CN213899286U - Pump device and vehicle - Google Patents

Abstract

The utility model provides a pump unit and vehicle, wherein, pump unit includes: a rotating shaft; the pivot is located to the cover to the bearing, is equipped with the cell body on the axial terminal surface of bearing, and the cell body takes place deformation for bearing tip position and provides the space for pivot and bearing are flexible contact, have reduced the wearing and tearing speed of bearing, thereby have effectively reduced the spoilage of bearing, have thoroughly solved pivot and bearing rigid connection and have caused the easy problem of damaging of bearing.

Description

Pump device and vehicle

Technical Field

The utility model belongs to the technical field of the pump unit, particularly, relate to a pump unit and a vehicle.

Background

When the bearing supports the shaft, the shaft is stressed to cause the shaft to bend along the axial direction, the contact positions of the two axial end faces of the bearing and the shaft are the maximum load area of the bearing, and the bearing is easy to grind and damage due to large local pressure at the load point.

SUMMERY OF THE UTILITY MODEL

The utility model discloses aim at solving one of the technical problem that exists among the prior art or the correlation technique.

In view of this, a first aspect of the present invention provides a pump apparatus, including: a rotating shaft; the bearing is sleeved on the rotating shaft, and a groove body is arranged on the axial end face of the bearing.

The utility model provides a pump unit includes pivot and bearing, and the bearing housing is located in the pivot to play the supporting role to the pivot, when the pivot drove the load and rotates, the pivot along radial removal and change with the clearance of bearing, the great condition of bearing partial pressure can appear this moment. Specifically, the pressure applied to the two axial ends of the bearing is the largest, an oil film exists between the bearing and the rotating shaft, when the rotating shaft moves along the radial direction, the thickness of the oil film between the rotating shaft and the end part of the bearing is reduced, and when the thickness of the oil film is smaller than a critical value, the rotating shaft and the bearing are abraded. In order to avoid the axial tip of pivot and bearing to take place wearing and tearing and the condition of damage for a long time takes place, the utility model discloses in set up the cell body on the axial terminal surface of bearing, when the axial tip of bearing receives great pressure, the position that the bearing is located axial tip can take place deformation, the cell body takes place deformation for bearing tip position promptly and provides the space for pivot and bearing are the flexonics, the increase contact surface is in order to reduce the face pressure, make the oil film thickness increase between pivot and the bearing, the wearing and tearing speed of bearing has been reduced, thereby effectively reduced the spoilage of bearing, thoroughly solved pivot and bearing rigid connection and caused the easy problem of damaging of bearing.

In addition, according to the utility model provides a pump device among the above-mentioned technical scheme, can also have following additional technical characteristics:

in one possible design, the trough is constructed as an annular structure arranged around the axis of rotation.

In this design, a structure of cell body has specifically been injectd, the cell body is constructed for the loop configuration, that is, all be provided with the cell body in the circumference of bearing, when the pivot drives the load rotation, the radial force direction that the pivot received can change at any time, the pivot can receive the radial force of a plurality of direction changes promptly, and no matter the radial force that the pivot received is to which direction, when the pivot moves towards the bearing, the existence of loop configuration makes the bearing can take place deformation, thereby make pivot and bearing flexonics, increase the contact surface is in order to reduce the face pressure, the bearing plays the cushioning effect to the radial force of pivot, solve pivot and bearing rigid connection and cause the problem that the bearing damaged easily, when the radial force that the pivot received changes, the bearing also can play the cushioning effect to the pivot, further reduce the spoilage of bearing.

In one possible design, the groove body is provided in plurality, and the plurality of groove bodies are arranged at intervals along the circumferential direction of the bearing.

In this design, another kind of structure of cell body has specifically been injectd, the cell body is a plurality of and sets up along the circumference interval of bearing, when the pivot drives the load rotation, the radial force direction that the pivot received can change at any time, the pivot can receive the radial force of a plurality of direction changes promptly, quantity through increasing the cell body, make the bearing all play the cushioning effect to the radial force of a plurality of directions, avoid pivot and bearing rigid connection and cause the easy problem of damaging of bearing, when the radial force that the pivot received changes, the bearing also can play the cushioning effect to the pivot, further reduce the spoilage of bearing.

Two adjacent groove bodies in the plurality of groove bodies are not penetrated, so that the structure between the two adjacent groove bodies can ensure the structural stability of the bearing, and the support stability of the bearing on the rotating shaft is improved.

In one possible design, two adjacent channels of the plurality of channels are in communication with each other.

In this design, in order to reduce the frictional force between pivot and the bearing, can let in lubricating oil between pivot and the bearing, thereby reduce the wearing and tearing speed of pivot and bearing, when lubricating oil flows to the axial end face of bearing, partial fluid can flow to the cell body in, in order to avoid fluid to pile up the cell body for a long time, with two adjacent cell bodies intercommunication, for example set up the through-hole between two adjacent cell bodies, thereby make fluid in the cell body can flow to adjacent cell body in, realize fluid from the high pressure position to the function that the low pressure position flows.

In one possible design, the open area of the tank body is greater than the tank floor area of the tank body.

In this design, specifically limited the cell body shape, the cell body is the shape that the opening is big and the tank bottom is little, or the cell body is constructed for flaring form, when the pivot moves towards the bearing, the pressure that the bearing tip received is the biggest, the power that the tip that is close to the bearing more receives promptly is big more, so set up the cell body into flaring form, make the tip that is close to the cell body more, the section of seting up of cell body is big more, make the bearing tip that receives big power can produce bigger deformation, take place deformation for the bearing tip department of bearing and reserve bigger space, make the bearing be difficult for wearing and tearing to appear, further reduce the spoilage of bearing.

