Gear pump, suspension lifting mechanism and vehicle

Abstract

The utility model discloses a gear pump, a suspension lifting mechanism and a vehicle, the gear pump comprises: a housing, which is provided with an inflow channel, an outflow channel and a floating channel; the gear shaft is rotationally installed on the shell, the gear shaft is provided with a driving part, the shaft sleeve is arranged outside the gear shaft in a sleeving mode, a pump cavity for containing the driving part is defined by the shaft sleeve and the shell, and a floating cavity is defined by the end, away from the driving part, of the shaft sleeve and the shell; the inflow runner and the outflow runner communicate with the two sides of the pump cavity correspondingly, one end of the floating runner communicates with the outflow runner, the other end of the floating runner communicates with the floating cavity, and radial force balance grooves are formed in the two sides of the peripheral wall of the shaft sleeve correspondingly and communicate with the floating cavity. According to the gear pump disclosed by the utility model, the radial force borne by the shaft sleeve can be balanced, the positions of the shaft sleeve and the gear shaft are kept stable, and oil leakage caused by excessive shaking and inclination of the shaft sleeve and the gear shaft is avoided, so that the volume efficiency of the gear pump can be improved, and the abrasion degree and noise of the gear pump are reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of gear pumps, in particular to a gear pump, a suspension lifting mechanism with the gear pump, and a vehicle with the suspension lifting mechanism. Background Art

[0002] Gear pumps are used in various hydraulic systems and projects, including the fields of the automotive industry, agricultural equipment, construction engineering, aerospace, etc. The volumetric efficiency of a gear pump represents the ability of the gear pump to resist leakage. The volumetric efficiency of a gear pump is equal to the actual flow rate of the gear pump divided by the theoretical flow rate of the gear pump. In existing gear pumps, the gear shaft and the shaft sleeve are prone to tilt due to unbalanced radial forces during operation, resulting in leakage and wear of the gear pump. Content of the Utility Model

[0003] The utility model aims to solve at least one of the technical problems existing in the prior art. For this purpose, the utility model provides a gear pump, which can balance the radial force received by the shaft sleeve, keep the positions of the shaft sleeve and the gear shaft stable, avoid excessive shaking and tilting of the shaft sleeve and the gear shaft, resulting in oil leakage, thereby improving the volumetric efficiency of the gear pump, reducing the wear degree and noise of the gear pump.

[0004] The gear pump according to an embodiment of the utility model includes: a housing, which is provided with an inlet flow channel, an outlet flow channel, and a floating flow channel; a gear shaft and a shaft sleeve, the gear shaft is rotatably installed in the housing, the gear shaft is provided with a driving part, the shaft sleeve is sleeved outside the gear shaft, the shaft sleeve and the housing define a pump chamber for accommodating the driving part, and the shaft sleeve and the housing define a floating chamber at one end away from the driving part; wherein, the inlet flow channel and the outlet flow channel are respectively communicated with both sides of the pump chamber, one end of the floating flow channel is communicated with the outlet flow channel and the other end is communicated with the floating chamber, and radial force balance grooves are provided on both sides of the outer peripheral wall of the shaft sleeve and are respectively communicated with the floating chamber.

[0005] For the gear pump according to an embodiment of the utility model, by providing radial force balance grooves on both sides of the outer peripheral wall of the shaft sleeve, and the radial force balance grooves are communicated with the floating chamber, the high-pressure oil in the floating chamber can flow into the radial force balance grooves, thereby balancing the radial force received by the shaft sleeve, keeping the positions of the shaft sleeve and the gear shaft stable, avoiding excessive shaking and tilting of the shaft sleeve and the gear shaft, resulting in oil leakage, thereby improving the volumetric efficiency of the gear pump, reducing the wear degree and noise of the gear pump.

[0006] According to the gear pump of some embodiments of the present utility model, there are two gear shafts, the driving part is configured as a gear part, the gear parts of the two gear shafts are meshed, the shaft sleeve includes two connected sleeve parts, and the two sleeve parts are respectively sleeved outside the two gear shafts one by one and are axially oppositely distributed with the corresponding gear parts; diversion grooves are formed on both sides of the connection of the outer peripheral walls of the two sleeve parts, the diversion grooves extend along the axial direction of the shaft sleeve, and the floating cavity is communicated with the radial force balance groove through the diversion groove on the corresponding side.

[0007] According to the gear pump of some embodiments of the present utility model, the radial force balance groove includes an intermediate sub-groove and two end sub-grooves, the two end sub-grooves are respectively arranged on the outer peripheral walls of the two sleeve parts, the intermediate sub-groove is communicated with the diversion groove, the intermediate sub-groove is communicated between the two end sub-grooves, and the width of the end sub-groove along the axial direction of the sleeve part is greater than the width of the intermediate sub-groove along the axial direction of the sleeve part.

[0008] According to the gear pump of some embodiments of the present utility model, the two end sub-grooves are symmetrically distributed at both ends of the intermediate sub-groove; and / or, the depth of the end sub-groove along the radial direction of the sleeve part is the same as the depth of the intermediate sub-groove along the radial direction of the sleeve part.

[0009] According to the gear pump of some embodiments of the present utility model, the distribution directions of the inlet flow channel and the outlet flow channel intersect with the distribution direction of the two gear shafts; and / or, the inlet direction of the inlet flow channel coincides with the outlet direction of the outlet flow channel, and the meshing position of the two gear parts is on the extension direction of the inlet flow channel.

[0010] According to the gear pump of some embodiments of the present utility model, a relief groove is formed at one end of the connection of the two sleeve parts facing the pump cavity.

[0011] According to the gear pump of some embodiments of the present utility model, relief grooves are provided on both sides of one end of the connection of the two sleeve parts facing the pump cavity, and the relief grooves on both sides are asymmetrically distributed.

[0012] According to the gear pump of some embodiments of the present utility model, the number of teeth of the two gear parts is M, and it satisfies: 12 ≤ M ≤ 15; and / or, the contact ratio of the two gear parts is A, and it satisfies: 1.5 ≤ A ≤ 2.0; and / or, the pressure angle of the two gear parts is B, and it satisfies: 23° ≤ B ≤ 26°.

[0013] According to the gear pump of some embodiments of the present utility model, the inner diameter of the outlet flow channel is smaller than the inner diameter of the inlet flow channel.

[0014] The gear pump according to some embodiments of the present utility model, the housing includes a first mounting hole, a mounting space and a second mounting hole that are communicated in sequence, and the gear shaft includes a first shaft segment, a gear portion and a second shaft segment that are connected in sequence; wherein, the sleeve is sleeved outside the first shaft segment and both the sleeve and the gear portion are located in the mounting space, a fitting portion that penetrates through the first mounting hole is formed at the free end of the sleeve, and the second shaft segment rotatably penetrates through the second mounting hole.

[0015] The gear pump according to some embodiments of the present utility model, the housing includes an upper cover and a lower housing, the upper cover is detachably connected to the upper end of the lower housing, the upper cover and the lower housing jointly define the mounting space, the first mounting hole is formed in the upper cover, and the second mounting hole is formed in the lower housing.

[0016] The present utility model also proposes a suspension lifting mechanism.

[0017] The suspension lifting mechanism according to an embodiment of the present utility model includes the gear pump described in any one of the above embodiments.

