell electric vehicles, hydrogen engine vehicles, etc.
  • the vehicle comprises: a vehicle body; a pump device set in the vehicle body; an engine set in the vehicle body, the engine comprises a mounting seat, and the mounting seat is connected with the extension portion of the pump device.
  • the vehicle comprises a vehicle body and an engine. Both the pump device and the engine are set in the vehicle body, the engine comprises a mounting seat, and the mounting seat is connected with the extension portion of the pump device, the engine and the pump device can be connected through the cooperation of the mounting seat and the extension portion.
  • the vehicle comprises any one of the pump devices in the above-mentioned first aspect, it has the beneficial effects of any one of the above-mentioned embodiments, which will not be repeated here.
  • 100 pump device 110 casing, 111 cavity, 112 machine shell, 113 pump cover, 114 extension portion, 115 oil pool, 120 motor portion, 121 rotating shaft, 122 rotor, 123 stator, 130 pump portion, 131 first pressure chamber, 132 second pressure chamber, 133 first rotation member, 134 second rotation member, 140 first bearing, 141 first oil groove, 142 throttle groove, 143 first lubrication groove, 144 pressure relief groove, 150 sealing member, 151 liquid passage chamber, 160 buffer chamber, 161 first wall surface, 162 second wall surface, 170 second bearing, 171 second lubrication groove, 172 anti-push lubrication groove, 181 oil inlet, 182 oil outlet, 190 controller, 200 vehicle, 210 vehicle body, 220 engine, 221 mounting seat.
  • the pump device 100 and the vehicle 200 provided according to some embodiments of the present invention are described below with reference to Figs. 1 to 6 .
  • the embodiment of the present invention first aspect provides a pump device 100, as shown in Figs. 1 , 2 and 3 , comprising: a casing 110, comprising a cavity 111; a motor portion 120, comprising a rotating shaft 121 rotatable around a central axis of the motor portion 120; a pump portion 130, the pump portion 130 is arranged on an axial side of the motor portion 120 and in contact with the rotating shaft 121, and can be driven by the rotating shaft 121 to rotate; the pump portion 130 comprises a first pressure chamber 131 and a second pressure chamber 132, the pressure that the first pressure chamber 131 bears is greater than the pressure that the second pressure chamber 132 bears; a first bearing 140, connected with the casing 110 and sleeved on the rotating shaft 121, the first bearing 140 is located between the motor portion 120 and the pump portion 130; a first oil groove 141, arranged on a first end surface of the first bearing 140 facing the pump portion 130, and communicating with the first pressure chamber 131; and a
  • the pump device 100 comprises a casing 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 portion 120 and the pump portion 130 are set in the cavity 111, to ensure that the motor portion 120 and the pump portion 130 are not affected by the external environment and can operate normally through the casing 110.
  • the motor portion 120 comprises a rotating shaft 121 that rotates around the central axis of the motor portion 120, the pump portion 130 is arranged on an axial side of the motor portion 120, and the pump portion 130 is in contact with the rotating shaft 121.
  • the pump portion 130 has an interference fit with the rotating shaft 121, and the pump portion 130 can be driven by the rotating shaft 121 to rotate. It can be understood that the motor portion 120 drives the pump portion 130 to rotate through the rotating shaft 121.
  • the pump portion 130 comprises a first pressure chamber 131 and a second pressure chamber 132, the pressure of the first pressure chamber 131 is greater than that of the second pressure chamber 132, furthermore, the first pressure chamber 131 can be a high pressure chamber, and the second pressure chamber 132 can be a low pressure chamber.
  • the first bearing 140 is connected with the casing 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 is worth noting that the first bearing 140 can provide lubricating support to the rotating shaft 121. Since the axes of the first bearing 140 and the rotating shaft 121 coincide, in the actual working process, the rotating shaft 121 drives the pump portion 130 to rotate. Therefore, the pump portion 130 will exert a radial force on the rotating shaft 121, and the rotating shaft 121 will push the first bearing 140 to one side while receiving the radial force.
  • the rotating shaft 121 is in contact with the first bearing 140, and the first bearing 140 will provide support for the rotating shaft 121, the clearance of the rotating shaft 121 can be controlled within a reasonable range, to facilitate the control of the axis of the rotating shaft 121.
  • the first bearing 140 is a sliding bearing
  • the sliding bearing refers to a bearing that works under sliding friction. Compared with the form of rolling bearing, the sliding bearing works smoothly, reliably and without noise. Under the condition of liquid lubrication, the sliding surface is separated by the lubricating oil without direct contact, which can greatly reduce the friction loss and surface wear. And the gap between the sliding bearing and the rotating shaft 121 is filled with lubricating oil, and the lubricating oil on the sliding surface will form an oil film to realize fluid lubrication. The oil film also has a certain vibration absorption capacity, which improves the service life of the first bearing 140 and the rotating shaft 121.
  • the first oil groove 141 is arranged on the first end surface of the first bearing 140 facing the pump portion 130, and the first oil groove 141 communicates with the first pressure chamber 131. Due to the high pressure in the first pressure chamber 131, a portion of the oil will flow from the first pressure chamber 131 to the first oil groove 141, and then flow into the gap between the rotating shaft 121 and the first bearing 140, to ensure the lubrication performance between the first bearing 140 and the rotating shaft 121.
  • the throttle groove 142 is arranged on the first end surface, that is, the throttle groove 142 is arranged on the first end surface of the first bearing 140 facing the pump portion 130, and the throttle groove 142 is used to communicate with 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 first flows to the first oil groove 141, and then flows to the gap between the first bearing 140 and the rotating shaft 121 through the throttle groove 142.
  • the throttle groove 142 can effectively avoid excessive oil flowing into the gap between the first bearing 140 and the rotating shaft 121, and then affect the displacement of the pump device 100.
  • first oil groove 141 and throttle groove 142 the lubrication requirements between the first bearing 140 and the rotating shaft 121 can be achieved, and the flow rate in the first bearing 140 will not be too large to reduce the displacement of the pump device 100.
  • the first oil groove 141 can balance the pressure between the cavities in the high pressure side of the pump portion 130, and then the pressures of the cavities on the high pressure side are similar, thereby reducing the noise and mechanical vibration during operation.
  • 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 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.
  • a portion of an inner side wall of the first bearing 140 is recessed away from the rotating shaft 121 to form a first lubrication groove 143, which communicates with the throttle groove 142.