In one possible design, the tank comprises: the first wall surface is the wall surface of the groove body close to the rotating shaft, and the distance between the first wall surface of the groove body and the rotating shaft is increased from the opening of the groove body to the groove bottom of the groove body.

In the design, the shape of the first wall surface is specifically limited, the first wall surface is a wall surface close to the rotating shaft in the groove body, the first wall surface is arranged in an inclined mode relative to the axial direction of the rotating shaft, the distance between the first wall surface and the rotating shaft is smaller at the opening of the groove body, and the distance between the first wall surface and the rotating shaft is larger at the position of the groove body. This also makes between the tank bottom of first wall and cell body not the right angle structure, and the bearing is made by aluminum alloy material usually, when the tip of pivot and bearing offsets, can make the bearing take place to deform, the contained angle between the tank bottom of first wall and cell body changes promptly, if be the right angle structure between the tank bottom of first wall and cell body, the condition of stress concentration can appear in the junction of the tank bottom of first wall and cell body, when the bearing received the pressure of pivot, the bearing was followed the connection structure department between the tank bottom of first wall and cell body easily and is broken. The groove bottom of the groove body is generally parallel to the end face of the bearing, and the first wall face is arranged in an inclined mode relative to the axial direction of the rotating shaft, so that the first wall face and the groove bottom of the groove body are not of a right-angle structure, breakage of a connecting structure between the first wall face and the groove bottom of the groove body due to stress concentration is avoided, and the damage rate of the bearing is effectively reduced.

In one possible design, the tank comprises: the second wall surface is arranged opposite to the first wall surface, and the distance between the second wall surface and the rotating shaft is reduced from the opening of the groove body to the groove bottom of the groove body.

In this design, specifically limited the shape of second wall, the second wall is the wall of keeping away from the pivot in the cell body, and the second wall sets up for the axial slope of pivot, and the interval of second wall and pivot is great at the opening part of cell body, and the interval of second wall and pivot is located the tank bottom department of cell body less. It can be understood that, by the opening side of cell body to the tank bottom side of cell body, the interval increase of first wall and pivot, the clearance of second wall and pivot reduces, and at the ascending cross-section of bearing axle, the cell body is constructed for the back taper, processes the back to the cell body, and the cell body of back taper is favorable to the drawing die, improves the processing convenience to the cell body.

In one possible embodiment, the first wall and/or the second wall comprise at least one flat or curved section.

In this design, by the opening side of cell body to the tank bottom side of cell body, first wall can be one section plane or multistage plane, as long as the open area of cell body is greater than the groove bottom area of cell body, first wall is one section plane or multistage plane, and the homoenergetic makes the bearing play the cushioning effect to the radial force that receives.

Similarly, from the opening side of the groove body to the groove bottom side of the groove body, the second wall surface can be a section of plane or a plurality of sections of planes, and as long as the opening area of the groove body is larger than the groove bottom area of the groove body, the second wall surface is a section of plane or a plurality of sections of planes, the bearing can play a role in buffering the received radial force.

In one possible design, a chamfer structure is formed between the wall surface of the groove body and the axial end surface of the bearing; and/or a chamfer angle structure is formed between the first wall surface and the groove bottom of the groove body and between the second wall surface and the groove bottom of the groove body.

In the design, when the groove body is machined, the chamfer structure can be machined between the wall surface of the groove body and the axial end surface of the bearing and between the first wall surface and the groove bottom of the groove body, and the chamfer structure can avoid structural defects on the surface of the bearing. Moreover, the chamfer structures are arranged at the connecting positions of the first wall surface and the second wall surface and the groove bottom of the groove body, so that the connecting positions of the first wall surface and the second wall surface and the groove bottom of the groove body are in smooth transition, the stress concentration at the connecting positions is avoided, the fracture of the bearing at the connecting positions of the first wall surface and the second wall surface and the groove bottom of the groove body is avoided, and the damage rate of the bearing is effectively reduced.

In one possible design, the pump device further comprises: the bearing divides a cavity enclosed by the shell into a pump cavity and a motor cavity; the pump part is connected to the shell and is positioned in the pump cavity; the motor part is connected to the shell, and the motor part is positioned in the motor cavity; and the sealing element is arranged on the axial end face of the bearing, which deviates from the pump part, and is positioned in the motor cavity, and the sealing element is sleeved on the rotating shaft.

In this design, the cavity that the bearing encloses the casing is separated for pump chamber and motor chamber, is used for holding pump portion in the pump chamber, is used for holding motor portion in the motor chamber, and pump portion and motor portion all connect on the casing for pump portion and motor portion all are difficult for relative casing to rock, improve the stability of pump portion and motor portion during operation. The sealing member is the oil blanket, and the sealing member is installed on the bearing, and the pivot is located to the sealing member cover, and the oil blanket is isolated with motor chamber and pump chamber to make working medium can not flow into the motor intracavity, can not influence the normal use of parts such as stator, rotor, control panel in the motor chamber, need not additionally set up other structures in the motor chamber and receive the corruption in order to guarantee that the spare part in the motor chamber, make pump unit's sealing performance better, the structure is simpler simultaneously, is favorable to reduce cost.