[0018] The present utility model also proposes a vehicle.

[0019] The vehicle according to an embodiment of the present utility model includes the above suspension lifting mechanism.

[0020] The advantages of the suspension lifting mechanism, the vehicle and the above gear pump over the prior art are the same and will not be described herein again.

[0021] The additional aspects and advantages of the present utility model will be partially given in the following description, partially become obvious from the following description, or be understood through the practice of the present utility model. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] The above and / or additional aspects and advantages of the present utility model will become obvious and easy to understand from the description of the embodiments in conjunction with the following drawings, wherein:

[0023] Figure 1 is an exploded view of the gear pump according to an embodiment of the present utility model;

[0024] Figure 2 is a schematic structural view of the sleeve according to an embodiment of the present utility model Figure 1 ;

[0025] Figure 3 is a schematic structural view of the sleeve according to an embodiment of the present utility model Figure 2 ;

[0026] Figure 4 is a schematic structural view of the sleeve according to an embodiment of the present utility model Figure 3 ;

[0027] Figure 5 is a schematic structure diagram of a bushing according to an embodiment of the present utility model Figure 4 ;

[0028] Figure 6 is a schematic structure diagram of a bushing according to an embodiment of the present utility model Figure 5 ;

[0029] Figure 7 is a schematic structure diagram of a bushing according to an embodiment of the present utility model Figure 6 ;

[0030] Figure 8 is Figure 7 a sectional view of;

[0031] Figure 9 is a top view of a gear pump according to an embodiment of the present utility model;

[0032] Figure 10 is Figure 9 a sectional view of;

[0033] Figure 11 is a schematic structure diagram of a gear shaft according to an embodiment of the present utility model Figure 1 ;

[0034] Figure 12 is a schematic structure diagram of a gear shaft according to an embodiment of the present utility model Figure 2 .

[0035] Reference numerals:

[0036] gear pump 100,

[0037] housing 1, upper cover 11, first mounting hole 111, lower housing 12, second mounting hole 121, mounting space 13,

[0038] gear shaft 2, first shaft section 21, gear portion 22, second shaft section 23,

[0039] bushing 3, radial force balance groove 31, intermediate sub-groove 311, end sub-groove 312, sleeve portion 32, diversion groove 33, unloading groove 34, mating portion 35,

[0040] floating flow channel 41, inlet flow channel 42, outlet flow channel 43, positioning post 44, retaining ring 45, sealing ring 46, filter element 47, pump chamber 48. Detailed implementation manners

[0041] Embodiments of the present utility model will be described in detail below. Examples of the embodiments are shown in the accompanying drawings, where the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the accompanying drawings are exemplary and are only used to explain the present utility model and should not be construed as limiting the present utility model.

[0042] In the description of the present utility model, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present utility model. In addition, the features defined as "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present utility model, unless otherwise specified, the meaning of "a plurality" is two or more.

[0043] In the description of the present utility model, it should be noted that unless otherwise clearly specified and defined, the terms "mounted", "connected" and "connected" should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific situations.

[0044] Reference will be made below Figures 1 - 12 to describe a gear pump 100 according to an embodiment of the present utility model. The gear pump 100 can balance the radial force received by the shaft sleeve 3, keep the positions of the shaft sleeve 3 and the gear shaft 2 stable, and prevent excessive shaking and tilting of the shaft sleeve 3 and the gear shaft 2, thereby avoiding oil leakage. As a result, the volumetric efficiency of the gear pump 100 can be greatly improved, and the wear degree and noise of the gear pump 100 can be reduced.

[0045] As Figures 1 - 12 shown, a gear pump 100 according to an embodiment of the present utility model includes: a housing 1, a gear shaft 2 and a shaft sleeve 3.

[0046] The housing 1 is the main structure of the gear pump 100. It is used to install and protect the internal components and bear the pressure of the internal liquid and the external environment. The housing 1 needs to be made of a strong material to ensure the stable and reliable operation of the gear pump 100.

[0047] The shell 1 is provided with an inlet flow channel 42, an outlet flow channel 43 and a floating flow channel 41, that is, a plurality of flow channels are arranged inside the shell 1, and the inlet flow channel 42 is used to introduce external liquid (such as oil, etc.) into the shell 1, and the inlet flow channel 42 may be provided with a liquid inlet, which is connected to an external liquid source (such as an oil tank or a pipeline, etc.) to facilitate external liquid to enter the inlet flow channel 42 through the liquid inlet; the outlet flow channel 43 is used to transport the liquid compressed and discharged by the gear pump 100 to an external device or a pipeline, and the outlet flow channel 43 may be provided with a liquid outlet, which is connected to an external device or a pipeline to facilitate the discharge of the liquid through the liquid outlet.

[0048] The size and shape of the inlet flow channel 42 and the size and shape of the outlet flow channel 43 have a certain influence on the efficiency of the gear pump 100. The design of the inlet flow channel 42 needs to reduce the resistance during liquid flow and improve the suction efficiency and performance of the gear pump 100. The design of the outlet flow channel 43 needs to ensure that the liquid can be discharged smoothly out of the shell 1 and reduce pressure loss and energy loss.

[0049] Liquid can flow in the floating flow channel 41 , which is used to adjust the position of the sleeve 3 and balance the radial force on the sleeve 3 .

[0050] The gear shaft 2 is rotatably mounted on the housing 1. The gear shaft 2 is provided with a driving part. The shaft sleeve 3 is sleeved outside the gear shaft 2. The shaft sleeve 3 and the housing 1 define a pump chamber 48 for accommodating the driving part. The shaft sleeve 3 defines a floating chamber with the housing 1 at one end away from the driving part.

[0051] Specifically, a hollow area is formed inside the housing 1 for accommodating and installing the gear shaft 2. The gear shaft 2 can rotate relative to the housing 1, and the housing 1 can position and support the gear shaft 2 to ensure the smooth movement of the gear shaft 2. The gear shaft 2 is provided with a driving part, which can be designed as an integrated whole with the gear shaft 2, which is convenient for manufacturing and has high transmission efficiency, or can be provided separately. When the gear shaft 2 rotates, it drives the driving part to rotate, and the driving part drives and squeezes the liquid when rotating. The sleeve 3 is used to protect the gear shaft 2, and can be provided in an annular shape to be sleeved outside the gear shaft 2 and distributed in the up and down directions with the driving part in the axial direction, so as to protect the driving part, avoid friction between the driving part and the sleeve 3, and cause wear to the driving part. At the same time, the sleeve 3 separates the gear shaft 2 from the housing 1, reduces direct friction between the gear shaft 2 and the housing 1, causes wear to the gear shaft 2, and affects the movement of the gear shaft 2.

[0052] The space between one side of the bushing 3 facing the driving part and the housing 1 is the pump chamber 48. The driving part is accommodated in the pump chamber 48. The pump chamber 48 can drive the flow of liquid through the rotation of the driving part. And one end of the bushing 3 facing away from the driving part and the housing 1 define a floating chamber. The floating chamber can store a certain amount of liquid. The bushing 3 can float in the floating chamber, thereby providing a certain degree of freedom for the gear shaft 2, which is beneficial to buffering and reducing vibration and impact during operation, avoiding excessive noise, and improving the operation reliability and stability of the gear pump 100.

