Internal gearing linear conjugate / involute gear pump and active suspension electro-hydraulic pump assembly

Abstract

The invention discloses an internal meshing linear conjugate / involute gear pump and active suspension electro-hydraulic pump assembly, which is characterized in that a first gear with external teeth and a second gear with internal teeth are arranged in a pump shell, and the first gear and the second gear are meshed with each other in a meshing area and form a fluid space far away from the meshing area; a filling piece is further arranged to divide the fluid space into a first fluid cavity and a second fluid cavity on the two sides in the circumferential direction, and the first fluid cavity and the second fluid cavity communicate with a first fluid opening and a second fluid opening in the pump shell correspondingly. According to the embodiment, the first gear and the second gear are arranged to be in the linear conjugate tooth shape, compared with a mainstream involute tooth shape, the linear conjugate tooth shape does not have the oil trapping phenomenon in a meshing area, the oil trapping problem is greatly reduced, the tooth number of the first gear and the tooth number of the second gear are arranged to be the co-prime tooth number ratio, the resonance generation probability is reduced, and the service life of the gear is prolonged. Therefore, the problems of low efficiency, abnormal abrasion, vibration and noise caused by the oil trapping phenomenon of the existing internal gearing involute gear pump are solved.

Description

Technical Field

[0001] The present invention belongs to the technical field of internal meshing gear pumps, and in particular relates to an internal meshing linear conjugate / involute gear pump and an active suspension electro-hydraulic pump assembly. Background Art

[0002] Internal meshing involute gear pumps are widely used in many industrial fields such as hydraulic transmission systems, lubrication systems, fuel supply systems, etc. due to their compact structure, small flow pulsation, relatively low noise, and good self-priming performance. They serve as important power components to provide high-pressure oil.

[0003] Over the course of long-term use and performance improvements, existing internal involute gear pumps have exposed several critical design flaws that impact their reliability, efficiency, and service life. These existing internal involute gear pumps suffer from inappropriate design aspects, including the drive structure, tooth count (ratio), gear parameter design, unloading groove structure and distribution, moving part clearances, and cooling or lubrication channel layout of their active gears. These flaws can easily lead to oil trapping (the inability to drain or replenish oil within a sealed cavity), low efficiency, abnormal wear, vibration, and noise, negatively impacting the pump's efficiency and service life.

[0004] For example, poor design of gear ratio and gear parameters will lead to increased gear contact stress, accelerated abnormal wear (such as pitting and bonding), and vibration and noise; when there is a common denominator in the design of the tooth ratio of the internal meshing pump head, harmonic resonance noise may be generated under specific working conditions, and the tooth profile design is mainly based on the involute profile, which may cause oil trapping. Summary of the Invention

[0005] The technical problem to be solved by the present invention is to provide an internal meshing linear conjugate / involute gear pump and an active suspension electro-hydraulic pump assembly to solve the problems of oil trapping in existing internal meshing involute gear pumps, which lead to low efficiency, abnormal wear, vibration and noise.

[0006] In order to solve the above problems, the technical solution of the present invention is: The present invention provides an internally meshing linear conjugate gear pump for an active suspension electro-hydraulic pump, comprising: a pump housing defining a working space therein, the pump housing being provided with a first fluid port and a second fluid port communicating with the working space; an internally meshing gear set arranged in the working space, comprising a first gear having external teeth and a second gear having internal teeth; The first gear is rotatably arranged along a first axis, and the first gear is configured to rotate under the drive of an external rotating shaft; The second gear is rotatably arranged along a second axis different from the first axis; the second gear is configured to mesh with the first gear in an engagement area and form a fluid space away from the engagement area between the first gear and the second gear; a filling member arranged in the fluid space and dividing the fluid space into a first fluid chamber and a second fluid chamber located on both sides thereof in a circumferential direction, wherein the first fluid chamber is connected to the first fluid port via a first fluid channel, and the second fluid chamber is connected to the second fluid port via a second fluid channel; The first gear and the second gear have linear conjugate tooth profiles, and the number of teeth of the first gear and the number of teeth of the second gear are in a mutually prime tooth ratio.

[0007] In the internally meshing linear conjugate gear pump for the active suspension electro-hydraulic pump of the present invention, the gear parameters of the first gear and the second gear include: Tooth profile half angle β=25.5°~26.5°, pitch circle tooth thickness coefficient ks=4 / 15~2 / 5, tooth addendum height coefficient hax=0.58~0.59, tooth root height coefficient hfx=0.78~0.79, overlap degree ε=1.05~1.15.

[0008] The internal meshing linear conjugate gear pump for the active suspension electro-hydraulic pump of the present invention also includes two axial compensation units respectively arranged at the axial ends of the internal meshing gear set; both of the axial compensation units are configured to be axially attached to the internal meshing gear set under the action of the compensation force, and the axial compensation units close to the first fluid port and the second fluid port form the first fluid channel and the second fluid channel, wherein the axial compensation unit is attached to the first gear and / or the second gear.

[0009] The internal meshing linear conjugate gear pump for the active suspension electro-hydraulic pump of the present invention is further provided with a third fluid chamber located between the first fluid chamber and the second fluid chamber in the fluid space, and the fluid pressure in the third fluid chamber is located between the first fluid chamber and the second fluid chamber; wherein the axial compensation unit is provided with an oil channel connected to the third fluid chamber, and the oil channel is configured to guide the oil in the third fluid chamber into the side of the axial compensation unit away from the internal meshing gear set to balance the deflection force acting on the axial compensation unit by the fluid pressure difference between the first fluid chamber and the second fluid chamber.

[0010] In the internally meshing linear conjugate gear pump for an active suspension electro-hydraulic pump of the present invention, the axial compensation unit includes an axial floating plate and an axial elastic member, the ends of the axial elastic member being respectively attached to the pump housing and the axial floating plate; the axial elastic member near the first fluid port and the second fluid port cooperates with the axial floating plate to form the first fluid channel and the second fluid channel, which are not connected to each other, and a pressure balance chamber located on the side of the axial floating plate facing away from the internally meshing gear set; The oil channel is opened on the axial floating plate, and the pressure balance chamber is connected to the oil channel.