  • the first lubrication groove 143 is formed by the depression of a portion of the inner side wall of the first bearing 140 away from the rotating shaft 121, and the first lubrication groove 143 communicates with the throttle groove 142. 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 first oil groove 141 and the throttle groove 142 in turn, and can also be filled in the first lubrication groove 143. As the rotating shaft 121 rotates, the oil in the first lubrication groove 143 will coat the surface of the rotating shaft 121.
  • the first lubrication groove 143 acts as a short-term storage of lubricating oil, and then a fluid lubricating oil film can be formed between the inner wall of the first bearing 140 and the rotating shaft 121, which further ensures the reliable lubricity between the rotating shaft 121 and the bearing. Furthermore, the first lubrication groove 143 is arranged axially through the first bearing 140, 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 another end of the first lubrication groove 143 extends toward the motor cavity. Furthermore, the number of first lubrication groove 143s is at least one, which can be flexibly set according to actual lubrication requirements.
  • a ratio of a flow cross-sectional area S1 of the throttle groove 142 to a flow cross-sectional area S2 of the first lubrication groove 143 is greater than or equal to 0.1 and less than or equal to 0.4.
  • the flow cross-sectional area of the throttle groove 142 will not be too large, to ensure that the oil on the high pressure side of the pump portion 130 will not leak too much and affect the normal compression of the pump portion 130. That is, the oil will not flow into the first lubrication groove 143 too much through the throttle groove 142, and will not have a significant impact on the displacement of the pump portion 130.
  • the flow cross-sectional area of the first lubrication groove 143 By limiting the flow cross-sectional area of the first lubrication groove 143, the flow cross-sectional area of the first lubrication groove 143 will not be too small. This ensures that sufficient flow of lubricating oil can form an oil film between the first bearing 140 and the rotating shaft 121 to meet the fluid lubrication requirements.
  • a ratio of the flow cross-sectional area S2 of the first lubrication groove 143 to a cross-sectional area SO of a shaft hole of the first bearing 140 is greater than or equal to 0.02 and less than or equal to 0.08.
  • the flow cross-sectional area of the first lubrication groove 143 is limited, the flow cross-sectional area of the first lubrication groove 143 is not too small. It can ensure that the lubricating oil has enough flow rates to form an oil film between the first bearing 140 and the rotating shaft 121 to meet the fluid lubrication requirements. The flow cross-sectional area of the first lubrication groove 143 will not be too large, resulting in an excessively thick oil film formed between the first bearing 140 and the rotating shaft 121, increasing the power consumption of the rotating shaft 121.
  • the cross-sectional area of the shaft hole of the first bearing 140 is limited, it is in a suitable range, and it will not affect the oil entering the gap between the rotating shaft 121 and the first bearing 140 because it is too small.
  • the strength of the first bearing140 itself will not be affected because the cross-sectional area of the shaft hole of the first bearing 140 is too large.
  • the shaft diameter of the first bearing 140 is greater than or equal to 6mm and less than or equal to 12mm.
  • the shaft diameter of the first bearing 140 is less than 6mm
  • the deformation of the bearing is large, which is not conducive to the bearing to support the rotating shaft 121.
  • the shaft diameter is greater than 12mm
  • the power consumption of the bearing increases sharply. Therefore, if the shaft diameter of the first bearing 140 meets the above range, it not only meets the power consumption requirements of the bearing, but also avoids the excessive deformation of the bearing.
  • the pump device 100 further comprises: a sealing member 150, connected to one side of the first bearing 140 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 liquid passage chamber 151, the liquid passage chamber 151 communicates with the first lubrication groove 143.
  • the first bearing 140 is connected to the casing 110, and the first bearing 140 can separate the cavity 111 enclosed by the casing 110 into the motor cavity and the pump cavity, which can make the space layout more reasonable.
  • the motor portion 120 is located in the motor cavity
  • the pump portion 130 is located in the pump cavity.
  • the sealing member 150 is connected on one side of the first bearing 140 away from the pump portion 130 and the sealing member 150 is sleeved on the rotating shaft 121.
  • the sealing member 150 can isolate the motor cavity from the pump cavity; the working medium will not flow into the motor cavity, and will not affect the normal use of the stator 123, rotor 122, controller 190 and other components in the motor cavity.
  • There is no need to set other structures in the motor cavity to ensure that the components in the motor cavity are not corroded, which makes the sealing performance of the pump device 100 better, and at the same time, the structure is simpler, which is conducive to reducing costs.
  • a portion of the first bearing 140 extends away from the pump portion 130 to construct the installation position. Since the installation position and the first bearing 140 are integral structures, compared with the post-processing method, the integral structure has better mechanical properties, thus can improve connection strength. In addition, the first bearing 140 can be mass-produced to improve the processing efficiency of the product, reduce the processing cost of the product, improve the integrity of the pump device 100, reduce the number of parts, reduce the installation process, and improve the installation efficiency. In addition, the installation position for installing the sealing member 150 is formed by a portion of the first bearing 140, 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.
  • the sealing member 150, the first bearing 140 and the rotating shaft 121 form a liquid passage chamber 151, and the liquid passage chamber 151 communicates with the first lubrication groove 143.
  • the liquid passage chamber 151 formed by the sealing member 150, the first bearing 140 and the rotating shaft 121 can store a portion of the lubricating oil, and the liquid passage chamber 151 is used to store the lubricating oil from the first lubrication groove 143.
  • the liquid passage chamber 151 can play a buffering role, the oil in the liquid passage chamber 151, the first lubrication groove 143, and the throttle groove 142 can be in a state of pressure equalization.
  • the pump device 100 further comprises: a pressure relief groove 144, arranged on the first bearing 140, and communicating with the liquid passage chamber 151 and the second pressure chamber 132.
  • the pressure relief groove 144 is arranged on the first bearing 140, and the pressure relief groove 144 is used to communicate with the liquid passage chamber 151 and the second pressure chamber 132.
  • the pressure relief groove 144 can be in the form of a through hole, both ends of the through hole can communicate with the second pressure chamber 132 and the liquid passage chamber 151. Since the pressure in the second pressure chamber 132 is small, the pressure in the liquid passage chamber 151 can be better released, and the pressure of the oil is not only buffered by the liquid passage chamber151 itself.
  • a complete lubricating oil circuit 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, and then flows into the gap between the first bearing 140 and the rotating shaft 121 and the first lubrication groove 143 through the throttle groove 142, to fully lubricate the rotating shaft 121 and the first bearing 140 and form an oil film, to meet fluid lubrication requirements. After that, the lubricating oil will flow into the liquid passage chamber 151, and further flow from the pressure relief groove 144 into the second pressure chamber 132 (low pressure chamber), to ensure that the pressure in the entire lubricating oil circuit will not be too high.