[0053] In actual design, two gear shafts 2 can be provided, and the driving parts of the two gear shafts 2 mesh with each other. Thus, when one gear shaft 2 rotates to drive the rotation of its driving part, the driving part can drive the driving part of the other gear shaft 2 meshing with it to rotate, so that the other gear shaft 2 rotates. In this way, through the continuous meshing transmission of the two driving parts, the volume of the pump chamber 48 continuously changes. When the driving parts gradually separate, the volume of the pump chamber 48 increases, forming a low-pressure area, and the external liquid is sucked into the pump chamber 48 through the inlet flow channel 42. When the driving parts gradually mesh, the volume of the pump chamber 48 gradually decreases, and the liquid is compressed into high-pressure liquid and discharged out of the housing 1 through the outlet flow channel 43. Thus, through continuous squeezing of the liquid, continuous transportation of the liquid is realized. Among them, a driving member can also be provided. For example, a driving motor provides power to drive the rotation of the gear shaft 2.

[0054] And filter elements 47 can be arranged in the floating flow channel 41, the inlet flow channel 42 and the outlet flow channel 43 to filter the liquid, ensure the purity of the flowing liquid, and prevent external foreign objects from entering the flow channels to block the flow channels and hinder the normal operation of the gear pump 100.

[0055] Furthermore, among them, the inlet flow channel 42 and the outlet flow channel 43 are respectively communicated with both sides of the pump chamber 48. One end of the floating flow channel 41 is communicated with the outlet flow channel 43 and the other end is communicated with the floating chamber. Radial force balance grooves 31 are provided on both sides of the outer peripheral wall of the bushing 3 and are respectively communicated with the floating chamber.

[0056] Specifically, the inlet flow channel 42 and the outlet flow channel 43 are respectively communicated with both sides of the pump chamber 48, that is, the inlet flow channel 42 and the outlet flow channel 43 are arranged at intervals in the housing 1 to ensure the smooth flow of the liquid. The inlet flow channel 42 is a low-pressure area, and the outlet flow channel 43 is a high-pressure area. The liquid entering the inlet flow channel 42 can flow into the pump chamber 48 and be compressed and pressurized under the action of the driving part in the pump chamber 48, and the liquid is led out of the pump chamber 48 and into the outlet flow channel 43, thereby realizing the liquid transportation from the low-pressure area to the high-pressure area.

[0057] It should be noted that, for example, when the liquid is oil, due to the different pressures in the inflow channel 42 and the outflow channel 43 on both sides of the pump chamber 48, one side of the driving part and the bushing 3 is at high pressure and the other side is at low pressure. This will cause the radial forces on both sides of the gear part 22 and the bushing 3 to be unbalanced. During operation, it will cause the driving part and the bushing 3 to tilt and not maintain a stable state, which may lead to oil leakage. Moreover, when the driving part and the bushing 3 tilt, it is easy to cause wear to the housing 1 and generate noise.

[0058] Therefore, a floating channel 41 is provided or radial force balance grooves 31 are provided on the outer peripheral wall of the bushing 3 to solve the problem. One end of the floating channel 41 is communicated with the outflow channel 43, so that part of the high-pressure oil in the outflow channel 43 can flow into the floating channel 41. The other end of the floating channel 41 is communicated with the floating cavity, that is, part of the high-pressure oil can flow into the floating cavity through the floating channel 41 to adjust the liquid flow rate and pressure in the floating cavity. Thus, it is beneficial for the high-pressure oil in the floating cavity to axially press the bushing 3, realize the adjustment of the position of the bushing 3, keep the position of the bushing 3 stable, balance the radial force received by the bushing 3, avoid excessive shaking and tilting of the bushing 3 leading to liquid leakage, and reduce the wear degree of the bushing 3 on the housing 1. At the same time, when the position of the bushing 3 is stable, the driving part can rotate stably, avoiding tilting of the driving part. Thus, it can avoid excessive shaking and tilting of the driving part leading to liquid leakage and reduce the wear degree of the gear shaft 2 on the housing 1.

[0059] In addition, radial force balance grooves 31 are provided on both the relatively high-pressure and low-pressure sides of the outer peripheral wall of the bushing 3. The radial force balance grooves 31 are used to reduce the unbalanced radial force generated when the driving part rotates and the unbalanced radial force generated by the bushing 3 due to uneven force. Among them, the radial force balance grooves 31 are communicated with the floating cavity, that is, the high-pressure oil in the floating cavity can flow into the radial force balance grooves 31 located on both the high-pressure and low-pressure sides respectively to offset the unbalanced radial force on one side of the bushing 3, keep both sides of the bushing 3 balanced, and further realize the balance of the radial force received by the bushing 3, keep the positions of the bushing 3 and the gear shaft 2 stable, avoid excessive shaking and tilting of the bushing 3 and the driving part leading to liquid leakage, and thus can greatly improve the volumetric efficiency of the gear pump 100, reduce the wear degree of the bushing 3 and the gear shaft 2 on the housing 1, and the noise generated by the gear pump 100.

[0060] According to the gear pump 100 of the embodiment of the present invention, by providing radial force balance grooves 31 on both sides of the outer peripheral wall of the bushing 3 and communicating the radial force balance grooves 31 with the floating cavity, the high-pressure oil in the floating cavity can flow into the radial force balance grooves 31, thereby balancing the radial force received by the bushing 3, keeping the positions of the bushing 3 and the gear shaft 2 stable, avoiding excessive shaking and tilting of the bushing 3 and the gear shaft 2 leading to oil leakage, and thus can greatly improve the volumetric efficiency of the gear pump 100, reduce the wear degree and noise of the gear pump 100.

[0061] In some embodiments, there are two gear shafts 2, the driving part is configured as a gear part 22, the gear parts 22 of the two gear shafts 2 are meshed, the sleeve 3 includes two connected sleeve parts 32, and the two sleeve parts 32 are respectively sleeved outside the two gear shafts 2 in a one-to-one correspondence and are axially distributed opposite to the corresponding gear parts 22.

[0062] Specifically, as Figure 1 shown, there are two gear shafts 2, the driving part is configured as a gear part 22, the two gear shafts 2 are parallel and spaced apart, and the gear parts 22 are correspondingly positioned and meshed with each other, so as to realize the power transmission from one gear part 22 to another gear part 22. One of them is a driving gear and the other is a driven gear. The driving gear is driven by a driving member to rotate, so as to drive the meshed driven gear to rotate in the opposite direction to realize the transmission of hydraulic oil.

[0063] As Figures 2 - 6 shown, the sleeve 3 includes two connected sleeve parts 32. The shape and size of the sleeve part should match the shape and size of the gear shaft 2. The sleeve part is a hollow structure in the shape of a cylinder and has a certain thickness, so that the two sleeve parts 32 can be respectively tightly sleeved outside the two gear shafts 2 to support and fix the two gear shafts 2 and prevent the gear shafts 2 from being worn. And the two sleeve parts 32 and the corresponding gear parts 22 are axially distributed opposite to each other, that is, the gear part 22 and the sleeve part 32 are distributed one above the other axially. In this way, it can be ensured that the gear part 22 has enough space to rotate axially to transmit hydraulic oil.