[0011] The internal meshing linear conjugate gear pump for the active suspension electro-hydraulic pump of the present invention is provided with an extended blind groove extending from the first fluid chamber and the second fluid chamber along the filling piece respectively on the mating surface of the axial floating plate facing the internal meshing gear group, and each of the extended blind grooves is provided with a unloading groove group connected thereto, wherein the unloading grooves in each of the unloading groove groups cover the areas where the teeth of the first gear and the second gear are located.

[0012] The internal meshing linear conjugate gear pump for the active suspension electro-hydraulic pump of the present invention comprises a crescent plate, two radial compensation members and two floating plates; The crescent plate is rotatably mounted on the pump housing via a fixing pin, and floating grooves are respectively provided on both sides of the outer ring surface or the inner ring surface of the crescent plate in the circumferential direction; the floating plates are respectively arranged in the floating grooves; the radial compensation members are respectively arranged between the corresponding floating plates and the floating grooves, and the radial compensation members are configured to push the floating plates away from the crescent plate in the radial direction.

[0013] The internally meshing linear conjugate gear pump for the active suspension electro-hydraulic pump of the present invention, the radial compensation part includes an adjustment pin and an adjustment spring, an adjustment groove with an opening toward the floating plate is provided in the floating groove, the adjustment pin and the adjustment spring are arranged in the adjustment groove, and the adjustment spring is configured to push the adjustment pin close to the floating plate.

[0014] The internal meshing linear conjugate gear pump for the active suspension electro-hydraulic pump of the present invention, under the action of the radial compensating member, The fitting clearance between the crescent plate and the tooth top of the first gear is in the range of 0-0.003mm, and the fitting clearance between the floating plate and the tooth top of the second gear is in the range of 0-0.003mm; Alternatively, the fitting clearance between the crescent plate and the tooth top of the second gear is in the range of 0-0.003 mm, and the fitting clearance between the floating plate and the tooth top of the first gear is in the range of 0-0.003 mm.

[0015] The internal meshing linear conjugate gear pump for the active suspension electro-hydraulic pump of the present invention, the pump housing includes an oil inlet plate and an oil outlet plate; the oil inlet plate covers the oil outlet plate and cooperates to form the working space, the oil outlet plate is installed on the external motor, and the first fluid port and the second fluid port are provided on the oil inlet plate.

[0016] The internal meshing linear conjugate gear pump for the active suspension electro-hydraulic pump of the present invention has a gear cavity bushing provided in the inner cavity of the oil outlet plate, and the gear cavity bushing cooperates with the inner side surfaces of the oil inlet plate and the oil outlet plate in the axial direction to form a gear cavity for installing the internal meshing gear set; wherein the inner surface of the gear cavity bushing is coated with a friction-reducing coating.

[0017] The internal meshing linear conjugate gear pump for the active suspension electro-hydraulic pump of the present invention has a driving hole for connecting to an external rotating shaft on the first gear, and the driving hole is a regular hexagonal driving hole or a spline hole.

[0018] The present invention provides an internal meshing involute gear pump for an active suspension electro-hydraulic pump, comprising: a pump housing defining a working space therein, the pump housing being provided with a first fluid port and a second fluid port communicating with the working space; an internally meshing gear set arranged in the working space, comprising a third gear having external teeth and a fourth gear having internal teeth; The third gear is rotatably arranged along the first axis, and the third gear is configured to rotate under the drive of the external rotating shaft; The fourth gear is rotatably arranged along a second axis different from the first axis; the fourth gear is configured to mesh with the third gear in an engagement area and form a fluid space away from the engagement area between the third gear and the fourth gear; a filling member arranged in the fluid space and dividing the fluid space into a first fluid chamber and a second fluid chamber located on both sides thereof in a circumferential direction, wherein the first fluid chamber is connected to the first fluid port via a first fluid channel, and the second fluid chamber is connected to the second fluid port via a second fluid channel; The third gear and the fourth gear have involute tooth profiles, and the number of teeth of the third gear and the number of teeth of the fourth gear are in a mutually prime tooth ratio.

[0019] In the internal meshing involute gear pump for the active suspension electro-hydraulic pump of the present invention, the gear parameters of the third gear and the fourth gear include: The pressure angle range is 24°~25°, the tooth top height coefficient is 0.85~0.95, the top clearance coefficient is 0.18~0.22, and the overlap range is 1.4~1.55.

[0020] The internal meshing involute gear pump for the active suspension electro-hydraulic pump of the present invention also includes two axial compensation units respectively arranged at the axial ends of the internal meshing gear set; both of the axial compensation units are configured to be axially attached to the internal meshing gear set under the action of the compensation force, and the axial compensation units close to the first fluid port and the second fluid port form the first fluid channel and the second fluid channel, wherein the axial compensation unit is attached to the third gear and / or the fourth gear.

[0021] The internal meshing involute gear pump for the active suspension electro-hydraulic pump of the present invention is further provided with a third fluid cavity located between the first fluid cavity and the second fluid cavity in the fluid space, and the fluid pressure in the third fluid cavity is located between the first fluid cavity and the second fluid cavity; wherein the axial compensation unit is provided with an oil channel connected to the third fluid cavity, and the oil channel is configured to guide the oil in the third fluid cavity into the side of the axial compensation unit away from the internal meshing gear set to balance the deflection force acting on the axial compensation unit by the fluid pressure difference between the first fluid cavity and the second fluid cavity.

[0022] In the internally meshing involute gear pump for an active suspension electro-hydraulic pump of the present invention, the axial compensation unit includes an axial floating plate and an axial elastic member, with the ends of the axial elastic member respectively affixed to the pump housing and the axial floating plate; the axial elastic member near the first fluid port and the second fluid port cooperates with the axial floating plate to form the first fluid channel and the second fluid channel, which are not connected to each other, and a pressure balance chamber located on the side of the axial floating plate facing away from the internally meshing gear set; The oil channel is opened on the axial floating plate, and the pressure balance chamber is connected to the oil channel.

[0023] The internal meshing involute gear pump for the active suspension electro-hydraulic pump of the present invention has at least two unloading groove groups provided on the mating surface of the axial floating plate facing the internal meshing gear group, and the two unloading groove groups are respectively arranged corresponding to the first fluid cavity and the second fluid cavity, and the unloading grooves in each of the unloading groove groups cover the areas where the teeth of the third gear and the fourth gear are located.