In one possible design, a portion of the bearing extends away from the pump section to create a mounting location in which the seal is disposed.

In the design, a part of the first bearing forms a mounting position for mounting the sealing element, so that the mounting accuracy of the sealing element can be ensured, and the bearing is simple to assemble, good in sealing performance and low in cost. One side that the installation position deviates from the pump chamber is farther away from the pump chamber than one side that the sealing member deviates from the pump chamber for the whole accommodations of sealing member improve the installation stability of sealing member in the installation position, avoid sealing member and installation position separation.

In one possible design, the pump section includes: the first rotating piece is matched with the rotating shaft; the second rotating part is arranged on the outer side of the first rotating part, the first rotating part can drive the second rotating part to rotate, the second rotating part and the first rotating part construct a compression cavity, the compression cavity comprises a first pressure cavity and a second pressure cavity, and the pressure borne by the first pressure cavity is greater than the pressure borne by the second pressure cavity; along the axial of pivot, be equipped with the clearance between bearing and the sealing member in order to form and cross the sap cavity, cross the first pressure chamber of sap cavity intercommunication and second pressure chamber.

In this design, the first and second rotating members form a compression chamber, and the compression chamber includes a first pressure chamber and a second pressure chamber, the first pressure chamber being subjected to a pressure greater than the second pressure chamber, i.e., the first pressure chamber serves as a high pressure chamber and the second pressure chamber serves as a low pressure chamber. Because the pressure that first pressure chamber bore is great for fluid in the first pressure chamber can flow to crossing the sap cavity, and fluid can lubricate pivot and bearing when flowing to crossing the sap cavity by first pressure chamber, reduces the rate of wear of pivot and bearing. The fluid of crossing the hydraulic chamber can flow to the second pressure chamber, avoids fluid to pile up in crossing the hydraulic chamber and causes the condition emergence that the sealing member was pushed away from the installation position, improves the sealing stability of sealing member.

In one possible design, a groove is provided on the end face of the bearing facing the seal, which groove communicates with the liquid chamber.

In this design, can all set up the cell body at the terminal surface at the axial both ends of bearing, the utility model discloses in set up the cell body on the axial terminal surface of bearing towards the sealing member, the cell body communicates with crossing the sap cavity moreover, and when fluid flowed clearance department between bearing and the sealing member, it was internal that fluid also can the flow groove. The sealing element is located at the groove body, the distance between the sealing element and the bearing is large, the flow cross-sectional area of the liquid passing cavity is increased, and the flow cross-sectional area of the liquid passing cavity is increased, so that the oil pressure in the liquid passing cavity can be reduced, the oil is difficult to push the sealing element away from the installation position, a gap between the sealing element and the installation position is avoided, and the sealing element is guaranteed to play a role in stably sealing.

In one possible design, the pump device further comprises: the lubricating groove is arranged on the inner side wall of the bearing, and two ends of the lubricating groove are respectively communicated with the first pressure cavity and the liquid passing cavity; and the oil return channel is arranged on the bearing and/or the shell, and two ends of the oil return channel are respectively communicated with the second pressure cavity and the liquid passing cavity.

In this design, fluid in the first pressure chamber can flow into through the fluid cavity through the lubrication groove, and fluid can lubricate bearing and pivot, reduces the wearing and tearing speed of pivot and bearing. In order to enable the oil to better flow between the rotating shaft and the bearing, a liquid clearance needs to be arranged between the rotating shaft and the bearing, specifically, a lubricating groove is formed in the bearing, the lubricating groove does not need to be formed in the rotating shaft, damage to the structure of the rotating shaft is avoided, and the structural stability of the rotating shaft is ensured. Because the pressure that first pressure chamber bore is great, fluid in the first pressure chamber can flow out and flow into through the lubrication groove and cross the sap cavity, and the fluid of crossing in the sap cavity passes through oil return passage and flows into the second pressure chamber. The oil return passage is formed between the bearing and the shell, so that the oil return passage is formed on the bearing or the shell and cannot influence the structural stability of the rotating shaft, the oil return passage can be processed on the bearing or the shell, the oil return passage can also be processed between the bearing and the shell, and through the arrangement of the oil return passage, oil in the liquid passing cavity can flow into the second pressure cavity, the situation that the sealing element is pushed away from the installation position due to accumulation of the oil in the liquid passing cavity is avoided, and the sealing stability of the sealing element is ensured.

In one possible design, the radial dimension of the throughflow cross section of the oil return channel is greater than or equal to 1 mm.

In this design, oil return channel's size has specifically been injectd, when oil return channel through-flow cross-section's radial dimension is less, the outflow speed of crossing the fluid in the fluid chamber is slower, the condition of crossing the pressure crescent in the fluid chamber appears easily, avoid crossing the great and condition emergence that causes the sealing member to break away from the installation position of pressure in the fluid chamber, the radial dimension of the through-flow cross-section of injecing oil return channel is greater than or equal to 1 millimeter, make the fluid of crossing the fluid intracavity can flow out fast, oil return channel has played the effect of pressure release, effectively avoid the sealing member to break away from the installation position, improve the sealing stability of sealing member.

A second aspect of the present invention provides a vehicle, including: the pump device in any of the above designs, therefore the present invention provides a vehicle having all the benefits of the pump device provided in any of the above technical solutions.

The vehicle further includes a vehicle body into which the pump device is mounted.