[0064] Thus, the stable rotation of the gear shaft 2 can be ensured and its operation reliability can be improved.

[0065] Furthermore, flow guiding grooves 33 are formed on both sides of the connection of the outer peripheral walls of the two sleeve parts 32. The flow guiding grooves 33 extend along the axial direction of the sleeve 3, and the floating cavity is communicated with the radial force balance groove 31 through the flow guiding grooves 33 on the corresponding side.

[0066] Specifically, as Figure 5 and Figure 6 shown, flow guiding grooves 33 are formed on opposite sides of the connection of the outer peripheral walls of the two sleeve parts 32. The flow guiding grooves 33 are used to guide the flow of hydraulic oil, and the flow guiding grooves 33 extend along the axial direction of the sleeve 3, that is, along the length direction of the sleeve 3, which is beneficial to guiding the hydraulic oil to flow in the up and down directions.

[0067] Among them, the floating cavity is communicated with the radial force balance groove 31 through the diversion grooves 33 on the corresponding sides, that is, the high-pressure hydraulic oil in the floating cavity can be drained to the radial force balance grooves 31 on both sides through the diversion grooves 33 on both sides, so that the radial force balance grooves 31 are filled with high-pressure hydraulic oil, thereby enabling the balance of the high and low pressure sides of the sleeve 3. That is, when the sleeve 3 is subjected to an unbalanced radial force during operation, the unbalanced radial force can flow through the high-pressure hydraulic oil to the radial force balance groove 31 for balance and cancellation, so that both sides of the sleeve 3 are kept balanced, and further, the swaying and tilting of the sleeve 3 can be reduced, the position of the sleeve 3 is stabilized, the wear of the sleeve 3 is reduced, and the leakage of the hydraulic oil caused by the tilting of the sleeve 3 is avoided.

[0068] In some embodiments, the radial force balance groove 31 includes an intermediate sub-groove 311 and two end sub-grooves 312. The two end sub-grooves 312 are respectively arranged on the outer peripheral walls of the two sleeve parts 32. The intermediate sub-groove 311 is communicated with the diversion groove 33. The intermediate sub-groove 311 is communicated between the two end sub-grooves 312. The width of the end sub-groove 312 along the axial direction of the sleeve part 32 is greater than the width of the intermediate sub-groove 311 along the axial direction of the sleeve part 32.

[0069] Specifically, as Figure 5 and Figure 6 shown, radial force balance grooves 31 are arranged on both sides of the outer peripheral wall of the sleeve 3. One side of the radial force balance groove 31 is located on the high-pressure side, and one side of the radial force balance groove 31 is located on the low-pressure side. The radial force balance grooves 31 on both sides can be symmetrically arranged or asymmetrically arranged, and can be flexibly designed according to actual needs. And the radial force balance grooves 31 all include an intermediate sub-groove 311 and two end sub-grooves 312. The two end sub-grooves 312 are respectively arranged on the outer peripheral walls of the sleeve parts 32, that is, grooves with a certain depth are formed on the outer peripheral walls of the two sleeve parts 32, that is, the end sub-grooves 312, and the two end sub-grooves 312 can be symmetrically arranged or asymmetrically arranged, and can be flexibly designed according to actual needs, so as to facilitate the balance of the radial forces on the two sleeve parts 32, so that both of the two sleeve parts 32 can be effectively balanced.

[0070] An intermediate sub-groove 311 is also arranged on the sleeve 3. The intermediate sub-groove 311 is communicated with the diversion groove 33. In this way, the high-pressure hydraulic oil flowing from the floating cavity into the diversion groove 33 can continue to be shunted into the two end sub-grooves 312 through the intermediate sub-groove 311, so that the two end sub-grooves 312 are filled with high-pressure hydraulic oil, thereby realizing the free flow of the high-pressure hydraulic oil and effectively balancing the radial forces of the two sleeve parts 32.

[0071] Moreover, the width of the end sub-groove 312 in the axial direction of the sleeve portion 32 is greater than the width of the middle sub-groove 311 in the axial direction of the sleeve portion 32. Exemplarily, the width of the end sub-groove 312 can be set to 4 mm, 5 mm, 6 mm, etc., and the width of the middle sub-groove 311 can be set to 1 mm, 1.5 mm, 2 mm, 2.5 mm, 3 mm, etc. It is only necessary that the width of the end sub-groove 312 is greater than the width of the middle sub-groove 311, but the width of the end sub-groove 312 should not be too large to avoid affecting the strength of the bushing 3.

[0072] In this way, the area of the end sub-groove 312 can be increased, so that more high-pressure hydraulic oil can be filled in the end sub-groove 312, thereby more effectively dispersing and balancing the radial force, enabling better balance on both the high-pressure and low-pressure sides of the bushing 3, and further effectively reducing the tilt and wear of the bushing 3 and reducing the leakage of hydraulic oil.

[0073] In actual design, such as Figure 5 and Figure 6 shown, the end sub-groove 312 can be configured as a rectangular groove. Of course, it can also be configured as other shapes, such as oval, irregular, etc.

[0074] It should be noted that the end sub-groove 312 has a certain depth. The deeper the depth of the end sub-groove 312, the more hydraulic oil can flow. On the contrary, the shallower the depth, the less hydraulic oil can flow. However, the depth should not be too deep to avoid affecting the strength of the bushing 3. For example, the depth of the end sub-groove 312 can be set to 0.1 mm, 0.2 mm, 0.3 mm, etc., and can be specifically and flexibly set according to actual situations and requirements, not limited to those described in this embodiment.

[0075] In some embodiments, the two end sub-grooves 312 are symmetrically distributed at both ends of the middle sub-groove 311.

[0076] Specifically, as Figure 5 and Figure 6 shown, the front-back direction shown in the figure is the high-pressure and low-pressure sides. Radial force balance grooves 31 are provided on the outer peripheral wall of the bushing on the high-pressure side, and radial force balance grooves 31 are also provided on the outer peripheral wall of the bushing on the low-pressure side. The two end sub-grooves 312 of the radial force balance groove 31 are symmetrically distributed at both ends of the middle sub-groove 311, so that hydraulic oil is evenly distributed on both the high-pressure and low-pressure sides of the two sleeve portions 32, and the radial force received by the entire bushing 3 during operation can be effectively balanced.

[0077] In the radial force balance groove 31, the two end sub-grooves 312 have the same structure. That is, as shown in the left-right direction in the figure, the left end sub-groove 312 and the right end sub-groove 312 have the same structure and the same height position on the outer peripheral wall of the bushing 3. In this way, when the oil flows through the radial force balance groove 31, it can be evenly distributed in the two end sub-grooves 312 at both ends. Thus, while maintaining the stability of the bushing, it can more effectively disperse and balance the radial force on one side. Moreover, the symmetric setting can also improve the stability and balance of the bushing 3, which is conducive to maintaining the stability of the bushing 3 to a certain extent.

[0078] In actual design, the structures of the two end sub-grooves 312 on the high-pressure side and the structures of the two end sub-grooves 312 on the low-pressure side can be flexibly adjusted according to actual needs, that is, they can be designed to have the same or different structures. For example, the shapes or sizes of the two end sub-grooves 312 on the high-pressure side can be set smaller so that less high-pressure oil flows through them, while the shapes or sizes of the two end sub-grooves 312 on the low-pressure side can be set larger so that more high-pressure oil flows through them. Thus, it is beneficial to further effectively balance the pressures on both the high-pressure and low-pressure sides of the bushing 3.