[0024] The internal meshing involute gear pump for the active suspension electro-hydraulic pump of the present invention, the filling piece includes a crescent plate, two radial compensation pieces and two floating plates; The crescent plate is rotatably mounted on the pump housing via a fixing pin, and floating grooves are respectively provided on both sides of the outer ring surface or the inner ring surface of the crescent plate in the circumferential direction; the floating plates are respectively arranged in the floating grooves; the radial compensation members are respectively arranged between the corresponding floating plates and the floating grooves, and the radial compensation members are configured to push the floating plates away from the crescent plate in the radial direction.

[0025] The internal meshing involute gear pump for the active suspension electro-hydraulic pump of the present invention, the radial compensating member includes an adjusting pin and an adjusting spring, an adjusting slot with an opening toward the floating plate is provided in the floating slot, the adjusting pin and the adjusting spring are arranged in the adjusting slot, and the adjusting spring is configured to push the adjusting pin to fit tightly against the floating plate.

[0026] The internal meshing involute gear pump for the active suspension electro-hydraulic pump of the present invention, under the action of the radial compensating member, The fitting clearance between the crescent plate and the tooth top of the third gear is in the range of 0-0.003mm, and the fitting clearance between the floating plate and the tooth top of the fourth gear is in the range of 0-0.003mm; Alternatively, the fitting clearance between the crescent plate and the tooth top of the fourth gear is in the range of 0-0.003 mm, and the fitting clearance between the floating plate and the tooth top of the third gear is in the range of 0-0.003 mm.

[0027] The internal meshing involute gear pump for the active suspension electro-hydraulic pump of the present invention, the pump housing includes an oil inlet plate and an oil outlet plate; the oil inlet plate covers the oil outlet plate and cooperates to form the working space, the oil outlet plate is installed on the external motor, and the first fluid port and the second fluid port are provided on the oil inlet plate.

[0028] The internal meshing involute gear pump for the active suspension electro-hydraulic pump of the present invention has a gear cavity bushing provided in the inner cavity of the oil outlet plate, and the gear cavity bushing cooperates with the inner side surfaces of the oil inlet plate and the oil outlet plate in the axial direction to form a gear cavity for installing the internal meshing gear set; wherein the inner surface of the gear cavity bushing is coated with a friction-reducing coating.

[0029] In the internal meshing involute gear pump for the active suspension electro-hydraulic pump of the present invention, the third gear is provided with a drive hole for connecting to an external rotating shaft, and the drive hole is a regular hexagonal drive hole or a spline hole.

[0030] An active suspension electro-hydraulic pump assembly of the present invention includes an electric motor; Also includes any one of the above-mentioned internal meshing linear conjugate gear pumps, or any one of the above-mentioned internal meshing involute gear pumps; The rotating shaft of the motor extends into the working space and is transmission-connected with the first gear or the third gear.

[0031] An active suspension electro-hydraulic pump assembly of the present invention includes two electric motors; Also includes two of the internal meshing linear conjugate gear pumps described in any one of the above items, or two of the internal meshing involute gear pumps described in any one of the above items; The two motors are both arranged in a common housing, and the rotating shafts of the two motors respectively extend into the corresponding working spaces and are transmission-connected to the first gear or the third gear.

[0032] A chassis axle of the present invention, An internally meshing linear conjugate gear pump for two active suspension electro-hydraulic pumps as described above, or an internally meshing involute gear pump for two active suspension electro-hydraulic pumps as described above; or Having the two active suspension electro-hydraulic pump assemblies mentioned above; or, An active suspension electro-hydraulic pump assembly as described above; A first hydraulically adjustable shock absorber and a second hydraulically adjustable shock absorber are respectively hydraulically connected to the internally meshing linear conjugate gear pump.

[0033] Due to the adoption of the above technical solution, the present invention has the following advantages and positive effects compared with the prior art: In one embodiment of the present invention, a first gear having external teeth and a second gear having internal teeth are arranged in a pump housing, and the first gear and the second gear mesh with each other in a meshing area to form a fluid space away from the meshing area; and a filler is further provided to divide the fluid space into a first fluid cavity and a second fluid cavity on both sides in a circumferential direction, and both are connected to a first fluid port and a second fluid port on the pump housing, respectively. When the first gear rotates forward, the first fluid cavity and the second fluid cavity are respectively a high-pressure cavity and a low-pressure cavity; when the first gear rotates reversely, the first fluid cavity and the second fluid cavity are respectively a low-pressure cavity and a high-pressure cavity. Among them, this embodiment sets the first gear and the second gear as a linear conjugate tooth profile. Compared with the mainstream involute tooth profile, the linear conjugate tooth profile does not have oil trapping in the meshing area, which greatly reduces the problem of oil trapping, improves the meshing smoothness and gear reliability life, and reduces the noise caused by gear meshing. The number of teeth of the first gear and the number of teeth of the second gear are set to a mutually prime tooth ratio, that is, there is no common divisor between the number of teeth of the first gear and the number of teeth of the second gear, which can reduce the probability of resonance, thereby solving the problem of low efficiency, abnormal wear, vibration and noise caused by oil trapping in existing internal meshing involute gear pumps. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] Figure 1 Schematic diagram of an explosion of an internal meshing linear conjugate gear pump according to the first embodiment of the present invention; Figure 2Schematic cross-sectional view of an internal meshing linear conjugate gear pump according to the first embodiment of the present invention; Figure 3 Schematic diagram of the driving hole of the first gear of the internal meshing linear conjugate gear pump according to the first embodiment of the present invention; Figure 4 This is a schematic diagram of the side of the axial floating plate of the internal meshing linear conjugate gear pump facing the internal meshing gear set according to the first embodiment of the present invention; Figure 5 Schematic diagram of the side of the axial floating plate of the internal meshing linear conjugate gear pump facing away from the internal meshing gear set according to the first embodiment of the present invention; Figure 6 Schematic diagram of an exploded view of an internal meshing involute gear pump according to a second embodiment of the present invention; Figure 7 Schematic cross-sectional view of an internal meshing involute gear pump according to a second embodiment of the present invention; Figure 8 Schematic diagram of the driving hole of the first gear of the internal meshing involute gear pump according to the second embodiment of the present invention; Figure 9 A schematic diagram of the side of the axial floating plate of the internal meshing involute gear pump facing the internal meshing gear set according to the second embodiment of the present invention; Figure 10 This is a schematic diagram of the side of the axial floating plate of the internal meshing involute gear pump facing away from the internal meshing gear set according to the second embodiment of the present invention.