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

Drawings

The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:

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

fig. 2 shows a schematic structural view of a pump device according to another embodiment of the present invention;

fig. 3 shows a schematic structural view of a pump device according to a further embodiment of the present invention;

fig. 4 shows a schematic structural diagram of a vehicle according to an embodiment of the present invention.

Wherein, the correspondence between the reference numbers and the part names in fig. 1 to 4 is:

100 pump devices, 110 pump parts, 111 first rotating parts, 112 second rotating parts, 113 compression cavities, 114 first pressure cavities, 115 second pressure cavities, 120 motor parts, 130 shells, 140 cavities, 150 bearings, 1510 groove bodies, 1510a first wall surfaces, 1510b second wall surfaces, 1510c groove bottoms, 1512 lubricating grooves, 1514 oil return channels, 152 rotating shafts, 170 sealing parts, 171 mounting positions, 180 liquid passing cavities, 200 vehicles, 210 vehicle bodies and 220 engines.

Detailed Description

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

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

Pump devices provided according to some embodiments of the present invention are described below with reference to fig. 1 to 4.

The first embodiment is as follows:

referring to fig. 1 and 2, a first aspect of the present invention provides a pump apparatus 100, including: the bearing 150 is sleeved on the rotating shaft 152, and a groove 1510 is arranged on the axial end face of the bearing 150.

The utility model provides a pump unit 100 includes pivot 152 and bearing 150, and bearing 150 cover is located on the pivot 152 to play the supporting role to pivot 152, when pivot 152 drives the load rotation, pivot 152 along radial movement and with bearing 150's clearance change, the great condition of bearing 150 local pressure can appear this moment. Specifically, the pressure applied to the two axial ends of the bearing 150 is the greatest, an oil film exists between the bearing 150 and the rotating shaft 152, and when the rotating shaft 152 moves in the radial direction, the thickness of the oil film at the ends of the rotating shaft 152 and the bearing 150 decreases, and when the thickness is smaller than a critical value, the rotating shaft 152 and the bearing 150 are worn. In order to avoid the condition that the axial tip of pivot 152 and bearing 150 takes place to wear and damage for a long time, the utility model discloses in offer cell body 1510 on bearing 150's axial terminal surface, when bearing 150's axial tip received great pressure, bearing 150 is located the position of axial tip and can takes place deformation, cell body 1510 takes place deformation for bearing 150 tip position and provides the space promptly, make pivot 152 and bearing 150 be flexible contact, the increase contact surface is in order to reduce the face pressure, make the oil film thickness increase between pivot 152 and the bearing 150, the wearing and tearing speed of bearing 150 has been reduced, thereby effectively reduced bearing 150's spoilage, thoroughly solved pivot 152 and bearing 150 rigid connection and caused the easy problem of damaging of bearing 150.

The pump device 100 is an oil pump, and specifically, the oil pump is an electronic oil pump.

Example two:

in a specific embodiment based on the first embodiment, as shown in fig. 1 and 2, the groove 1510 is configured as an annular structure disposed around the rotation shaft 152.

In this embodiment, a structure of the groove 1510 is specifically defined, the groove 1510 is configured as an annular structure, that is, the groove 1510 is disposed on the circumference of the bearing 150, when the rotating shaft 152 rotates with a load, the direction of the radial force applied to the rotating shaft 152 may change at any time, that is, the rotating shaft 152 may be applied with a radial force with multiple directions, and no matter which direction the radial force applied to the rotating shaft 152 is directed, when the rotating shaft 152 moves towards the bearing 150, the bearing 150 can deform due to the existence of the annular groove 1510, so that the rotating shaft 152 and the bearing 150 flexibly connect, the contact surface is increased to reduce the surface pressure, the bearing 150 buffers the radial force of the rotating shaft 152, the problem that the bearing 150 is easily damaged due to the rigid connection between the rotating shaft 152 and the bearing 150 is solved, when the radial force applied to the rotating shaft 152 changes, the bearing 150 can also buffer the rotating shaft 152, further reducing the rate of damage to the bearing 150.

In another specific embodiment based on the first embodiment, the number of the grooves 1510 is multiple, and the multiple grooves 1510 are arranged at intervals along the circumferential direction of the bearing 150.

In this embodiment, another structure of the groove 1510 is specifically defined, the groove 1510 is multiple and is disposed at intervals along the circumferential direction of the bearing 150, when the rotating shaft 152 drives the load to rotate, the direction of the radial force applied to the rotating shaft 152 may change at any time, that is, the rotating shaft 152 may receive the radial force varying in multiple directions, by increasing the number of the grooves 1510, the bearing 150 can buffer the radial force in multiple directions, thereby avoiding the problem that the bearing 150 is easily damaged due to the rigid connection between the rotating shaft 152 and the bearing 150, and when the radial force applied to the rotating shaft 152 changes, the bearing 150 can also buffer the rotating shaft 152, thereby further reducing the damage rate of the bearing 150.

Adjacent two grooves 1510 of the plurality of grooves 1510 do not penetrate through each other, so that the structural stability of the bearing 150 can be ensured by the structure between the adjacent two grooves 1510, and the support stability of the bearing 150 on the rotating shaft 152 is improved.