[0079] In some other embodiments, the depth of the end sub-groove 312 in the radial direction of the sleeve portion 32 is the same as the depth of the middle sub-groove 311 in the radial direction of the sleeve portion 32.

[0080] In this way, when the oil flows through the middle sub-groove 311 and the end sub-groove 312, it can maintain the same flow velocity and pressure distribution, that is, the oil can stably flow into the radial force balance groove 31, thereby further improving the balance effect on the radial force.

[0081] Of course, in actual design, there is a certain allowable error between the depth of the end sub-groove 312 in the radial direction of the sleeve portion 32 and the depth of the middle sub-groove 311 in the radial direction of the sleeve portion 32. That is, the depths of the end sub-groove 312 and the middle sub-groove 311 in the radial direction of the sleeve portion 32 can be flexibly adjusted according to the actual situation. For example, the depth of the end sub-groove 312 in the radial direction of the sleeve portion 32 can be slightly greater than the depth of the middle sub-groove 311 in the radial direction of the sleeve portion 32, or the depth of the middle sub-groove 311 in the radial direction of the sleeve portion 32 can be slightly greater than the depth of the end sub-groove 312 in the radial direction of the sleeve portion 32.

[0082] In some embodiments, the distribution directions of the inlet flow channel 42 and the outlet flow channel 43 intersect with the distribution directions of the two gear shafts 2.

[0083] That is, the distribution directions of the inlet flow channel 42 and the outlet flow channel 43 can intersect with the distribution directions of the two gear shafts 2 at a certain angle. For example, they can intersect at a right angle, non-right angle, etc., as long as it is ensured that the oil can smoothly enter and leave the pump chamber 48.

[0084] Thus, by the cross distribution setting, the distribution direction of the meshing parts of the gear part 22 conforms to the distribution directions of the inlet flow channel 42 and the outlet flow channel 43, enabling the oil to smoothly enter and leave the pump chamber 48, which is beneficial to reducing the oil leakage and energy loss in the pump chamber 48 and improving the conveying efficiency of the gear pump 100.

[0085] In some embodiments, the distribution directions of the inlet flow channel 42 and the outlet flow channel 43 are perpendicular to the distribution directions of the two gear shafts 2.

[0086] Specifically, that is, the distribution directions of the inlet flow channel 42 and the outlet flow channel 43 can intersect at a right angle with the distribution directions of the two gear shafts 2. For example, the inlet flow channel 42 and the outlet flow channel 43 can be distributed in the left-right direction, and the two gear shafts 2 can be distributed in the front-back direction, or the inlet flow channel 42 and the outlet flow channel 43 can be distributed in the front-back direction, and the two gear shafts 2 can be distributed in the left-right direction.

[0087] With such a setting, it is beneficial for the oil to more smoothly enter and leave the pump chamber 48, reducing the resistance and energy loss during the oil flow, thereby improving the operating efficiency of the gear pump 100.

[0088] During actual operation, since the distribution directions of the inlet flow channel 42 and the outlet flow channel 43 are perpendicular to the distribution directions of the two gear shafts 2, the oil flows along a direction perpendicular to the gear shafts 2 when entering and leaving the pump chamber 48, enabling the oil to be more evenly distributed in the pump chamber 48, reducing the impact and wear on the gear shafts 2, thereby extending the service life of the gear pump 100, and enabling the oil to more smoothly and stably enter and leave the pump chamber 48, reducing the resistance, making the gear pump 100 operate more smoothly, and reducing the generation of noise and vibration.

[0089] In some other embodiments, the inlet flow direction of the inlet flow channel 42 coincides with the outlet flow direction of the outlet flow channel 43, and the meshing part of the two gear parts 22 is located on the extending direction of the inlet flow channel 42.

[0090] Specifically, the inlet flow direction of the inlet flow channel 42 coincides with the outlet flow direction of the outlet flow channel 43, that is, the inlet flow direction of the inlet flow channel 42 and the outlet flow direction of the outlet flow channel 43 are on the same horizontal line. For example, it can be the left-right direction, the front-back direction, etc. In this way, the flow path of the oil is greatly simplified. The oil directly enters the pump chamber 48 from the inlet flow channel 42, and then is pushed by the rotation of the gears of the gear part 22 and discharged through the outlet flow channel 43 along the path in the same direction, reducing the turning and flow resistance of the oil, thereby improving the flow efficiency.

[0091] The meshing portion of the two gear parts 22 is located in the extending direction of the inlet flow passage 42. In this way, the normal operation of the gear pump 100 can be ensured. Through the continuous rotation of the gear parts 22, the high-pressure and low-pressure regions in the pump chamber 48 change continuously, realizing the continuous transportation of the oil fluid. The oil fluid can be sucked into the pump chamber 48 through the inlet flow passage 42 in the low-pressure region, and the meshing of the gears in the pump chamber 48 pushes the oil fluid into the high-pressure region. The high-pressure region pushes the oil fluid to be discharged through the outlet flow passage 43, thus ensuring the stable and reliable operation of the gear pump 100.

[0092] In some embodiments, a relief groove 34 is formed at one end of the connection portion of the two sleeve parts 32 facing the inside of the pump chamber 48.

[0093] Specifically, during the operation of the gear pump 100, in order to ensure the smoothness of gear transmission, strictly isolate the oil suction area and the oil discharge area, and ensure the continuity of oil supply of the gear pump 100, according to the gear meshing principle, it is required that the contact ratio of gear meshing is greater than 1. On this basis, due to the continuous meshing and separation of the gears, before the previous pair of gears disengages, the next pair of gears has already engaged. During the period when the two pairs of gears are meshing simultaneously, a part of the oil fluid is trapped in the closed oil cavity formed by the two pairs of gears, which is neither connected to the oil suction area nor the oil discharge area. The volume of this closed oil cavity gradually decreases with the rotation of the gears at first, and then gradually increases. When the volume of the closed oil cavity decreases, the oil fluid trapped in the oil cavity is squeezed and extruded from the gap, generating a very high pressure, causing the oil fluid to heat up and the load to increase; when the volume of the closed oil cavity increases, it will cause a local vacuum and cavitation phenomenon. These phenomena will cause strong vibration and noise of the gear pump 100, resulting in the oil trapping phenomenon.

[0094] Therefore, the relief groove 34 is provided to solve the oil trapping problem, that is, while ensuring that the inlet flow passage 42 and the outlet flow passage 43 are not connected to each other, the trapped oil volume is communicated with the inlet flow passage 42 and the outlet flow passage 43, so as to prevent the oil fluid from staying in the pump chamber 48 due to being unable to be discharged in time, and ensure the normal operation of the gear pump 100.