  • the pressure in the liquid passage chamber 151 will not be too high, avoid the pressure being higher than the limit value of the pressure that the sealing member 150 can bear, ensure the reliability of the position of the sealing member 150, and effectively prevent the sealing member 150 from detaching from the first bearing 140 under high pressure, resulting in the leakage of lubricating oil, and the sealing performance between the motor cavity and the pump cavity cannot be ensured.
  • a 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 greater than or equal to 1 and less than or equal to 4.
  • the flow cross-sectional area of the first lubrication groove 143 will not be too small to ensure that the lubricating oil has enough flow rate, to form an oil film between the first bearing 140 and the rotating shaft 121, to meet the fluid lubrication requirements.
  • the flow cross-sectional area of the first lubrication groove 143 will not be too large, resulting in an excessively thick oil film formed between the first bearing 140 and the rotating shaft 121, which increases the power consumption of the rotating shaft 121.
  • the present invention takes into account the flow cross-sectional area of the throttle groove 142, the flow cross-sectional area of the first lubrication groove 143 and the flow cross-sectional area of the pressure relief groove 144, the three satisfy the above-mentioned relationship, this ensures that there is sufficient oil flow in the first lubrication groove 143 to ensure the lubrication of the first bearing 140 and rotating shaft 121. At the same time, it can ensure that the pressure in the liquid passage chamber 151 is low enough, without affecting the sealing connection between the sealing member 150 and the first bearing 140, effectively reducing oil leakage.
  • the simulation data it is determined that the flow rate of the lubricating oil in the lubricating oil circuit of the first bearing 140 should not be lower than 3ml/s, and the shaft diameter of the first bearing 140 is 8mm.
  • the flow cross-sectional area S2 1.57mm 2 of the first lubrication groove 143 is the best choice. Then design the different structure of the flow cross-sectional area S1 of throttle groove 142 and the flow cross-sectional area S3 of the pressure relief groove 144 to obtain the simulation data shown in Table 1 below: Table 1 Serial No.
  • the scheme in No. 3 is the optimal scheme, that is, the flow cross-sectional area S1 of the throttle groove 142 is 0.4mm 2 , the flow cross-sectional area S2 of the first lubrication groove 143 is 1.57mm 2 , the flow cross-sectional area S3 of the pressure relief groove 144 is 3.14mm 2 .
  • the oil flow rate in the first lubrication groove 143 is 7.3ml/s, which can meet the lubrication requirement without the oil flow rate in the first bearing 140 being too large and reducing the displacement of the pump device 100.
  • the pressure in the liquid passage chamber 151 is 112kPa, and the pressure will not be too high, and then serious leakage of oil can be avoided.
  • the pump device 100 further comprises a buffer chamber 160, and the buffer chamber 160 is disposed on the end surface of the first bearing 140 away from the pump portion 130.
  • the buffer chamber 160 is arranged on the end surface of the first bearing 140 away from the pump portion 130, specifically, the buffer chamber 160 can be a tapered-shape. That is, the buffer chamber 160 can be a tapered cavity; the buffer chamber 160 can reduce the rigidity of the first bearing 140 and provide flexible support for the rotating shaft 121. It can reduce the surface pressure on the axial end surface of the first bearing 140 away from the pump portion 130, which can effectively improve the wear of the first bearing 140 and the rotating shaft 121.
  • the buffer chamber 160 comprises: a first wall surface 161, the first wall surface 161 is a wall surface of the buffer chamber 160 close to the rotating shaft 121, from an end of an opening of the buffer chamber 160 to a bottom wall of the buffer chamber 160, a distance between the first wall surface 161 and the rotating shaft 121 increases. It can be understood that the first wall surface 161 is inclined and the position of the first wall surface 161 located at the opening end of the buffer chamber 160 is closer to the rotating shaft 121, and the distance between the first wall surface 161 and the rotating shaft 121 is smaller at the opening.
  • the distance between the first wall surface 161 and the rotating shaft 121 is larger at the position located at the bottom of the cavity, which also makes a right-angle structure not formed between the first wall surface 161 and the groove bottom of the groove body.
  • the first bearing 140 is usually made of aluminum alloy material, when the rotating shaft 121 is in contact with the end of the first bearing 140, the first bearing 140 will be deformed. If the connection between the first wall surface 161 and the bottom wall of the conical cavity is a right-angle structure, stress concentration will occur at the connection between the first wall surface 161 and the groove bottom of the groove body. When the first bearing 140 is under the pressure of the rotating shaft 121, the first bearing 140 is easily broken at the connection structure between the first wall surface 161 and the bottom wall of the buffer chamber 160. When the first wall surface 161 is inclined relative to the axial direction of the rotating shaft 121, the structure between the first wall surface 161 and the bottom wall of the buffer chamber 160 is not a right-angle structure, which can effectively reduce the damage rate of the first bearing 140.
  • the buffer chamber 160 comprises: a second wall surface 162, the second wall surface 162 is arranged face the first wall surface 161, from an opening end of the buffer chamber 160 to a bottom wall of the buffer chamber 160, a distance between the second wall surface 162 and the rotating shaft 121 decreases.
  • the second wall surface 162 is inclined relative to the axial direction of the rotating shaft 121, the second wall surface 162 faces the first wall surface 161, and the distance between the second wall surface 162 and the rotating shaft 121 decreases from the end of the opening of the buffer chamber 160 to the bottom wall of the buffer chamber 160. Therefore, the second wall surface 162 and the first wall surface 161 can be arranged axially symmetrically with respect to the center line of the buffer chamber 160. That is, the buffer chamber 160 can have a regular cone shape, which can better provide flexible support for the rotating shaft 121.
  • the buffer chamber 160 is constructed as an inverted cone shape. In the process of processing the buffer chamber 160, the inverted tapered buffer chamber 160 is conducive to drafting.
  • the buffer chamber 160 is constructed as an annular structure, that is, the buffer chambers 160 are arranged in the circumferential direction of the first bearing 140.
  • the radial force on the first bearing 140 may change at any time. That is, the first bearing 140 will be subjected to radial forces that change in multiple directions, and no matter which direction the radial force received by the first bearing 140 faces, the existence of the annular buffer chamber 160 enables the first bearing 140 to deform to a certain extent.
  • the rotating shaft 121 and the first bearing 140 are connected flexibly, and the first bearing 140 has a buffering effect on the radial force of the rotating shaft 121, avoiding the problem that the first bearing 140 is easily damaged due to the rigid connection between the rotating shaft 121 and the first bearing 140.