Further, adjacent two grooves 1510 of the plurality of grooves 1510 communicate with each other. In order to reduce the friction force between the rotating shaft 152 and the bearing 150, lubricating oil can be introduced between the rotating shaft 152 and the bearing 150, so that the wear speed of the rotating shaft 152 and the bearing 150 is reduced, when the lubricating oil flows to the axial end face of the bearing 150, part of the oil can flow into the grooves 1510, in order to avoid long-time accumulation of the oil in the grooves 1510, two adjacent grooves 1510 are communicated, for example, a through hole is formed between two adjacent grooves 1510, so that the oil in the grooves 1510 can flow into the adjacent grooves 1510, and the function of flowing the oil from a high pressure level to a low pressure level is realized.

Example three:

as shown in fig. 1, 2 and 3, in the above embodiment, the opening area of the groove 1510 is larger than the area of the groove bottom 1510c of the groove 1510.

In this embodiment, the shape of the groove 1510 is specifically defined, the groove 1510 has a large opening and the groove bottom 1510c is small, or the groove 1510 is configured to be flared, when the rotating shaft 152 moves towards the bearing 150, the pressure applied to the end of the bearing 150 is the largest, that is, the force applied to the end closer to the bearing 150 is the larger, so the groove 1510 is configured to be flared, the opening section of the groove 1510 is larger closer to the end of the groove 1510, the end of the bearing 150 subjected to the larger force can be deformed more, and a larger space is left for the deformation at the end of the bearing 150, so that the bearing 150 is not easily worn, the damage rate of the bearing 150 is further reduced, and the flaring of the groove 1510 facilitates the demolding function, the convenience of the demolding process is improved, and the convenience of processing of the groove 1510 is improved.

Further, the groove 1510 includes a first wall 1510a, the first wall 1510a is a wall of the groove 1510 close to the rotation axis 152, and a distance between the first wall 1510a of the groove 1510 and the rotation axis 152 increases from the opening of the groove 1510 to the groove bottom 1510c of the groove 1510.

Specifically, the shape of the first wall 1510a is defined, the first wall 1510a is a wall surface of the groove 1510 close to the rotation axis 152, the first wall 1510a is disposed obliquely with respect to the axial direction of the rotation axis 152, the distance between the first wall 1510a and the rotation axis 152 is smaller at the opening of the groove 1510, and the distance between the first wall 1510a and the rotation axis 152 is larger at the groove bottom 1510 c. This is to say, the first wall 1510a and the bottom 1510c of the groove 1510 are not in a right-angle structure, and the bearing 150 is usually made of an aluminum alloy material, when the rotating shaft 152 abuts against the end of the bearing 150, the bearing 150 is deformed, that is, the included angle between the first wall 1510a and the bottom 1510c of the groove 1510 changes, if the first wall 1510a and the bottom 1510c of the groove 1510 are in a right-angle structure, a stress concentration may occur at the connection between the first wall 1510a and the bottom 1510c of the groove 1510, and when the bearing 150 is pressed by the rotating shaft 152, the bearing 150 is easily broken along the connection between the first wall 1510a and the bottom 1510c of the groove 1510. The groove bottom 1510c of the groove body 1510 is generally parallel to the end surface of the bearing 150, and the first wall surface 1510a is disposed obliquely with respect to the axial direction of the rotating shaft 152, so that the first wall surface 1510a and the groove bottom 1510c of the groove body 1510 are not in a right-angle structure, and the fracture of the connecting structure between the first wall surface 1510a and the groove bottom 1510c of the groove body 1510 due to stress concentration is avoided, thereby effectively reducing the damage rate of the bearing 150.

Further, the groove 1510 includes a second wall 1510b, the second wall 1510b is disposed opposite to the first wall 1510a, and a distance between the second wall 1510b and the rotation axis 152 decreases from the opening of the groove 1510 to the groove bottom 1510c of the groove 1510.

The shape of the second wall 1510b is specifically defined, the second wall 1510b is a wall surface of the groove 1510 far away from the rotation axis 152, the second wall 1510b is inclined with respect to the axial direction of the rotation axis 152, the distance between the second wall 1510b and the rotation axis 152 is larger at the opening of the groove 1510, and the distance between the second wall 1510b and the rotation axis 152 is smaller at the groove bottom 1510c of the groove 1510. It can be understood that, from the opening side of the groove body 1510 to the groove bottom 1510c side of the groove body 1510, the distance between the first wall 1510a and the rotating shaft 152 increases, the gap between the second wall 1510b and the rotating shaft 152 decreases, and the groove body 1510 is configured in an inverted cone shape in the axial section of the bearing 150, and after the groove body 1510 is machined, the inverted cone-shaped groove body 1510 facilitates the drawing and improves the machining convenience of the groove body 1510.

And the liquid passing cavity is timely decompressed to ensure the normal work of the liquid passing cavity. The rotating shaft 152 can deform and incline when running under the action of load, so that the pressure of the two end surfaces of the bearing 150 is maximum; a tapered cavity is arranged in the liquid passing cavity, the first wall surface 1510a of the tapered cavity and the inner wall surface of the bearing 150 are reduced and close to each other in the direction away from the gear pump part 110, a flexible support is formed at the front end of the bearing 150, the upper end surface pressure of the bearing 150 is reduced, and abrasion is improved.

Further, the first wall 1510a and/or the second wall 1510b may include at least one flat section or curved section.

From the opening side of the groove 1510 to the groove bottom 1510c side of the groove 1510, the first wall 1510a may be a plane or multiple planes, as long as the opening area of the groove 1510 is larger than the area of the groove bottom 1510c of the groove 1510, and the first wall 1510a is a plane or multiple planes, the bearing 150 can buffer the received radial force.