[0095] Such as Figure 1 、 Figures 2 - 4As shown in the figure, at one end of the connection between the two sleeve parts 32 facing the pump chamber 48, that is, at the bottom of the shaft sleeve 3, a relief groove 34 is provided, which facilitates the connection between the relief groove 34 and the pump chamber 48, enabling the relief groove 34 to effectively function. When the oil fluid flows through the relief groove 34, it can enter the relief groove 34 for backflow, realizing the effective transfer and dispersion of pressure, thereby reducing the formation of local high pressure, ensuring the stability of the pressure inside the gear pump 100, enabling the trapped oil volume to communicate with the inlet flow channel 42 and the outlet flow channel 43, so that the oil fluid remaining in the pump chamber 48 can be discharged in time, avoiding the repeated extrusion and release of the oil fluid in the closed volume, generating pressure fluctuations, noise, and vibration, avoiding the occurrence of the trapped oil problem, thus keeping the oil fluid flow in the pump chamber 48 smooth, avoiding the ineffective flow of the oil fluid, and improving the working efficiency and volumetric efficiency of the gear pump 100.

[0096] In addition, the design of the relief groove 34 can also increase the flow path and heat dissipation area of the oil fluid, which is beneficial to reducing the temperature of the oil fluid, improving the working efficiency and stability of the gear pump 100. And since high temperature and high pressure will cause the components of the gear pump 100 to wear more severely, the relief groove 34 can reduce the wear and damage of the components of the gear pump 100 by reducing the oil fluid temperature and pressure fluctuations, thereby extending the service life of the gear pump 100.

[0097] Therefore, through the setting of the relief groove 34, the pressure inside the pump chamber 48 can be effectively released, the pressure can be balanced, the occurrence of the trapped oil phenomenon can be reduced, the temperature and wear of the gear pump 100 can be reduced, and thus the efficiency and performance of the gear pump 100 can be effectively improved.

[0098] In some embodiments, relief grooves 34 are provided on both sides of one end of the connection between the two sleeve parts 32 facing the inside of the pump chamber 48, and the relief grooves 34 on both sides are asymmetrically distributed.

[0099] Specifically, as Figures 2 - 4 shown, relief grooves 34 are provided at the bottoms on both sides of one end of the connection between the two sleeve parts 32 facing the inside of the pump chamber 48, that is, at the bottoms on both sides of the connection between the two sleeve parts 32 located in the high-pressure area and the low-pressure area. The extending direction of the relief groove 34 is perpendicular to the axial direction of the shaft sleeve 3. One side of the relief groove 34 extends towards the direction of the inlet flow channel 42, which is beneficial to the connection between the trapped oil volume and the inlet flow channel 42, so that the trapped oil flows towards the inlet flow channel 42. The other side of the relief groove 34 extends towards the direction of the outlet flow channel 43, which is beneficial to the connection between the trapped oil volume and the outlet flow channel 43, so that the trapped oil flows towards the outlet flow channel 43. Thus, the trapped oil problem can be effectively solved.

[0100] The unloading grooves 34 on both sides are asymmetrically distributed, that is, the unloading grooves 34 on both sides are set to be different. For example, the shapes, sizes, depths or positions relative to the center line of the connection of the two unloading grooves 34 are not exactly the same. In practice, the extension length of the unloading groove 34 on one side can be set to 3 mm, 4 mm, 5 mm, etc., and the extension length of the unloading groove 34 on the other side can be set to 4.5 mm, 6 mm, etc., and there is a certain distance between the two unloading grooves 34. Specifically, the unloading groove 34 can be flexibly set according to the actual situation and requirements, not limited to what is described in this embodiment, as long as the asymmetric distribution can achieve the effect.

[0101] Thus, by setting the unloading grooves 34 on both sides to be asymmetrically distributed, it is beneficial to better disperse and guide the oil flow, make the oil flow more smoothly in the pump chamber 48, thereby improving the flow efficiency. Moreover, the asymmetric unloading grooves 34 can better adapt to the pressure changes in the pump chamber 48 to ensure the stable operation of the gear pump 100 under different working conditions, better balance the pressure distribution in the pump chamber 48 to reduce the vibration and noise caused by uneven pressure, and make the closed volume communicate with the outflow passage 43 when the volume decreases and communicate with the inflow passage 42 when the volume increases, thereby further effectively solving the problem of trapped oil.

[0102] In some embodiments, the number of teeth of both gear parts 22 is M, and it satisfies: 12 ≤ M ≤ 15.

[0103] That is to say, the number of teeth M of the two gear parts 22 can be set to 12, 13, 14 or 15. The number of teeth M of the gear part 22 affects the flow rate, rotational speed and torque of the gear pump 100. A smaller number of teeth can provide a larger oil flow rate discharge, but may increase noise and vibration. On the contrary, a larger number of teeth can reduce noise and vibration, but will correspondingly reduce the oil flow rate discharge.

[0104] By setting the number of teeth M of the two gear parts 22 within a reasonable range between 12 and 15, the oil flow rate discharge, noise and vibration of the gear pump 100 can reach the best effect. The specific number of teeth selection can be flexibly adjusted according to actual needs. For example, when higher rotational speed and oil flow rate discharge are required, the number of teeth close to 12 can be selected, and when low noise and vibration are required, the number of teeth close to 16 can be selected.

[0105] In other embodiments, the contact ratio of the two gear parts 22 is A, and it satisfies: 1.5 ≤ A ≤ 2.0.

[0106] That is to say, the meshing overlap A of the two gear parts 22 can be set to 1.5, 1.6, 1.7, 1.8, 1.9 or 2.0. The meshing overlap is used to measure the number of tooth pairs simultaneously involved in the meshing process of the gears. A higher meshing overlap can reduce the impact and noise when the gear parts 22 are meshing, and improve the transmission smoothness. Correspondingly, a lower meshing overlap increases the impact and noise when the gear parts 22 are meshing, and reduces the transmission smoothness.

[0107] The meshing overlap of the gear portion 22 cannot be set to be too large or too small. When the meshing overlap is too small, the transmission smoothness will be reduced. For example, when it is less than 1, the transmission of the gear portion 22 will be discontinuous, and the inlet flow channel 42 and the outlet flow channel 43 will be instantly connected, causing the high-pressure oil to flow from the outlet flow channel 43 to the inlet flow channel 42, and the load borne by a single gear tooth will increase. Fewer gear teeth need to bear the same load, which will accelerate the wear and fatigue of the gear teeth.

[0108] Although a larger value will result in smoother transmission, it is easy to cause oil trapping. Too high a degree of overlap may lead to uneven distribution of contact pressure between gears, which will reduce the sealing performance in some areas and cause oil leakage, thereby reducing the volumetric efficiency of the gear pump 100 and increasing the difficulty of process processing.

[0109] By setting the meshing overlap A of the two gear parts 22 within a reasonable range of 1.5 to 2.0 and coordinating the setting of the asymmetric unloading groove 34, not only the oil trapping problem is effectively solved, but also the transmission stability is improved, so that the gear pump 100 has extremely low noise and vibration during operation; the higher meshing overlap also reduces the processing difficulty of the gear part 22, effectively improves the sealing of the gear pump, avoids oil leakage, and further improves the volumetric efficiency of the gear pump 100 and the discharge flow of the gear pump 100.

[0110] In some other embodiments, the pressure angles of the two gear parts 22 are both B, and satisfy: 23°≤B≤26°.

[0111] That is to say, the pressure angle B of the two gear parts 22 can be set to 23°, 24°, 25° or 26°. The pressure angle of the gear part 22 affects the transmission performance and load-bearing capacity of the gear part 22. A smaller pressure angle can improve the transmission efficiency but reduce the load-bearing capacity. On the contrary, a larger pressure angle can increase the load-bearing capacity but reduce the transmission efficiency.