  • this embodiment explains the supporting structure of the rotating shaft 121 in the pump device 100, furthermore, as shown in Figs. 1 , 4 and 5 , the pump device 100 further comprises: a second bearing 170, the second bearing 170 is connected with the casing 110 and sleeved on the rotating shaft 121, and the second bearing 170 is located on one side of the pump portion 130 away from the first bearing 140.
  • the second bearing 170 is connected with the casing 110, and the second bearing 170 is sleeved on the rotating shaft 121, and the second bearing 170 is located on one side of the pump portion 130 away from the first bearing 140, that is, the first bearing 140 and the second bearing 170 are located on both 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.
  • the load of the pump portion 130 can be evenly shared by the rotating shaft 121, the first bearing 140 and the second bearing 170, avoiding the possible damage to the rotating shaft 121 caused by the load being concentrated on the rotating shaft 121.
  • the first bearing 140 and the second bearing 170 are sliding bearings. Compared with the form of double rolling bearings, the sliding bearings work smoothly, reliably and without noise. Under the condition of liquid lubrication, the sliding surfaces are separated by lubricating oil without direct contact, which can greatly reduce friction loss and surface wear. And the gap between the sliding bearing and the rotating shaft 121 is filled with lubricating oil, and the lubricating oil on the sliding surface will form an oil film to realize fluid lubrication. The oil film also has a certain ability to absorb vibration, which improves the service life of the first bearing 140, the second bearing 170 and the rotating shaft 121.
  • Two sliding bearings support the rotating shaft 121, the clearance of the rotating shaft 121 is small, and the position of the axis of the rotating shaft 121 can be controlled within a reasonable range.
  • only two sliding bearings are used in this embodiment, which can not only simplify the support structure, but also reduce the cost.
  • the first bearing 140 has a first bearing surface close to the rotating shaft 121
  • the second bearing 170 has a second bearing surface close to the rotating shaft 121
  • the axial height of the second bearing surface is less than or equal to the axial height of the first bearing surface, that is, not greater than it.
  • 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, and a load is also generated on the rotating shaft 121. Therefore, the first bearing 140 also needs to carry the load from the motor portion 120.
  • the second bearing surface 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 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 a minimum level.
  • a portion of an inner side wall of the second bearing 170 is recessed away from the rotating shaft 121 to form a second lubrication groove 171, which communicates with the first pressure chamber 131.
  • the second lubrication groove 171 is formed by the depression of a portion of the inner side wall of the second bearing 170 away from the rotating 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. As the rotating shaft 121 rotates, the oil in the second lubrication groove 171 will coat the surface of the rotating shaft 121.
  • the second lubrication groove 171 can play a role of short-term storage of lubricating oil; a fluid lubricating oil film can be formed between the inner wall of the second bearing 170 and the rotating shaft 121, to further ensure the lubricating performance between the rotating shaft 121 and the bearing.
  • the pump device 100 further comprises: an anti-push lubrication groove 172, provided on an end surface of the second bearing 170 close to the pump portion 130, and communicating with a shaft hole of the second bearing 170.
  • the anti-push lubrication groove 172 is arranged on the end surface of the second bearing 170 close to the pump portion 130, and the anti-push lubrication groove 172 communicates with the shaft hole of the second bearing 170.
  • the lubricating oil in the matching gap with the second bearing 170 will be sheared, and the lubricating oil will enter the anti-push lubrication groove 172 through the second bearing 170 oil groove under the action of shearing force, forming a certain speed and pressure.
  • the anti-push lubrication groove 172 is arranged on the end surface of the second bearing 170 close to the pump portion 130, and the anti-push lubrication groove 172 communicates with the second bearing 170 and the shaft hole of the second bearing 170.
  • the rotating shaft 121 will shear the lubricating oil in the matching gap between itself and the second bearing 170.
  • the lubricating oil will enter the anti-push lubrication groove 172 from the matching gap, and the lubricating oil entering the anti-push lubrication groove 172 has a certain speed and pressure at this time.
  • the end surface clearance between the second bearing 170 and the pump portion 130 is small, and the lubricating oil in the anti-push lubrication groove 172 can flow to the end surface clearance between the second bearing 170 and the pump portion 130.
  • the condition of fluid lubrication is formed between the contact end surfaces of the pump portion 130 and the second bearing 170.
  • an oil film is formed at the contact end surface between the second bearing 170 and the pump portion 130, the boundary lubrication between the second bearing 170 and the pump portion 130 is transitioned to fluid lubrication, the wear of the contact end surface between the pump portion 130 and the second bearing 170 can be greatly improved, and the power consumption can be reduced. In addition, it can reduce the running noise of the pump device 100.
  • the notch area of the anti-push lubrication groove 172 in the axial direction is larger than the groove bottom area of the anti-push lubrication groove 172.
  • the anti-push lubrication groove 172 comprises two notches with different orientations, one towards the pump portion 130 and another towards the rotating shaft 121.
  • the area of the notch toward the pump portion 130 is defined to be larger than the area of the groove bottom. That is, in the axial direction away from the pump portion 130, that is, in the top-down direction, the anti-push lubrication groove 172 has a constricted shape, that is, the groove wall of the anti-push lubrication groove 172 has an inclined shape.
  • the lubricating oil entering the anti-push lubrication groove 172 has a certain speed and pressure
  • the groove wall of the anti-push lubrication groove 172 has an inclined shape.
  • there is a convergent wedge-shaped angle between the anti-push lubrication groove 172 and the end surface clearance and the lubricating oil in the anti-push lubrication groove 172 will flow along the inclined groove wall to the end surface clearance between the pump portion 130 and the second bearing 170, that is, the lubricating oil from "big port" to "small port”.
  • the "big port” refers to the anti-push lubrication groove 172
  • the "small port” refers to the gap between the second bearing 170 and the pump portion 130.
  • the oil film between the contacting surfaces between the pump portion 130 and the second bearing 170 will generate a force F that pushes the pump portion 130 upward, and then the lubricating oil located in the end surfaces of the second bearing 170 and the pump portion 130 acts as a floating seal, which can further reduce the leakage of the end surfaces.
  • the end surface leakage of the pump device 100 accounts for 75% ⁇ 80% of the total leakage of the pump device 100. Therefore, it is very important to improve the leakage between the contacting end surfaces of the pump device 100. It is worth noting that lubricating oil has a certain viscosity.