[0035] Explanation of the accompanying drawings: 1. Oil outlet plate; 2. Rubber pad; 3. Axial floating plate; 4. Second gear; 5. First gear; 6. Crescent plate; 7. Floating plate; 8. Oil inlet plate; 9. External rotating shaft; 10. Adjusting pin; 11. Adjusting spring; 12. Guide pin shaft; 13. Gear cavity bushing; 14. Friction-reducing coating; 15.1. First fluid port; 15.2. First fluid cavity; 16.1. Second fluid port; 16.2. Second fluid cavity; 17. Drive hole; 18.1. First unloading groove; 18.2. Second unloading groove; 18.3. Third unloading groove; 18.4. Fourth unloading groove; 18.5. Fifth unloading groove; 19. Oil channel; 20. Third gear; 21. Fourth gear. DETAILED DESCRIPTION

[0036] The following is a detailed description of the internal meshing linear conjugate / involute gear pump and active suspension electro-hydraulic pump assembly proposed by the present invention, with reference to the accompanying drawings and specific embodiments. The advantages and features of the present invention will become more apparent from the following description and claims.

[0037] Example 1 See Figures 1 to 5In one embodiment, an internally meshing linear conjugate gear pump for an active suspension electro-hydraulic pump includes a pump housing, an internally meshing gear set, and a filling member.

[0038] A working space is defined in the pump housing, and a first fluid port 15.1 and a second fluid port 16.1 communicating with the working space are provided on the pump housing.

[0039] An internally meshing gear set is arranged within the workspace and includes a first gear 5 having external teeth and a second gear 4 having internal teeth. The first gear 5 is rotatably arranged along a first axis and is configured to rotate when driven by an external rotating shaft 9. The second gear 4 is rotatably arranged along a second axis different from the first axis. The second gear 4 is configured to mesh with the first gear 5 in an engagement zone, forming a fluid space between the first and second gears 5, away from the engagement zone.

[0040] A filler is arranged in the fluid space and divides the fluid space into a first fluid chamber 15.2 and a second fluid chamber 16.2 located on both sides of the fluid space in the circumferential direction (specifically, the fluid space enclosed by the mutually meshing first and second gears 5 and 4 and the inner cavity of the pump casing is initially divided into two parts by the meshing of the filler and the gears; these two parts are the first fluid chamber 15.2 and the second fluid chamber 16.2). The first fluid chamber 15.2 is connected to the first fluid port 15.1 via a first fluid channel, and the second fluid chamber 16.2 is connected to the second fluid port 16.1 via a second fluid channel.

[0041] When the first gear 5 rotates forward, the second gear 4 rotates in the same direction, and the volume of the first fluid chamber 15.2 gradually increases, forming a partial vacuum. Under the action of atmospheric pressure, oil enters the first fluid chamber 15.2 from the first fluid port 15.1, forming a low-pressure chamber for oil absorption. Simultaneously, the volume of the second fluid chamber 16.2 gradually decreases, squeezing the oil, increasing its pressure, and forcing it out of the second fluid port 16.1, forming a high-pressure chamber for oil discharge. Conversely, when the first gear 5 rotates counterclockwise, the second gear 4 rotates in the same direction, and the volume of the second fluid chamber 16.2 gradually increases, forming a partial vacuum. Under the action of atmospheric pressure, oil enters the second fluid chamber 16.2 from the second fluid port 16.1, forming a low-pressure chamber for oil absorption. Simultaneously, the volume of the first fluid chamber 15.2 gradually decreases, squeezing the oil, increasing its pressure, and forcing it out of the first fluid port 15.1, forming a high-pressure chamber for oil discharge.

[0042] Among them, the first gear 5 and the second gear 4 have linear conjugate tooth shapes, and the number of teeth of the first gear 5 and the number of teeth of the second gear 4 are mutually prime tooth ratios. A typical value is that the first gear 5 uses 10 teeth and the second gear 4 uses 13 teeth, but it is not limited to this tooth number pairing.

[0043] This embodiment comprises a first gear 5 having external teeth and a second gear 4 having internal teeth disposed within the pump housing. The first gear 5 and the second gear 4 mesh with each other in the meshing region, forming a fluid space away from the meshing region. Furthermore, a filler is provided to divide the fluid space into a first fluid chamber 15.2 and a second fluid chamber 16.2 on either side of the circumference, each of which is connected to the first fluid port 15.1 and the second fluid port 16.1 on the pump housing, respectively. Specifically, this embodiment configures the first gear 5 and the second gear 4 with a linear conjugate tooth profile. Compared to the mainstream involute tooth profile, the linear conjugate tooth profile does not trap oil in the meshing region, significantly reducing the problem of oil trapping, improving meshing smoothness and gear reliability and lifespan, and reducing noise caused by gear meshing. Furthermore, the number of teeth of the first gear 5 and the second gear 4 are configured to be a mutually prime ratio, i.e., the number of teeth of the first gear 5 and the number of teeth of the second gear 4 do not have a common divisor, thereby reducing the probability of resonance. This solves the problem of oil trapping in existing internal meshing linear conjugate gear pumps, which leads to low efficiency, abnormal wear, vibration, and noise.

[0044] The specific structure of the internal meshing linear conjugate gear pump for the active suspension electro-hydraulic pump of this embodiment is further described below: In this embodiment, the gear parameters of the first gear 5 and the second gear 4 include: The tooth profile half angle β is 25.5° to 26.5°, the pitch thickness coefficient ks is 4 / 15 to 2 / 5, the addendum coefficient hax is 0.58 to 0.59, the root height coefficient hfx is 0.78 to 0.79, and the contact ratio ε is 1.05 to 1.15. The preferred values ​​are the tooth profile half angle β = 26°, the pitch thickness coefficient ks = 1 / 3, the addendum coefficient hax = 0.585, the root height coefficient hfx = 0.785, and the contact ratio ε is in the range of 1.05 to 1.15.