[0112] By setting the pressure angle B of the two gear parts 22 within a reasonable range of 23° to 26°, the transmission efficiency of the gear pump 100 can be effectively improved, and excessive impact, noise and vibration of the gear parts 22 during the meshing process can be avoided, thereby improving the stability and reliability of the gear pump 100.

[0113] Therefore, by setting the number of teeth, meshing overlap and pressure angle of the gear part 22 within a reasonable range and cooperating with the asymmetric unloading groove 34, the manufacturing difficulty of the gear pump 100 is reduced, and the transmission stability, transmission efficiency and discharge flow of the gear pump 100 are effectively improved, the noise and vibration are reduced, and the sealing performance of the gear pump 100 is improved, thereby greatly improving the volumetric efficiency and working efficiency of the gear pump 100, and improving the working reliability and stability.

[0114] In some embodiments, the inner diameter of the outflow channel 43 is smaller than the inner diameter of the inflow channel 42 .

[0115] Specifically, the gear pump 100 draws the oil from the inlet flow channel 42 into the pump chamber 48 and pushes the oil from the pump chamber 48 into the outlet flow channel 43 through the rotation of the meshing gear parts 22, and then discharges the oil. Therefore, the oil is at a lower pressure on the side close to the inlet flow channel 42, and the inner diameter of the inlet flow channel 42 can be set larger to reduce the flow resistance, so that the oil is more easily drawn into the pump chamber 48.

[0116] On the side close to the outlet flow channel 43, due to the squeezing effect of the gear part 22, the oil is pressurized and pushed out. At this time, the pressure of the oil increases, and the inner diameter of the outlet flow channel 43 can be set smaller. The smaller inner diameter of the channel can control the flow rate and flow velocity of the oil, so that the oil can maintain a certain flow velocity and flow rate, thereby avoiding noise and energy loss caused by excessive flow velocity, and greatly reducing the radial force of the outlet flow channel 43 without affecting the pressure of the outlet flow channel 43, thereby maintaining the stability of the oil under high pressure.

[0117] Therefore, by setting the inner diameter of the outlet flow channel 43 to be smaller than the inner diameter of the inlet flow channel 42, the flow of oil can be reasonably controlled, thereby greatly reducing the radial force at the outlet flow channel 43, while keeping the pressure of the outlet flow channel 43 stable, and cooperating with the radial force balancing groove 31 to reduce the unbalanced radial force of the sleeve 3, the gear pump 100 can be made more stable, further reducing oil leakage and reducing the degree of wear of the gear pump 100.

[0118] In some embodiments, the housing 1 includes a first mounting hole 111, a mounting space 13, and a second mounting hole 121 that are connected in sequence, and the gear shaft 2 includes a first shaft segment 21, a gear portion 22, and a second shaft segment 23 that are connected in sequence; wherein, the sleeve 3 is sleeved on the outside of the first shaft segment 21 and is located in the mounting space 13 together with the gear portion 22, and a mating portion 35 that is penetrated through the first mounting hole 111 is formed at the free end of the sleeve 3, and the second shaft segment 23 is rotatably penetrated through the second mounting hole 121.

[0119] Specifically, Figure 1As shown, the housing 1 includes a first mounting hole 111, a mounting space 13, and a second mounting hole 121, and the first mounting hole 111, the mounting space 13, and the second mounting hole 121 are sequentially connected from top to bottom, and the gear shaft 2 includes a first shaft section 21, a gear portion 22, and a second shaft section 23 that are sequentially connected. Among them, the first mounting hole 111 is used to install the upper half of the gear shaft 2, that is, part of the first shaft section 21, and the second mounting hole 121 is used to install the lower half of the gear shaft 2, that is, the second shaft section 23. The inner diameters of the first mounting hole 111 and the second mounting hole 121 are both larger than the inner diameter of the mounting space 13, that is, the space of the mounting space 13 is larger, which is conducive to the installation of the sleeve 3 and the first shaft section 21.

[0120] The sleeve 3 is sleeved outside the first shaft section 21 to protect the first shaft section 21, reduce the friction and wear between the first shaft section 21 and the inner wall of the installation space 13, and improve the rotation accuracy and stability of the gear shaft 2. In practice, after the sleeve 3 is sleeved outside the first shaft section 21, it is installed in the installation space 13 together with the gear part 22. The inner bottom wall at the connection between the installation space 13 and the second installation hole 121 axially supports and fixes the gear part 22 to ensure the stable rotation of the gear part 22. The free end of the sleeve 3 is as shown in FIG. Figure 1 The upper end of the shaft sleeve 3 shown in the figure is formed with a matching portion 35 that is penetrated into the first mounting hole 111. The matching portion 35 is constructed as a boss, which is penetrated into the first mounting hole 111, so that the shaft sleeve 3 can be firmly connected to the housing 1, and also provides support and positioning for the first shaft segment 21; the second shaft segment 23 is penetrated into the second mounting hole 121 and can rotate in the second mounting hole 121 relative to the housing 1.

[0121] Therefore, by installing the gear shaft 2, the gear part 22 and the sleeve 3 in the housing 1 in an orderly manner, the gear shaft 2 and the gear part 22 are effectively positioned and installed, thereby realizing efficient and stable power transmission and improving the transportation efficiency of the oil.

[0122] In some embodiments, the shell 1 includes an upper cover 11 and a lower shell 12, the upper cover 11 is detachably connected to the upper end of the lower shell 12, the upper cover 11 and the lower shell 12 together define an installation space 13, a first installation hole 111 is formed in the upper cover 11, and a second installation hole 121 is formed in the lower shell 12.

[0123] Specifically, Figure 1As shown, the housing 1 can be integrally constructed as a cylindrical structure, and of course, it can also be of other shapes. The housing 1 can be set as a split structure, including an upper cover 11 and a lower housing 12, and the upper cover 11 and the lower housing 12 can be connected by detachable connection methods such as bolt connection to realize the relative disassembly of the upper cover 11 and the lower housing 12, which is beneficial to the installation of the components inside the housing 1. And when the upper housing, the lower cover or the gear shaft 2 is damaged, it is convenient to disassemble for replacement and repair, which is flexible and convenient. Among them, the first mounting hole 111 is arranged on the upper cover 11, the upper cover 11 is open downward, the second mounting hole 121 is arranged on the lower housing 12, the lower housing 12 is open upward, and when the upper cover 11 and the lower housing 12 are connected, they jointly define an installation space 13, that is, the top of the installation space 13 is formed on the upper cover 11, and the bottom is formed on the lower housing 12.

[0124] In this way, during actual installation, the second shaft section 23 can be first passed through the second mounting hole 121, and then the shaft sleeve 3 is sleeved on the first shaft section 21. At this time, the bottom of the installation space 13 stably supports the gear part 22, thus realizing the installation of the gear shaft 2 on the lower housing 12. After that, the upper cover 11 can be covered on the lower housing 12, so that the mating part 35 of the shaft sleeve 3 passes through the first mounting hole 111, thus realizing the installation of the gear shaft 2 on the upper cover 11. In order to accurately position the installation, positioning posts 44 can also be set when installing the upper cover 11 or the lower housing 12 to achieve precise positioning installation.