  • the anti-push lubrication groove 172 comprises an anti-push wall
  • the anti-push wall comprises at least one anti-push segment
  • at least one anti-push segment comprises a first anti-push segment
  • the first anti-push segment extends close to the center of the anti-push lubrication groove 172.
  • the anti-push lubrication groove 172 comprises an anti-push wall; the anti-push wall is an inclined wall. In the axial direction away from the pump portion 130, that is, in the top-down direction, the anti-push wall extends close to the center of the anti-push wall.
  • the anti-push wall comprises at least one anti-push segment, at least one anti-push segment comprises a first anti-push segment, and the first anti-push segment extends in the axial direction away from the pump portion 130 and close to the center of the anti-push lubrication groove 172.
  • the first anti-push segment can be composed of at least one straight segment and at least one curved segment, and the first anti-push segment has a first end close to the pump portion 130 and a second end away from the pump portion 130.
  • the second end of the first anti-push segment extends close to the center of the anti-push lubrication groove 172. That is, if the inclined extension trend of the first anti-push segment satisfies the above-mentioned relationship, the flow of lubricating oil can be facilitated.
  • the first anti-push segment can be composed of multi-segment curved surfaces or multi-segment arcs.
  • angle ⁇ between the first anti-push segment and the axial end surface of the second bearing 170 is greater than 0° and less than 90°.
  • the axial end surface of the second bearing 170 refers to the axial end surface of the second bearing 170 close to the pump portion 130.
  • the angle between the first anti-push segment and the axial end surface satisfies 0° ⁇ 90°. Therefore, the first anti-push segment can better drain the lubricating oil into the end surface clearance between the second bearing 170 and the pump portion 130, ensuring that the lubricating oil can enter the end surface clearance through its own velocity and pressure, and is guided by the first anti-push segment, a converging wedge-shaped angle is formed between the anti-push lubrication groove 172 and the end surface clearance.
  • the lubricating oil in the anti-push lubrication groove 172 will flow along the inclined groove wall to the end surface clearance of the pump portion 130 and the second bearing 170, that is, the lubricating oil enters the "small port” from the "big port”. Therefore, the lubrication between the pump portion 130 and the second bearing 170 can be enhanced, the lubrication state between the two transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate between the two. Furthermore, the angle ⁇ between the first anti-push segment and the axial end surface of the second bearing 170 is 45°.
  • the inclined first anti-push segment can be machined on the end surface of the second bearing 170 close to the pump portion 130 by using the forming tool.
  • the longitudinal section (along the axial direction) of the anti-push lubrication groove 172 can be an inverted triangle, a semicircle, etc.
  • At least one anti-push segment further comprises a second anti-push segment, which extends axially and connects between the first anti-push segment and the groove bottom of the anti-push lubrication groove 172.
  • the at least one anti-push segment further comprises a second anti-push segment, and the second anti-push segment extends along the axial direction to be connected between the first anti-push segment and the bottom of the groove.
  • the second anti-push segment cooperates with the first anti-push segment to form an anti-push wall, thereby ensuring that the volume of the anti-push lubrication groove 172 meets the lubrication requirements. It is worth noting that, during the machining process, a straight groove is machined on the end surface of the second bearing 170 toward the pump portion 130, and then chamfering is machined, the first anti-push segment and the second anti-push segment can be formed. Through the above processing sequence, the processing difficulty of anti-push lubrication groove 172 can be reduced.
  • the number of anti-push walls is at least two.
  • the number of anti-push walls is at least two, and each anti-push wall in the at least two anti-push walls comprises at least one anti-push segment. At least one anti-push segment comprises a first anti-push segment. At least one anti-push segment further comprises a second anti-push segment. It is worth noting that the structures of at least two anti-push walls can be equal or unequal. When the number of anti-push walls is three, the structures of the three anti-push walls can be partially equal and partially unequal.
  • At least two anti-push walls include a first anti-push wall, and the first end of the first anti-push wall is connected to the inner side wall of the second bearing 170.
  • the tangent plane where the connection point between the first anti-push wall and the inner side wall of the second bearing 170 is located is the first reference plane.
  • the angle ⁇ 1 between the first anti-push wall and the first reference plane is greater than or equal to 0° and less than 90°.
  • the first end of the first anti-push wall is the start end of the first anti-push wall
  • the second end of the first anti-push wall is the termination end of the first anti-push wall.
  • the first end is connected with the inner side wall of the second bearing 170
  • the inner side wall of the second bearing 170 is the side wall of the shaft hole of the second bearing 170.
  • the tangent plane where the connection point between the first end and the second bearing 170 is located is the first reference plane
  • the angle ⁇ 1 between the first anti-push wall and the first reference plane is greater than or equal to 0° and less than 90°.
  • the rotating shaft 121 will shear the lubricating oil in the matching gap between itself and the second bearing 170, and the lubricating oil will enter the anti-push lubrication groove 172 from the matching gap under the action of the shearing force ⁇ .
  • the lubricating oil entering the anti-push lubrication groove 172 has a certain speed and pressure. Since the first anti-push wall is biased towards the rotating direction of the rotating shaft 121, the lubricating oil in the anti-push lubrication groove 172 will have shaft shearing and surface shearing.
  • a negative pressure is formed at the position of the anti-push lubrication groove 172 close to the shaft hole, to suck the lubricating oil between the rotating shaft 121 and the second bearing 170.
  • the pressure in the anti-push lubrication groove 172 is higher at the position away from the shaft hole, the lubricating oil in the anti-push lubrication groove 172 will flow into the end surface clearance between the second bearing 170 and the pump portion 130 along the inclined anti-push wall. Therefore, the lubrication between the pump portion 130 and the second bearing 170 can be enhanced, the lubrication state between the two transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate between the two.
  • the at least two anti-push walls also include a second anti-push wall, the second anti-push wall is set opposite to the first anti-push wall, and the first end of the second anti-push wall is connected to the inner side wall of the second bearing 170.
  • the tangent plane where the connection point between the second anti-push wall and the inner side wall of the second bearing 170 is located is the second reference plane, and the angle ⁇ 2 between the second anti-push wall and the second reference plane is greater than 0° and less than 90°.
  • the at least two anti-push walls also include the second anti-push wall, and the first end of the second anti-push wall is the starting end of the second anti-push wall.
  • the second end of the second anti-push wall is the termination end of the second anti-push wall, the second end is connected to the inner side wall of the second bearing 170, and the inner side wall of the second bearing 170 is the side wall of the shaft hole of the second bearing 170.
  • the tangent plane of the connection point between the first end and the second bearing 170 is the second reference plane, and the angle ⁇ 2 between the second anti-push wall and the second reference plane is greater than or equal to 0° and less than 90°.