[0045] In this embodiment, the pump housing specifically includes an oil inlet plate 8 and an oil outlet plate 1. The oil inlet plate 8 covers the oil outlet plate 1 and cooperates to form the aforementioned working space. The oil outlet plate 1 is mounted on the external motor (specifically, the side of the oil outlet plate 1 facing away from the oil inlet plate 8 can be sealedly mounted to the motor housing or the inner wall of the stator). The oil inlet plate 8 is provided with the aforementioned first fluid port 15.1 and second fluid port 16.1.

[0046] Furthermore, the inner cavity of the oil outlet plate 1 may be provided with a gear cavity bushing 13 for sliding engagement with the outer ring surface of the second gear 4. This gear cavity bushing 13, in conjunction with the axially inner side surfaces of the oil inlet plate 8 and the oil outlet plate 1, forms a gear cavity for mounting the internally meshing gear set. The inner surface of the gear cavity bushing 13 is coated with a friction-reducing coating 14, which reduces friction between the second gear 4 and the inner surface of the gear cavity bushing 13 during pump operation, thereby lowering power consumption, improving efficiency, and reducing noise and vibration.

[0047] In this embodiment, to prevent axial leakage and adjust axial clearance, the internal linear conjugate gear pump may further include two axial compensation units, one disposed axially at each end of the internal gear set. Specifically, the two axial compensation units are disposed between the internal gear set and the oil inlet plate 8 and between the internal gear set and the oil outlet plate 1, respectively. Both axial compensation units are configured to axially abut against the internal gear set under the action of a compensation force, with the axial compensation units located near the first fluid port 15.1 and the second fluid port 16.1 forming a first fluid channel and a second fluid channel. These two fluid channels are defined on the axial compensation unit between the internal gear set and the oil inlet plate 8. The axial compensation units are abutted against the first gear 5 and / or the second gear 4.

[0048] Furthermore, a third fluid chamber is formed within the fluid space, located between the first fluid chamber 15.2 and the second fluid chamber 16.2. Specifically, this chamber can be formed in the area where the filler is located. The fluid pressure within the third fluid chamber is located between the first and second fluid chambers 15.2, 16.2, i.e., a medium-pressure chamber. The axial compensation unit is provided with an oil channel 19 connected to the third fluid chamber. Oil channel 19 is configured to direct the oil within the third fluid chamber into the side of the axial compensation unit facing away from the internal gear set, thereby balancing the deflection force acting on the axial compensation unit due to the fluid pressure difference between the first and second fluid chambers 15.2, 16.2. The first fluid chamber 15.2 and the second fluid chamber 16.2 are respectively a high-pressure chamber and a low-pressure chamber. The pressures of the two are different and they are located in different areas, which will result in different forces acting on the axial compensation unit in the axial direction, making the axial compensation unit prone to deflection. By cooperating with the third fluid chamber and the oil channel 19, the other side of the axial compensation unit can be supported by a medium-pressure fluid, thereby reducing the deflection force, avoiding the problem of abnormal wear caused by the deflection of the axial compensation unit, and improving the service life of the oil pump and its efficiency during its service life.

[0049] Specifically, the axial compensation unit comprises an axial floating plate 3 and an axial elastic member, with both ends of the axial elastic member respectively attached to the pump housing and the axial floating plate 3. The axial elastic member near the first fluid port 15.1 and the second fluid port 16.1 cooperates with the axial floating plate 3 to form a first and second fluid channel, each disconnected from the other, and a pressure balance chamber located on the side of the axial floating plate 3 facing away from the internal gear set.

[0050] The aforementioned oil channel 19 is defined on the axial floating plate 3, and the pressure balance chamber is connected to the oil channel 19. Furthermore, a lubrication channel can be defined on the surface of the axial floating plate facing away from the internally meshing gear set. This lubrication channel connects to the oil channel 19 or the pressure balance chamber, and then to the outer edge of the axial floating plate. This lubrication channel allows oil to flow through the lubrication channel between the outer side of the second gear 4 and the gear chamber bushing 13 for lubrication.

[0051] The axial elastic member can be specifically a rubber pad 2. When the end face of the axial floating plate 3 rubs and wears against the first gear 5 and / or the second gear 4, the elastic force of the rubber pad 2 can be used to squeeze the axial floating plate 3 to automatically compensate for the gap. Furthermore, the axial floating plate 3 is provided with a first fluid hole and a second fluid hole. The axial elastic member can be specifically two rubber rings, which are respectively attached to the side of the axial floating plate 3 facing away from the gears and are respectively mounted on the first fluid hole and the second fluid hole. The first fluid hole cooperates with the inner surface of the rubber ring to form the aforementioned first fluid channel, and the second fluid hole cooperates with the inner surface of the rubber ring to form the aforementioned second flow channel. The outer surfaces of the two rubber rings cooperate with the surface of the axial floating plate 3 facing away from the gears to form the aforementioned pressure balance chamber.

[0052] Furthermore, an axial floating plate, on its mating surface facing the internally meshing gear set, is provided with extended blind grooves extending from the first and second fluid chambers along the filler, respectively. Each of the extended blind grooves is provided with a connected unloading groove group, allowing fluid within the two fluid chambers to enter the extended blind grooves and achieve unloading through the unloading grooves within the unloading groove group. Each unloading groove within the unloading groove group covers the area where the teeth of the first and second gears are located. The unloading grooves function to partially release the fluid pressure carried between the teeth of the first or second gear and the filler through their gradually decreasing cross-sectional area, thereby preventing this portion of fluid from being compressed and causing impact on the two gears.

[0053] Among them, each unloading groove group can include three or more unloading grooves (when the number of unloading grooves is three, the first unloading groove 18.1 corresponding to the first gear 5 (can be set to extend from the extended blind groove toward the area where the gear teeth of the first gear 5 are located), and the second unloading groove 18.2 and the third unloading groove 18.3 corresponding to the second gear 4 (can be set to extend from the extended blind groove toward the area where the gear teeth of the second gear 4 are located), the cross-section of the unloading groove can be specifically triangular, so as to take into account the reasonable unloading requirements when the first gear 5 and the second gear 4 are meshed, reduce the situation where the gear pump is trapped in oil during operation, reduce vibration and noise, and improve the life of the pump.

[0054] In this embodiment, in order to adjust the radial gap and perform gap compensation to improve efficiency, the filling piece includes a crescent plate 6 , two radial compensation pieces and two floating plates 7 .