[0125] In actual design, a sealing ring 46 can be arranged at the lower end of the gear part 22 for sealing to prevent oil from leaking downward, a sealing ring 46 can be arranged at the upper end of the shaft sleeve 3 to seal the upper end of the shaft sleeve 3 to prevent oil from leaking from the upper end of the shaft sleeve 3, and a retaining ring 45 can also be arranged at the upper end of the shaft sleeve 3 to limit the shaft sleeve 3 to prevent the shaft sleeve 3 from generating excessive offset, so as to further improve the sealing performance of the gear pump 100 and improve the effect of reducing oil leakage.

[0126] The present utility model also proposes a suspension lifting mechanism.

[0127] The suspension lifting mechanism according to the embodiment of the present utility model includes the gear pump 100 of any one of the above embodiments.

[0128] Specifically, the suspension lifting mechanism can lift or lower the height of the vehicle axle to meet different driving requirements. The gear pump 100 can be used as the power source of the suspension lifting mechanism to provide high-pressure oil for it. Then, the hydraulic cylinder in the suspension lifting mechanism can convert the high-pressure oil into mechanical energy to realize the lifting and lowering movement of the axle.

[0129] In the gear pump 100, by providing radial force balance grooves 31 on both sides of the outer peripheral wall of the bushing 3, and connecting the radial force balance grooves 31 with the floating cavity, the high-pressure hydraulic oil in the floating cavity can flow into the radial force balance grooves 31, thereby balancing the radial force received by the bushing 3, keeping the positions of the bushing 3 and the gear shaft 2 stable, and preventing excessive shaking and tilting of the bushing 3 and the gear shaft 2, which may cause oil leakage. Therefore, the volumetric efficiency of the gear pump 100 can be greatly improved, and the wear degree and noise of the gear pump 100 can be reduced.

[0130] By arranging the above-mentioned gear pump 100 with high volumetric efficiency, low noise, high flow rate and low wear in the suspension lifting mechanism, due to the high oil transportation efficiency and large flow rate of the gear pump 100, the action speed of the suspension lifting mechanism can be accelerated, and the lifting efficiency can be improved. Moreover, the oil discharge of the gear pump 100 is stable, which can keep the suspension lifting mechanism stable during the lifting and lowering process, reduce fluctuations. The gear pump 100 with low wear can also extend the service life of the suspension lifting mechanism and reduce costs. Therefore, the overall performance of the suspension lifting mechanism is greatly improved.

[0131] The present utility model also proposes a vehicle.

[0132] The vehicle according to the embodiment of the present utility model includes the suspension lifting mechanism of any one of the above embodiments.

[0133] By arranging the above-mentioned suspension lifting mechanism, the vehicle according to the embodiment of the present utility model can maintain good, stable and efficient lifting performance under various working conditions, improve fuel economy, thereby enhancing the user experience and ride comfort.

[0134] In the description of this specification, the description with reference to terms such as "one embodiment", "some embodiments", "schematic embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present utility model. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0135] Although the embodiments of the present utility model have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and purposes of the present utility model. The scope of the present utility model is defined by the claims and their equivalents.

Claims

1. A gear pump, characterized in that: include: A shell, wherein the shell is provided with an inlet flow channel, an outlet flow channel and a floating flow channel; A gear shaft and a sleeve, wherein the gear shaft is rotatably mounted on the housing, the gear shaft is provided with a driving part, the sleeve is sleeved outside the gear shaft, the sleeve and the housing define a pump chamber for accommodating the driving part, and the sleeve defines a floating chamber with the housing at one end away from the driving part; Among them, the inlet flow channel and the outlet flow channel are respectively connected to the two sides of the pump chamber, one end of the floating flow channel is connected to the outlet flow channel and the other end is connected to the floating chamber, and radial force balancing grooves are provided on both sides of the outer peripheral wall of the sleeve and are respectively connected to the floating chamber.

2. The gear pump according to claim 1, characterized in that: There are two gear shafts, the driving part is configured as a gear part, the gear parts of the two gear shafts are meshed, the sleeve includes two connected sleeve parts, the two sleeve parts are respectively sleeved outside the two gear shafts in a one-to-one correspondence and are axially distributed relative to the corresponding gear parts; Guide grooves are formed on both sides of the connection between the outer peripheral walls of the two sleeve parts. The guide grooves extend along the axial direction of the sleeve. The floating cavity is connected with the radial force balance groove through the guide grooves on the corresponding sides.

3. The gear pump according to claim 2, characterized in that: The radial force balancing groove includes a middle sub-groove and two end sub-grooves, the two end sub-grooves are respectively arranged on the outer peripheral walls of the two sleeve parts, the middle sub-groove is connected with the guide groove, the middle sub-groove is connected between the two end sub-grooves, and the width of the end sub-groove along the axial direction of the sleeve part is greater than the width of the middle sub-groove along the axial direction of the sleeve part.

4. The gear pump according to claim 3, characterized in that: The two end sub-grooves are symmetrically distributed at two ends of the middle sub-groove; And / or, a depth of the end sub-groove along the radial direction of the sleeve portion is the same as a depth of the middle sub-groove along the radial direction of the sleeve portion.

5. The gear pump according to claim 2, characterized in that: The distribution direction of the inlet flow channel and the outlet flow channel intersects with the distribution direction of the two gear shafts; And / or, the inflow direction of the inflow channel coincides with the outflow direction of the outflow channel, and the meshing point of the two gear parts is located in the extension direction of the inlet channel.

6. The gear pump according to claim 2, characterized in that: A relief groove is formed at one end of the connection between the two sleeve parts facing the pump chamber.

7. The gear pump according to claim 6, characterized in that The connection between the two sleeve parts is provided with the unloading grooves on both sides of one end facing the pump chamber, and the unloading grooves on both sides are distributed asymmetrically.

8. The gear pump according to claim 2, characterized in that: The number of teeth of the two gear parts is M and satisfies: 12≤M≤15; And / or, the meshing overlap of the two gear parts is A, and satisfies: 1.5≤A≤2.0; And / or, the pressure angles of the two gear parts are both B, and satisfy: 23°≤B≤26°.

9. The gear pump according to claim 1, characterized in that: The inner diameter of the outflow channel is smaller than the inner diameter of the inflow channel.

10. The gear pump according to claim 1, characterized in that The housing comprises a first mounting hole, a mounting space and a second mounting hole which are connected in sequence, and the gear shaft comprises a first shaft section, a gear part and a second shaft section which are connected in sequence; Among them, the sleeve is sleeved outside the first shaft section and is located in the installation space together with the gear part. The free end of the sleeve is formed with a matching part penetrated into the first installation hole, and the second shaft section is rotatably penetrated into the second installation hole.

11. The gear pump according to claim 10, characterized in that The shell includes an upper cover and a lower shell, the upper cover is detachably connected to the upper end of the lower shell, the upper cover and the lower shell together define the installation space, the first installation hole is formed in the upper cover, and the second installation hole is formed in the lower shell.

12. A suspension lifting mechanism, characterized in that: A gear pump comprising the gear pump described in any one of claims 1-11.

13. A vehicle, characterized in that: Includes the suspension lifting mechanism as described in claim 12.

Images