  • the rotating shaft 121 will shear the lubricating oil in the matching gap between itself and the second bearing 170, and the lubricating oil will enter the anti-push lubrication groove 172 from the matching gap under the action of the shearing force ⁇ .
  • the lubricating oil entering the anti-push lubrication groove 172 has a certain speed and pressure. Since the second anti-push wall is biased towards the rotating direction of the rotating shaft 121, the lubricating oil in the anti-push lubrication groove 172 will have shaft shearing and surface shearing.
  • a negative pressure is formed at the position of the anti-push lubrication groove 172 close to the shaft hole, to suck the lubricating oil between the rotating shaft 121 and the second bearing 170.
  • the pressure in the anti-push lubrication groove 172 is higher at the position away from the shaft hole, the lubricating oil in the anti-push lubrication groove 172 will flow into the end surface clearance between the second bearing 170 and the pump portion 130 along the inclined anti-push wall. Therefore, the lubrication between the pump portion 130 and the second bearing 170 can be enhanced, the lubrication state between the two transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate between the two.
  • the at least two anti-push walls also include a third anti-push wall, and the third anti-push wall is respectively connected with the second end of the first anti-push wall and the second end of the second anti-push wall.
  • the at least two anti-push walls also include a third anti-push wall, and the third anti-push wall is respectively connected with the second end of the first anti-push wall and the second end of the second anti-push wall. That is, the anti-push lubrication groove 172 is composed of the first anti-push wall, the second anti-push wall and the third anti-push wall, which can facilitate the shape design of the anti-push lubrication groove 172.
  • the projection of the first anti-push wall, the second anti-push wall and the third anti-push wall on the axial end surface of the second bearing 170 can be a straight segment or a curved segment.
  • the third anti-push wall of the anti-push lubrication groove 172 is an arc-shaped wall.
  • the third anti-push wall is an arc-shaped wall, that is, the projection of the third anti-push wall on the axial end surface of the second bearing 170 is an arc-shaped segment. Since the position corresponding to the third anti-push wall is the position away from the shaft hole in the anti-push lubrication groove 172, the lubricating oil pressure in the anti-push lubrication groove 172 corresponding to this position is higher.
  • the third anti-push wall an arc-shaped wall, the flow of lubricating oil in the anti-push lubrication groove 172 can be facilitated, it can facilitate lubricating oil from the "big port” into the "small port”, and can enhance the lubrication between the pump portion 130 and the second bearing 170, the lubrication state between the two transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate between the two.
  • this embodiment explains a lubricating oil circuit of the second bearing 170, furthermore, as shown in Fig. 4 , the casing 110 comprises: a machine shell 112, surrounding the motor portion 120 and the pump portion 130 and connected with the first bearing 140; and a pump cover 113, the pump cover 113 is connected on the machine shell 112, the pump cover 113 and the machine shell 112 form the cavity 111, the pump cover 113 is connected to the second bearing 170, a portion of the pump cover 113 extends away from the pump portion 130 to form an extension portion 114 being used for forming an oil pool 115, a shaft hole of the second bearing 170 is an axial through hole, one end of the through hole is communicated with the anti-push lubrication groove 172, and another end of the through hole is used to communicate with the oil pool 115.
  • the casing 110 comprises a machine shell 112 and a pump cover 113 connected on the machine shell 112, the pump cover 113 and the machine shell 112 form a cavity 111, and the machine shell 112 surrounds outside the motor portion 120 and the pump portion 130.
  • the machine shell 112 is connected with the first bearing 140, and the pump cover 113 is connected with the second bearing 170.
  • the first bearing 140 and the machine shell 112 can be integrally formed, and the machine shell 112 and the first bearing 140 can be integrally formed.
  • the connection strength is higher; it can save space, reduce the height of the whole machine, and can reduce the difficulty of the preparation process and reduce the production cost.
  • the pump cover 113 and the second bearing 170 can be integrally formed, saving more height space, not only reducing the height of the whole machine, but also reducing the cost.
  • the extension portion 114 is formed by an extension structure of a portion of the pump cover 113 away from the pump portion 130. Therefore, the extension portion 114 and the pump cover 113 are integrally formed, and the connection strength is higher than the post-processing method.
  • the extension portion 114 is used to form an oil pool 115, which can store the lubricating oil.
  • the shaft hole on the second bearing 170 is an axial through hole, and the two ends of the through hole are connected to the anti-push lubrication groove 172 and the oil pool 115 respectively.
  • the rotating shaft 121 will shear the lubricating oil in the matching gap between itself and the second bearing 170.
  • the lubricating oil will enter the anti-push lubrication groove 172 from the matching gap (through hole) under the action of shearing force.
  • the lubricating oil entering the anti-push lubrication groove 172 has a certain speed and pressure.
  • the lubricating oil in the anti-push lubrication groove 172 will undergo shaft shearing and surface shearing, thereby forming a negative pressure in the anti-push lubrication groove 172 close to the shaft hole, to suck the lubricating oil between the rotating shaft 121 and the second bearing 170.
  • the pressure in the anti-push lubrication groove 172 is higher at the position away from the shaft hole, and the lubricating oil in the anti-push lubrication groove 172 can be better pushed into the end surface clearance between the second bearing 170 and the pump portion 130. Therefore, the lubrication between the pump portion 130 and the second bearing 170 can be enhanced, the lubrication state between the two transitions from boundary lubrication to fluid lubrication, thereby effectively reducing the wear rate between the two.
  • the oil is drawn into the anti-push lubrication groove 172 to lubricate the contact surface between the pump portion 130 and the second bearing 170, and then enters the gap between the second bearing 170 and the pump portion 130, and then enters the oil pool 115 of the low pressure area under the action of pressure difference and gravity.
  • the lubricating oil circuit of the second bearing 170 is as follows: the oil enters the gap between the second bearing 170 and the rotating shaft 121 through the oil pool 115 (through hole, second lubrication groove 171) and then enters the anti-push lubrication groove 172. Under the action of the anti-push lubrication groove 172, the oil enters the end surface clearance between the pump portion 130 and the second bearing 170, and enters the low pressure oil pool 115 under the action of pressure difference and gravity.
  • the pump cover 113 and the second bearing 170 are integrally formed. Compared with the post-processing method, the connection strength is higher; it can save space, reduce the height of the whole machine, and can reduce the difficulty of the preparation process and reduce the production cost.