[0055] The crescent plate 6 is rotatably mounted to the pump housing via a retaining pin (the aforementioned third fluid chamber is formed in the area where the retaining pin is located). Floating grooves are provided on either the outer or inner surface of the crescent plate 6, circumferentially on either side (one on each side of the retaining pin). Floating plates 7 are positioned within these grooves. Radial compensators are positioned between the corresponding floating plates 7 and the grooves, configured to radially push the floating plates 7 away from the crescent plate 6. This embodiment utilizes radial compensators with optimized interplay and clearance to achieve high volumetric efficiency.

[0056] Among them, the radial compensation part includes an adjusting pin 10 and an adjusting spring 11. An adjusting slot with an opening facing the floating plate 7 is provided in the floating slot. The adjusting pin 10 and the adjusting spring 11 are arranged in the adjusting slot, and the adjusting spring 11 is configured to push the adjusting pin 10 to fit tightly against the floating plate 7.

[0057] The fixing pins may specifically be two guide pin shafts 12 , which are inserted into the crescent plate 6 from both sides in the axial direction and are connected to the oil inlet plate 8 and the oil outlet plate 1 respectively.

[0058] In this embodiment, a scheme is specifically adopted in which the floating groove opens toward the first gear 5. The outer surface of the crescent plate 6 cooperates with the tooth top of the second gear 4, the adjustment pin 10 cooperates with the outer surface of the floating plate 7, the adjustment spring 11 is assembled between the crescent plate 6 and the adjustment pin 10, and the inner surface of the floating plate 7 cooperates with the tooth top of the first gear 5. The adjustment spring 11 squeezes the adjustment pin 10 and pushes the floating plate 7 closer to the tooth top of the first gear 5 to achieve gap compensation; after compensation, the fitting clearance between the tooth top of the second gear 4 and the outer surface of the crescent plate 6 is in the range of 0-0.003mm, and the fitting clearance between the tooth top of the first gear 5 and the inner surface of the floating plate 7 is in the range of 0-0.003mm.

[0059] In this embodiment, a drive hole 17 for connecting to the external rotating shaft 9 is provided on the first gear 5, wherein, in order to improve the balance of the moving parts and enhance the driving stability, and improve noise and vibration, the drive hole 17 can be set to have a symmetrical regular hexagonal drive hole 17 or a spline hole.

[0060] In order to solve or improve problems such as oil trapping, low efficiency, abnormal wear, vibration and noise, and to improve the efficiency and life of the oil pump, this embodiment proposes solutions in terms of the driving structure of the driving gear (first gear 5), gear cavity coating, gear parameters and number of teeth, clearance between moving parts and clearance adjustment device, unloading groove structure, cooling or lubricating oil channel 19 on the axial floating plate 3, etc.

[0061] Example 2 See Figures 6 to 10 In one embodiment, an internal meshing involute gear pump for an active suspension electro-hydraulic pump includes a pump housing, an internal meshing gear set, and a filling piece.

[0062] A working space is defined in the pump housing, and a first fluid port 15.1 and a second fluid port 16.1 communicating with the working space are provided on the pump housing.

[0063] An internally meshing gear set is arranged within the workspace and includes a third gear 20 having external teeth and a fourth gear 21 having internal teeth. The third gear 20 is arranged to rotate along a first axis and is configured to rotate when driven by the external rotating shaft 9. The fourth gear 21 is arranged to rotate along a second axis different from the first axis. The fourth gear 21 is configured to mesh with the third gear 20 in an engagement zone, forming a fluid space between the third and fourth gears 20, 21, away from the engagement zone.

[0064] A filler is arranged in the fluid space and divides the fluid space into a first fluid chamber 15.2 and a second fluid chamber 16.2 located on both sides of the fluid space in the circumferential direction (specifically, the fluid space enclosed by the mutually meshing third gear 20 and fourth gear 21 and the inner cavity of the pump casing is initially divided into two parts by the meshing of the filler and the gears; these two parts are the first fluid chamber 15.2 and the second fluid chamber 16.2). The first fluid chamber 15.2 is connected to the first fluid port 15.1 via a first fluid channel, and the second fluid chamber 16.2 is connected to the second fluid port 16.1 via a second fluid channel.

[0065] When the third gear 20 rotates forward, the fourth gear 21 rotates in the same direction, gradually increasing the volume of the first fluid chamber 15.2, creating a partial vacuum. Oil, under the action of atmospheric pressure, enters the first fluid chamber 15.2 from the first fluid port 15.1, forming a low-pressure chamber for oil absorption. Simultaneously, the volume of the second fluid chamber 16.2 gradually decreases, squeezing the oil, increasing its pressure, and forcing it out of the second fluid port 16.1, forming a high-pressure chamber for oil discharge. Conversely, when the third gear 20 rotates counterclockwise, the fourth gear 21 rotates in the same direction, gradually increasing the volume of the second fluid chamber 16.2, creating a partial vacuum. Oil, under the action of atmospheric pressure, enters the second fluid chamber 16.2 from the second fluid port 16.1, forming a low-pressure chamber for oil absorption. Simultaneously, the volume of the first fluid chamber 15.2 gradually decreases, squeezing the oil, increasing its pressure, and forcing it out of the first fluid port 15.1, forming a high-pressure chamber for oil discharge.

[0066] Among them, the third gear 20 and the fourth gear 21 have involute tooth profiles, and the number of teeth of the third gear 20 and the number of teeth of the fourth gear 21 are mutually prime tooth ratios. A typical value is that the third gear 20 uses 14 teeth and the fourth gear 21 uses 19 teeth, but it is not limited to this tooth number pairing.

[0067] This embodiment disposes a third gear 20 with external teeth and a fourth gear 21 with internal teeth within the pump housing. The third gear 20 and the fourth gear 21 mesh with each other in the meshing area, forming a fluid space away from the meshing area. A filler is further provided to divide the fluid space into a first fluid chamber 15.2 and a second fluid chamber 16.2 on either side of the circumference, both of which are connected to the first fluid port 15.1 and the second fluid port 16.1 on the pump housing, respectively. In this embodiment, the third gear 20 and the fourth gear 21 are configured as involute tooth profiles, and the number of teeth of the third gear 20 and the number of teeth of the fourth gear 21 are configured to have a mutually prime tooth ratio, that is, there is no common divisor between the number of teeth of the third gear 20 and the number of teeth of the fourth gear 21. This reduces the probability of resonance and avoids the generation of harmonic resonance noise, thereby resolving the vibration and noise problems associated with existing internal meshing involute gear pumps.