Similarly, the second wall 1510b may be a plane or multiple planes from the opening side of the groove 1510 to the bottom 1510c of the groove 1510, so that the bearing 150 can buffer the radial force as long as the opening area of the groove 1510 is larger than the bottom 1510c of the groove 1510 and the second wall 1510b is a plane or multiple planes.

Further, a chamfer structure is formed between the wall surface of the groove body 1510 and the axial end surface of the bearing 150; and/or the first and second walls 1510a and 1510b are formed with a chamfered structure with the bottom 1510c of the groove 1510.

When the groove body 1510 is machined, a chamfer structure can be machined between the wall surface of the groove body 1510 and the axial end surface of the bearing 150 and between the first wall surface 1510a and the second wall surface 1510b and the groove bottom 1510c of the groove body 1510, and the chamfer structure can avoid structural defects on the surface of the bearing 150. Moreover, by providing the chamfer structure at the connection between the first wall surface 1510a and the groove bottom 1510c of the groove body 1510b, the connection between the first wall surface 1510a and the groove bottom 1510c of the groove body 1510b is smoothly transited, so as to avoid the occurrence of stress concentration at the connection, avoid the occurrence of fracture of the bearing 150 at the connection between the first wall surface 1510a and the groove bottom 1510c of the groove body 1510b, and effectively reduce the damage rate of the bearing 150.

Example four:

as shown in fig. 1 and fig. 2, on the basis of the above embodiment, the pump apparatus 100 further includes: the pump motor comprises a shell 130, a pump part 110, a motor part 120 and a sealing part 170, wherein a cavity 140 enclosed by the shell 130 is divided into a pump cavity and a motor cavity by a bearing 150; pump section 110 is attached to housing 130, with pump section 110 located within the pump cavity; the motor part 120 is connected to the shell 130, and the motor part 120 is positioned in the motor cavity; the sealing member 170 is disposed on an axial end surface of the bearing 150 facing away from the pump portion 110 and located in the motor cavity, and the sealing member 170 is sleeved on the rotating shaft 152.

In this embodiment, the bearing 150 divides a cavity enclosed by the casing 130 into a pump cavity and a motor cavity, the pump cavity is used for accommodating the pump portion 110, the motor cavity is used for accommodating the motor portion 120, and the pump portion 110 and the motor portion 120 are both connected to the casing 130, so that the pump portion 110 and the motor portion 120 are not easy to shake relative to the casing 130, and the stability of the pump portion 110 and the motor portion 120 during operation is improved. Sealing member 170 is the oil blanket promptly, sealing member 170 installs on bearing 150, and sealing member 170 cover is located pivot 152, the oil blanket is isolated with motor chamber and pump chamber, thereby make working medium can not flow into the motor chamber, can not influence the normal use of parts such as the stator in the motor chamber, the rotor, the control panel, the spare part that need not additionally set up other structures in order to guarantee in the motor chamber receives the corruption, make pump unit 100's sealing performance better, the structure is simpler simultaneously, be favorable to reduce cost.

Further, a portion of the bearing 150 extends away from the pump section 110 to form a mounting location 171, and the seal 170 is disposed within the mounting location 171.

The installation position 171 for installing the sealing member 170 is formed by a part of the first bearing 150, so that the installation accuracy of the sealing member 170 can be ensured, the assembly is simple, the sealing performance is good, and the cost is low. The side of the mounting portion 171 facing away from the pump cavity is farther away from the pump cavity than the side of the sealing member 170 facing away from the pump cavity, so that the sealing member 170 is completely accommodated in the mounting portion 171, the mounting stability of the sealing member 170 is improved, and the sealing member 170 is prevented from being separated from the mounting portion 171.

Further, the pump section 110 includes: a first rotating member 111 and a second rotating member 112, the first rotating member 111 cooperating with the rotating shaft 152; the second rotating member 112 is disposed outside the first rotating member 111, the first rotating member 111 can drive the second rotating member 112 to rotate, the second rotating member 112 and the first rotating member 111 form a compression chamber 113, the compression chamber 113 includes a first pressure chamber 114 and a second pressure chamber 115, and a pressure borne by the first pressure chamber 114 is greater than a pressure borne by the second pressure chamber 115. In the axial direction of the rotating shaft 152, a gap is provided between the bearing 150 and the seal 170 to form a liquid passing chamber 180, and the liquid passing chamber 180 communicates the first pressure chamber 114 and the second pressure chamber 115.

The first rotating member 111 and the second rotating member 112 constitute a compression chamber 113, and the compression chamber 113 includes a first pressure chamber 114 and a second pressure chamber 115, the first pressure chamber 114 being subjected to a pressure greater than the second pressure chamber 115, i.e., the first pressure chamber 114 serves as a high pressure chamber, and the second pressure chamber 115 serves as a low pressure chamber. Because the pressure born by the first pressure cavity 114 is larger, the oil liquid in the first pressure cavity 114 can flow out to the liquid passing cavity 180, and when the oil liquid flows to the liquid passing cavity 180 from the first pressure cavity 114, the rotating shaft 152 and the bearing 150 can be lubricated, so that the abrasion speed of the rotating shaft 152 and the bearing 150 is reduced. The oil in the liquid passing cavity 180 can flow to the second pressure cavity 115, so that the situation that the sealing element 170 is pushed away from the mounting position 171 due to the fact that the oil is accumulated in the liquid passing cavity 180 is avoided, and the sealing stability of the sealing element 170 is improved.