  • this embodiment explains another lubricating oil circuit of the second bearing 170, furthermore, as shown in Fig. 1 , the casing 110 comprises: a machine shell 112, surrounding the motor portion 120 and the pump portion 130, and the machine shell 112 is connected with the first bearing 140; and a pump cover 113, the pump cover 113 is connected on the machine shell 112, the pump cover 113 and the machine shell 112 form the 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 open; and a communication groove, arranged on the second bearing 170 and/or the pump cover 113, and communicating the first pressure chamber 131 and the blind hole.
  • the casing 110 comprises a machine shell 112 and a pump cover 113 connected on the machine shell 112, the pump cover 113 and the machine shell 112 form a cavity 111, and the machine shell 112 surrounds outside the motor portion 120 and the pump portion 130.
  • the machine shell 112 is connected with the first bearing 140, and the pump cover 113 is connected with the second bearing 170.
  • the first bearing 140 and the machine shell 112 can be integrally formed, and the machine shell 112 and the first bearing 140 are integrally formed.
  • the connection strength is higher; it can save space, reduce the height of the whole machine, and can reduce the difficulty of the preparation process and reduce the production cost.
  • the pump cover 113 and the second bearing 170 can be integrally formed, saving more height space, not only reducing the height of the whole machine, but also reducing the cost.
  • the shaft hole of the second bearing 170 is a blind hole with one end open, and the communication groove is arranged on the second bearing 170 and/or the pump cover 113, and the communication groove is used to communicate with the first pressure chamber 131 and the blind hole.
  • the lubricating oil circuit 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 (high pressure chamber) through the communication groove and then returns to the low pressure area through the gap between the second bearing 170 and the pump portion 130, where the low pressure area specifically refers to the oil inlet 181 and the second pressure chamber 132.
  • the pump portion 130 comprises: a first rotation member 133, matched with the rotating shaft 121; and a second rotation member 134, the second rotation member 134 is arranged on an outside of the first rotation member 133, and the first rotation member 133 can drive the second rotation member 134 to rotate, the second rotation member 134 and the first rotation member 133 form the first pressure chamber 131 and the second pressure chamber 132, the pump device 100 further comprises: an oil inlet 181, arranged on the pump cover 113 and/or the second bearing 170 along an axial direction, and the oil inlet 181 communicating with the second pressure chamber 132; an oil outlet 182, arranged on the pump cover 113 and the second bearing 170 along an radial direction, and the oil outlet 182 communicating with the first pressure chamber 131 of the pump portion 130.
  • the pump portion 130 comprises a first rotation member 133 and a second rotation member 134
  • the first rotation member 133 is matched with the rotating shaft 121
  • the second rotation member 134 is arranged outside the first rotation member 133
  • the first rotation member 133 can drive the second rotation member 134 to rotate.
  • the rotating shaft 121 can drive the second rotation member 134 to run through the first rotation member 133.
  • the first pressure chamber 131 and the second pressure chamber 132 are formed by setting the first rotation member 133 and the second rotation member 134, and the first pressure chamber 131 is a high pressure chamber, and the second pressure chamber 132 is a low pressure chamber.
  • the first rotation member 133 is an inner gear
  • the second rotation member 134 is an outer gear
  • the pump portion 130 is a gear pump.
  • the former pair of teeth has not yet been disengaged, and the latter pair of teeth has entered meshing, and each inner tooth surface is in contact with the outer tooth surface to form a closed cavity, with the rotation of the inner gear, the volume of the closed cavity 111 will change, and if the unloading channel cannot be connected, the trapped oil volume will be formed. Due to the small compressibility of the liquid, when the trapped oil volume changes from large to small, the liquid in the trapped oil volume is squeezed, and the pressure rises sharply, which greatly exceeds the working pressure of the gear pump.
  • the liquid in the trapped oil volume is also forcibly squeezed out from all leakable gaps, that the rotating shaft 121 and bearing will bear a large impact load. This will increase power loss and cause oil to heat up causing noise and vibrations that reduce the smoothness and life of the gear pump.
  • a vacuum is formed, which causes the air dissolved in the liquid to separate out and generate bubbles, which bring about hazards such as cavitation, noise, vibration, flow and pressure pulsation.
  • the method of eliminating the trapped oil is to open the unloading groove on both ends of the gear, when the closed volume decreases, the unloading groove communicates with the oil pressure chamber, and when the closed volume increases; it communicates with the oil suction chamber through the unloading groove.
  • the inner gear meshes with the tooth profile of the conjugate curve of the outer gear, and each tooth is in contact with each other, driving the outer gear to rotate in the same direction.
  • the inner gear divides the inner cavity of the outer gear into multiple working chambers. Due to the offset of the center of the inner and outer gears, the volumes of the multiple working chambers change with the rotation of the rotor 122, and a certain vacuum is formed in the area where the volume increases.
  • the oil inlet 181 is set at this position, the pressure increases in the area where the volume decreases, and the oil outlet 182 is set here accordingly.
  • the pump device 100 further comprises an oil inlet 181 and an oil outlet 182, the oil inlet 181 is arranged on the pump cover 113 and/or the second bearing 170 along an axial direction, and the oil inlet 181 communicates with the second pressure chamber 132. Since the second pressure chamber 132 is a low pressure chamber, there is a pressure difference with the outside of the chamber, so the oil will enter the second pressure chamber 132 through the oil inlet 181.
  • the oil outlet 182 is arranged on the pump cover 113 and the second bearing 170 along an radial direction, and the oil outlet 182 communicates with the first pressure chamber 131.
  • the main oil circuit of the pump device 100 is: the negative pressure that can be generated at the second pressure chamber 132 and the oil inlet 181 and 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), and then the oil entering the second pressure chamber 132 enters the high pressure chamber under the action of the first rotation member 133 and the second rotation member 134 to be pressurized, and the pressurized oil is discharged through the oil outlet 182.
  • 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 and the teeth of the first rotation member 133 and the second rotation member 134 are connected as soon as possible, before the inner gear and the outer gear form the maximum volume, the gear volume cavity is always communicated with the oil inlet 181, and the oil filling time should be prolonged as much as possible, the volume cavity between the inner and outer teeth is filled with oil, thereby ensuring the oil absorption.
  • the oil outlet 182 should also be connected to the high-pressure oil between the teeth as soon as possible, to reduce the excessive compression work between the teeth, and close as late as possible to make full use of the inertia of the fluid to drain the oil between the teeth, thereby improving the volumetric efficiency of the inner gear oil pump.
  • the inner and outer gears form the maximum volume, they cannot communicate with the oil inlet 181 to avoid affecting the volumetric efficiency of the pump device 100 at low speed.