[0068] The specific structure of the internal meshing involute gear pump for the active suspension electro-hydraulic pump of this embodiment is further described below: In this embodiment, the pump housing specifically includes an oil inlet plate 8 and an oil outlet plate 1. The oil inlet plate 8 covers the oil outlet plate 1 and cooperates to form the aforementioned working space. The oil outlet plate 1 is mounted on the external motor (specifically, the side of the oil outlet plate 1 facing away from the oil inlet plate 8 can be sealedly mounted to the motor housing or the inner wall of the stator). The oil inlet plate 8 is provided with the aforementioned first fluid port 15.1 and second fluid port 16.1.

[0069] Furthermore, the inner cavity of the oil outlet plate 1 may be provided with a gear cavity bushing 13 for sliding engagement with the outer ring surface of the fourth gear 21. This gear cavity bushing 13, in conjunction with the axially inner side surfaces of the oil inlet plate 8 and the oil outlet plate 1, forms a gear cavity for mounting the internally meshing gear set. The inner surface of the gear cavity bushing 13 is coated with a friction-reducing coating 14, which reduces friction between the fourth gear 21 and the inner surface of the gear cavity bushing 13 during pump operation, thereby lowering power consumption, improving efficiency, and reducing noise and vibration.

[0070] In this embodiment, to prevent axial leakage and adjust axial clearance, the internal involute gear pump may further include two axial compensation units, one disposed axially at each end of the internal gear set. Specifically, the two axial compensation units are disposed between the internal gear set and the oil inlet plate 8 and between the internal gear set and the oil outlet plate 1, respectively. Both axial compensation units are configured to axially abut against the internal gear set under the action of a compensation force, with the axial compensation units located near the first fluid port 15.1 and the second fluid port 16.1 forming a first fluid channel and a second fluid channel. These two fluid channels are defined on the axial compensation unit between the internal gear set and the oil inlet plate 8. The axial compensation units are abutted against the third gear 20 and / or the fourth gear 21.

[0071] Furthermore, a third fluid chamber is formed within the fluid space, located between the first fluid chamber 15.2 and the second fluid chamber 16.2. Specifically, this chamber can be formed in the area where the filler is located. The fluid pressure within the third fluid chamber is located between the first and second fluid chambers 15.2, 16.2, i.e., a medium-pressure chamber. The axial compensation unit is provided with an oil channel 19 connected to the third fluid chamber. Oil channel 19 is configured to direct the oil within the third fluid chamber into the side of the axial compensation unit facing away from the internal gear set, thereby balancing the deflection force acting on the axial compensation unit due to the fluid pressure difference between the first and second fluid chambers 15.2, 16.2. The first fluid chamber 15.2 and the second fluid chamber 16.2 are respectively a high-pressure chamber and a low-pressure chamber. The pressures of the two are different and they are located in different areas, which will result in different forces acting on the axial compensation unit in the axial direction, making the axial compensation unit prone to deflection. By cooperating with the third fluid chamber and the oil channel 19, the other side of the axial compensation unit can be supported by a medium-pressure fluid, thereby reducing the deflection force, avoiding the problem of abnormal wear caused by the deflection of the axial compensation unit, and improving the service life of the oil pump and its efficiency during its service life.

[0072] Specifically, the axial compensation unit comprises an axial floating plate 3 and an axial elastic member, with both ends of the axial elastic member respectively attached to the pump housing and the axial floating plate 3. The axial elastic member near the first fluid port 15.1 and the second fluid port 16.1 cooperates with the axial floating plate 3 to form a first and second fluid channel, each disconnected from the other, and a pressure balance chamber located on the side of the axial floating plate 3 facing away from the internal gear set.

[0073] The aforementioned oil channel 19 is defined on the axial floating plate 3, and the pressure balance chamber is connected to the oil channel 19. Furthermore, a lubrication channel can be defined on the surface of the axial floating plate facing away from the internally meshing gear set. This lubrication channel connects to the oil channel 19 or the pressure balance chamber, and then to the outer edge of the axial floating plate. This lubrication channel allows oil to flow through the lubrication channel between the outer side of the fourth gear 21 and the gear chamber bushing 13 for lubrication.

[0074] The axial elastic member can be specifically a rubber pad 2. When the end face of the axial floating plate 3 rubs and wears against the third gear 20 and / or the fourth gear 21, the elastic force of the rubber pad 2 can be used to squeeze the axial floating plate 3 to automatically compensate for the gap. Furthermore, the axial floating plate 3 is provided with a first fluid hole and a second fluid hole. The axial elastic member can be specifically two rubber rings, which are respectively attached to the side of the axial floating plate 3 facing away from the gears and are respectively mounted on the first fluid hole and the second fluid hole. The first fluid hole cooperates with the inner surface of the rubber ring to form the aforementioned first fluid channel, and the second fluid hole cooperates with the inner surface of the rubber ring to form the aforementioned second flow channel. The outer surfaces of the two rubber rings cooperate with the surface of the axial floating plate 3 facing away from the gears to form the aforementioned pressure balance chamber.

[0075] Furthermore, at least two unloading groove groups are provided on the mating surface of the axial floating plate 3 facing the internal meshing gear set. The two unloading groove groups are respectively arranged corresponding to the first fluid chamber 15.2 and the second fluid chamber 16.2, and the unloading grooves in each unloading groove group cover the area where the teeth of the third gear 20 and the fourth gear 21 are located. The function of the unloading groove is to release part of the fluid pressure carried by the first gear or the second gear to the space between the teeth and the filler through its gradually decreasing cross-sectional area, thereby avoiding the situation where this part of the fluid is compressed and causes impact on the two gears.

[0076] Among them, each unloading groove group can include two or more parallel distributed unloading grooves (when the number of unloading grooves is two, the fourth unloading groove 18.4 is close to the third gear 20, and the fifth unloading groove 18.5 is close to the fourth gear 21, and the groove length of the fourth unloading groove 18.4 is shorter than that of the fifth unloading groove 18.5). The cross-section of the unloading groove can be specifically triangular, so as to take into account the reasonable unloading requirements when the third gear 20 and the fourth gear 21 are engaged, reduce the situation where oil is trapped in the gear pump when the gear pump is running, reduce vibration and noise, and improve the life of the pump.