It should be noted that the first rotating member 111 is an internal gear, the second rotating member 112 is an external gear, and the pump portion is a gear pump. Specifically, in the gear pump meshing process, a front pair of teeth are not meshed yet, a rear pair of teeth are meshed, each inner tooth surface is in contact with an outer tooth surface to form a closed cavity, the volume of the closed cavity can be changed along with the rotation of an inner gear, and if an unloading channel cannot be communicated, an oil trapping volume can be formed. Because the compressibility of the liquid is very small, when the trapped oil volume is reduced from large to small, the liquid in the trapped oil volume is extruded, the pressure is increased sharply, and the working pressure of the gear pump is greatly exceeded. Meanwhile, liquid trapped in the oil volume is forcibly squeezed out from all gaps capable of leaking, so that the rotating shaft 152 and the bearing 150 can bear large impact load, power loss is increased, oil is heated, noise and vibration are caused, and the working stability and the service life of the gear pump are reduced. When the trapped oil volume is changed from small to large, vacuum is formed, so that air dissolved in liquid is separated out to generate bubbles, and the harm of cavitation, noise, vibration, flow, pressure pulsation and the like is brought. The method for eliminating the oil trapping phenomenon is characterized in that unloading grooves (first oil grooves) are formed in two end covers of a gear, so that the unloading grooves are communicated with an oil pressing cavity when the closed volume is reduced, and the unloading grooves are communicated with an oil suction cavity through the unloading grooves when the closed volume is increased.

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

Regarding the design principle of the oil inlet and the oil outlet, in the process of ensuring the rotation of the gear, the oil inlet is communicated with the tooth spaces of the first rotating part 111 and the second rotating part 112 as early as possible, before the internal gear and the external gear form the maximum volume, the gear volume cavity is always communicated with the oil inlet, and the oil filling time is prolonged as far as possible, so that the volume cavity between the internal gear and the external gear is filled with oil, thereby ensuring the oil absorption. The oil outlet is communicated with high-pressure oil between the teeth as early as possible to reduce the compression work between the teeth, and is closed as late as possible to fully utilize the inertia of fluid to exhaust the oil between the teeth, so that the volume efficiency of the internal gear type oil pump is improved. It should be noted, however, that the internal and external gears cannot communicate with the oil inlet when they form the maximum volume, thereby avoiding affecting the volumetric efficiency of the pump apparatus 100 at low speed.

Further, a groove 1510 is provided on an end surface of the bearing 150 facing the seal 170, and the groove 1510 communicates with the liquid chamber 180.

Can all set up cell body 1510 at the terminal surface at bearing 150's axial both ends, the utility model discloses in set up cell body 1510 on bearing 150 towards the axial terminal surface of sealing member 170, cell body 1510 communicates with cross sap cavity 180 moreover, and when fluid flowed to the clearance department between bearing 150 and the sealing member 170, fluid also can flow into in the cell body 1510. The gap between the sealing element 170 and the bearing 150 is large at the groove 1510, the cross-sectional area of the liquid passing cavity 180 is increased, and the cross-sectional area of the liquid passing cavity 180 is increased, so that the pressure of oil liquid in the liquid passing cavity 180 can be reduced, the sealing element 170 is not easily pushed away from the mounting position 171 by the oil liquid, a gap between the sealing element 170 and the mounting position 171 is also avoided, and the sealing element 170 can be ensured to play a role in stably sealing.

Further, the pump apparatus 100 further includes: the lubricating groove 1512 is arranged on the inner side wall of the bearing 150, and two ends of the lubricating groove 1512 are respectively communicated with the first pressure cavity 114 and the liquid passing cavity 180; and an oil return passage 1514 provided in the bearing 150 and/or the housing 130, both ends of the oil return passage 1514 being communicated with the second pressure chamber 115 and the liquid passing chamber 180, respectively.

The oil in the first pressure chamber 114 can flow into the fluid chamber 180 through the lubrication groove 1512, and the oil can lubricate the bearing 150 and the rotating shaft 152, thereby reducing the wear rate of the rotating shaft 152 and the bearing 150. In order to enable the oil to better flow between the rotating shaft 152 and the bearing 150, specifically, the bearing 150 is provided with the lubricating groove 1512, and the lubricating groove 1512 is not required to be provided on the rotating shaft 152, so that damage to the structure of the rotating shaft 152 is avoided, and the structural stability of the rotating shaft 152 is ensured. Due to the higher pressure experienced by the first pressure chamber 114, the oil in the first pressure chamber 114 is able to flow out through the lubrication channel 1512 and into the fluid chamber 180, and the oil in the fluid chamber 180 flows into the second pressure chamber 115 through the return channel 1514. The oil return passage 1514 is formed between the bearing 150 and the housing 130, so that the oil return passage 1514 is formed on the bearing 150 or the housing 130, and the structural stability of the rotating shaft 152 is not affected, the oil return passage 1514 can be machined on the bearing 150 or the housing 130, the oil return passage 1514 can be machined between the bearing 150 and the housing 130, oil in the liquid passing cavity 180 can flow into the second pressure cavity 115 by arranging the oil return passage 1514, the situation that the sealing element 170 is pushed away from the mounting position 171 due to accumulation of the oil in the liquid passing cavity 180 is avoided, and the sealing stability of the sealing element 170 is ensured.

Further, the radial dimension of the flow-through cross-section of the oil return passage 1514 is greater than or equal to 1 mm.