  • the motor portion 120 further comprises: a rotor 122, connected with the rotating shaft 121; and a stator 123, sleeved on an outside of the rotor 122, the stator 123 including a stator core and a stator winding, and the stator winding is arranged on the stator core
  • the pump device 100 further comprises: a controller 190, arranged on one side of the motor portion 120 away from the pump portion 130, and connected on the casing 110 and located in the cavity 111, and one end of the stator winding is electrically connected to the controller 190.
  • the motor portion 120 further comprises a rotor 122 and a stator 123.
  • the rotor 122 and the rotating shaft 121 are connected, in some embodiments, the rotor 122 and the rotating shaft 121 can be coaxially arranged, and the matching mode of the rotor 122 and the rotating shaft 121 can be interference fit.
  • the rotor 122 and rotating shaft 121 can be set on different shafts, but the two are connected by transmission, which can be flexibly set according to the actual situation.
  • the stator 123 is sleeved on the outer side of the rotor 122, the stator 123 comprises the stator core and the stator winding, and the stator winding is set on the stator core.
  • the pump device 100 further comprises a controller 190, and the controller 190 is arranged on one side of the motor portion 120 away from the pump portion 130, that is, the controller 190 is arranged at a position of the motor portion 120 away from the pump portion 130. Since the vibration near the pump portion 130 is more obvious during the working process, and the load is larger, the controller 190 is far away from the pump portion 130, which can protect the controller 190 to a certain extent and improve the service life of the controller 190.
  • controller 190 is connected on the casing 110 and located in the cavity 111, and the end of the stator winding is electrically connected to the controller 190.
  • the controller 190 controls the current of the stator winding in the stator 123 to change according to a certain law, thereby controlling the stator 123 to generate a changing excitation magnetic field.
  • the rotor 122 rotates under the action of the excitation magnetic field, thereby driving the first rotation member 133 in the pump portion 130 to rotate through the rotating shaft 121, thereby making the second rotation member 134 moves.
  • the volume of the compression cavity formed between the first rotation member 133 and the second rotation member 134 changes.
  • the working medium entering the compression chamber is pressed out to the oil outlet 182 to generate flow power.
  • the embodiment of the second aspect of the present invention provides a vehicle 200, including a pump device 100 in any one of the above-mentioned embodiments. Since the vehicle 200 provided by the present invention comprises the pump device 100 in any one of the above-mentioned embodiments, it has the beneficial effects of any one of the above-mentioned embodiments, which will not be repeated here.
  • the vehicle 200 can be a new energy vehicle.
  • New energy vehicles include pure electric vehicles, extended-range electric vehicles, hybrid electric vehicles, fuel cell electric vehicles, hydrogen engine vehicles, etc.
  • the vehicle 200 also can be a traditional fuel vehicle.
  • the vehicle 200 comprises a vehicle body 210 and an engine 220.
  • the pump device 100 and the engine 220 are both arranged in the vehicle body 210, and the engine 220 comprises a mounting seat 221.
  • the mounting seat 221 is connected with the extension portion 114 of the pump device 100, the oil pool 115 is formed by the cooperation of the mounting seat 221 and the extension portion 114, and then the oil pool 115 can be communicated with the oil source of the engine 220 to realize the oil passage.
  • the engine 220 when the vehicle 200 is a new energy vehicle, the engine 220 is an electric motor; when the vehicle 200 is a fuel vehicle, the engine 220 is a fuel engine.
  • connection may be a fixed connection, a removable connection or an integral connection; and “connected” may refer to direct connection or indirect connection through an intermediary.
  • orientation or position relationships indicated by the terms “upper”, “lower”, “left”, “right”, “front”, “back” and the like are the orientation or position relationships based on what is shown in the drawings, are merely for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or unit referred to must have a particular direction and is constructed and operated in a specific orientation, and thus cannot be understood as the limitation of the present invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
EP21863432.7A 2020-09-03 2021-07-30 Dispositif de pompe et véhicule Pending EP4056853A4 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CN202010913992.2A CN114135384A (zh) 2020-09-03 2020-09-03 泵装置和车辆
CN202021898979.6U CN213743646U (zh) 2020-09-03 2020-09-03 泵装置和车辆
PCT/CN2021/109591 WO2022048364A1 (fr) 2020-09-03 2021-07-30 Dispositif de pompe et véhicule

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EP4056853A1 true EP4056853A1 (fr) 2022-09-14
EP4056853A4 EP4056853A4 (fr) 2023-06-28

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JP (1) JP7350180B2 (fr)
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WO2023174888A1 (fr) * 2022-03-16 2023-09-21 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Pompe à huile pour un véhicule automobile

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JP2014062482A (ja) 2012-09-20 2014-04-10 Asmo Co Ltd 電動ポンプ
JP2014173587A (ja) * 2013-03-13 2014-09-22 Hitachi Automotive Systems Ltd 内接歯車ポンプ
JP6227445B2 (ja) 2014-03-04 2017-11-08 日立オートモティブシステムズ株式会社 電動オイルポンプ
JP6369194B2 (ja) 2014-07-23 2018-08-08 株式会社ジェイテクト 電動ポンプユニット
DE102015015863A1 (de) * 2015-12-09 2017-06-14 Fte Automotive Gmbh Elektromotorisch angetriebene Flüssigkeitspumpe
JP2017218960A (ja) 2016-06-07 2017-12-14 アイシン精機株式会社 オイルポンプ
CN206668608U (zh) * 2017-04-05 2017-11-24 涌镇液压机械（上海）有限公司 一种内插式电机泵组降噪结构
CN106948982A (zh) * 2017-04-29 2017-07-14 江苏新海科技发展有限公司 一种行星齿轮柴油泵
DE102018104015A1 (de) * 2018-02-22 2019-08-22 Nidec Gpm Gmbh Kühlmittelpumpe mit optimierter Lageranordnung und verbessertem Wärmehaushalt
CN110529425A (zh) * 2019-08-16 2019-12-03 中国航发北京航科发动机控制系统科技有限公司 一种用于高转速离心泵的润滑结构
CN110469502B (zh) * 2019-09-05 2021-04-13 兰州理工大学 一种气隙非浸油式内啮合齿轮电机泵
CN213743646U (zh) * 2020-09-03 2021-07-20 安徽威灵汽车部件有限公司 泵装置和车辆

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023174888A1 (fr) * 2022-03-16 2023-09-21 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Pompe à huile pour un véhicule automobile

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JP7350180B2 (ja) 2023-09-25

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