The size of the oil return channel 1514 is specifically limited, when the radial size of the through-flow section of the oil return channel 1514 is small, the outflow speed of oil in the through-liquid cavity 180 is slow, the situation that the pressure in the through-liquid cavity 180 is gradually increased easily occurs, in order to avoid the situation that the sealing element 170 is separated from the mounting position 171 due to the fact that the pressure in the through-liquid cavity 180 is large, the radial size of the through-flow section of the oil return channel 1514 is limited to be larger than or equal to 1 millimeter, the oil in the through-liquid cavity 180 can flow out quickly, the oil return channel 1514 plays a role in pressure relief, the sealing element 170 is effectively prevented from being separated from the mounting position 171, and the sealing stability of the sealing element 170 is improved.

Example five:

as shown in fig. 4, a second aspect of the present invention provides a vehicle 200, including: the pump apparatus 100 according to any of the above embodiments. The utility model provides a vehicle 200 owing to have the pump unit 100 of any embodiment of the aforesaid, and then has the beneficial effect of any embodiment of the aforesaid, and the unnecessary repetition here is repeated.

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

In one particular embodiment, vehicle 200 includes a body 210 and an engine 220. The pump apparatus 100 and the engine 220 are both provided in the vehicle body 210.

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

In the present application, the term "plurality" means two or more unless expressly defined otherwise. The terms "mounted," "connected," "fixed," and the like are to be construed broadly, and for example, "connected" may be a fixed connection, a removable connection, or an integral connection; "coupled" may be direct or indirect through an intermediary. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.

The above embodiments are only used to illustrate the technical solution of the present invention, and do not limit the protection scope of the present invention. It is to be understood that the embodiments described are only some embodiments of the invention, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from these embodiments without any inventive step, are within the scope of the present invention. Although the present invention has been described in detail with reference to the above embodiments, those skilled in the art can still make no creative work on the condition of conflict, and make mutual combination, addition and deletion, or other adjustments according to the features in the embodiments of the present invention, thereby obtaining other technical solutions which are different and do not depart from the concept of the present invention, and these technical solutions also belong to the scope to be protected by the present invention.

In the description of the present specification, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (16)

1. A pump apparatus, comprising:

a rotating shaft;

the bearing is sleeved on the rotating shaft, and a groove body is arranged on the axial end face of the bearing.

2. Pump apparatus according to claim 1,

the channel is configured as an annular structure disposed around the shaft.

3. Pump apparatus according to claim 1,

the groove bodies are multiple and are arranged at intervals along the circumferential direction of the bearing.

4. Pump apparatus according to claim 3,

two adjacent groove bodies in the plurality of groove bodies are mutually communicated.

5. Pump apparatus according to claim 1,

the opening area of the groove body is larger than the bottom area of the groove body.

6. The pump arrangement of claim 5, wherein the tank comprises:

the first wall surface is that the cell body is close to the wall surface of pivot, certainly the opening of cell body extremely the tank bottom of cell body, the first wall surface of cell body with the interval increase of pivot.

7. The pump arrangement of claim 6, wherein the tank comprises:

the second wall surface is arranged opposite to the first wall surface, the opening of the groove body reaches the groove bottom of the groove body, and the distance between the second wall surface and the rotating shaft is reduced.

8. The pump arrangement according to claim 7,

the first wall surface and/or the second wall surface comprise at least one section of plane surface section or curved surface section.

9. The pump arrangement according to claim 7,

a chamfer angle structure is formed between the wall surface of the groove body and the axial end surface of the bearing; and/or

And chamfer structures are formed on the first wall surface, the second wall surface and the groove bottom of the groove body.

10. The pump arrangement according to any one of claims 1 to 9, further comprising:

the bearing divides a cavity enclosed by the shell into a pump cavity and a motor cavity;

a pump portion coupled to the housing, the pump portion being located within the pump cavity;

the motor part is connected to the shell and is positioned in the motor cavity;

the sealing element is arranged on the axial end face of the bearing deviated from the pump part and located in the motor cavity, and the rotating shaft is sleeved with the sealing element.

11. The pump arrangement according to claim 10,

a portion of the bearing extends away from the pump portion to create a mounting location in which the seal is disposed.

12. The pump apparatus of claim 10, wherein the pump portion comprises:

the first rotating piece is matched with the rotating shaft;

the second rotating part is arranged on the outer side of the first rotating part, the first rotating part can drive the second rotating part to rotate, the second rotating part and the first rotating part form a compression cavity, the compression cavity comprises a first pressure cavity and a second pressure cavity, and the pressure borne by the first pressure cavity is greater than the pressure borne by the second pressure cavity;

along the axial of pivot, be equipped with the clearance in order to form the liquid chamber of crossing between the bearing and the sealing member, the liquid chamber of crossing communicates first pressure chamber with the second pressure chamber.

13. The pump arrangement according to claim 12,

the groove body is arranged on the end face, facing the sealing piece, of the bearing, and the groove body is communicated with the liquid passing cavity.

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

the lubricating groove is arranged on the inner side wall of the bearing, and two ends of the lubricating groove are respectively communicated with the first pressure cavity and the liquid passing cavity;

and the oil return passage is arranged on the bearing and/or the shell, and two ends of the oil return passage are respectively communicated with the second pressure cavity and the liquid passing cavity.

15. The pump arrangement according to claim 14,

the radial dimension of the through-flow section of the oil return channel is greater than or equal to 1 millimeter.

16. A vehicle, characterized by comprising: a pump device according to any one of claims 1 to 15.

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