[0077] In this embodiment, in order to adjust the radial gap and perform gap compensation to improve efficiency, the filling piece includes a crescent plate 6 , two radial compensation pieces and two floating plates 7 .

[0078] The crescent plate 6 is rotatably mounted to the pump housing via a retaining pin (the aforementioned third fluid chamber is formed in the area where the retaining pin is located). Floating grooves are provided on either the outer or inner surface of the crescent plate 6, circumferentially on either side (one on each side of the retaining pin). Floating plates 7 are positioned within these grooves. Radial compensators are positioned between the corresponding floating plates 7 and the grooves, configured to radially push the floating plates 7 away from the crescent plate 6. This embodiment utilizes radial compensators with optimized interplay and clearance to achieve high volumetric efficiency.

[0079] Among them, the radial compensation part includes an adjusting pin 10 and an adjusting spring 11. An adjusting slot with an opening facing the floating plate 7 is provided in the floating slot. The adjusting pin 10 and the adjusting spring 11 are arranged in the adjusting slot, and the adjusting spring 11 is configured to push the adjusting pin 10 to fit tightly against the floating plate 7.

[0080] The fixing pins may specifically be two guide pin shafts 12 , which are inserted into the crescent plate 6 from both sides in the axial direction and are connected to the oil inlet plate 8 and the oil outlet plate 1 respectively.

[0081] This embodiment specifically adopts a solution in which the floating groove opens toward the third gear 20. The outer surface of the crescent plate 6 cooperates with the tooth top of the fourth gear 21, the adjustment pin 10 cooperates with the outer surface of the floating plate 7, the adjustment spring 11 is assembled between the crescent plate 6 and the adjustment pin 10, and the inner surface of the floating plate 7 cooperates with the tooth top of the third gear 20. The adjustment spring 11 squeezes the adjustment pin 10 and pushes the floating plate 7 closer to the tooth top of the third gear 20 to achieve gap compensation; after compensation, the fitting clearance between the tooth top of the fourth gear 21 and the outer surface of the crescent plate 6 is in the range of 0-0.003mm, and the fitting clearance between the tooth top of the third gear 20 and the inner surface of the floating plate 7 is in the range of 0-0.003mm.

[0082] In this embodiment, the gear parameters of the third gear 20 and the fourth gear 21 include: The pressure angle range is 24° to 25°, the tooth addendum coefficient is 0.85 to 0.95, and the top clearance coefficient is 0.18 to 0.22. The preferred values ​​are a pressure angle α of 25°, a tooth addendum coefficient ha* of 0.9, and a top clearance coefficient c* of 0.2. While ensuring normal gear transmission, an overlap ratio of 1.4 to 1.55 is used to reduce oil trapping in the oil pump.

[0083] In this embodiment, a drive hole 17 for connecting to the external rotating shaft 9 is provided on the third gear 20, wherein, in order to improve the balance of the moving parts and enhance the driving stability, and improve noise and vibration, the drive hole 17 can be set to have a symmetrical regular hexagonal drive hole 17 or a spline hole.

[0084] In order to solve or improve problems such as oil trapping, low efficiency, abnormal wear, vibration and noise, and to improve the efficiency and life of the oil pump, this embodiment proposes solutions in terms of the driving structure of the driving gear (third gear 20), gear cavity coating, gear parameters and number of teeth, clearance between moving parts and clearance adjustment device, unloading groove structure, cooling or lubricating oil channel 19 on the axial floating plate 3, etc.

[0085] Example 3 This embodiment provides an active suspension electro-hydraulic pump assembly based on the above-mentioned embodiment 1 or embodiment 2. The active suspension electro-hydraulic pump assembly includes an electric motor and the internal meshing linear conjugate gear pump in the above-mentioned embodiment 1 or the internal meshing involute gear pump in the above-mentioned embodiment 2.

[0086] The motor's rotating shaft extends into the working space and is in transmission connection with the drive hole 17 of the first gear 5 of the first embodiment or the third gear 20 of the second embodiment. Specifically, to achieve cooling of the motor, the motor's rotating shaft can be configured as a hollow shaft and extend to the area where the pressure balance chamber is located, so that the hollow channel of the hollow shaft is connected to the pressure balance chamber and the rotor chamber where the motor rotor is located. The axial compensation unit located between the oil outlet plate 1 and the internal meshing gear set can be further configured to be symmetrical with the axial compensation unit on the other side. That is, the axial compensation unit located between the oil outlet plate 1 and the internal meshing gear set also includes two rubber rings and an axial floating plate 3 to form a third fluid channel and a fourth fluid channel. Two cooling channels are provided on the oil outlet plate 1, each connecting the third and fourth circulation channels to the rotor chamber. One-way valves can be further provided in the two cooling channels so that oil can only enter the pump housing from the rotor chamber. That is, the oil in the rotor cavity is in a medium-pressure state, while the third circulation channel and the fourth circulation channel connected to it through the cooling channel are in a low-pressure state and a high-pressure state respectively (depending on the direction of rotation of the first gear 5 or the third gear 20). The pressure difference between the medium pressure and the low pressure can cause the oil in the rotor cavity to flow back to the gear pump through the corresponding one-way valve, completing the oil cooling cycle.

[0087] Example 4 This embodiment provides an active suspension electro-hydraulic pump assembly based on the above-mentioned embodiment 1 and embodiment 2, which includes two electric motors and two internal meshing linear conjugate gear pumps in the above-mentioned embodiment 1 or the internal meshing involute gear pumps in embodiment 2.

[0088] Both motors are arranged in a common housing, and the rotating shafts of the two motors extend into the corresponding working spaces respectively and are transmission-connected to the first gear 5 of the first embodiment or the third gear 20 of the second embodiment, wherein the oil cooling cycle of the motor is consistent with that in the second embodiment.

[0089] This embodiment utilizes a single common housing, which contains two motor cavities with openings facing either end in the axial direction. The stator and rotor components of the two electric motors are housed within these cavities. This common housing significantly reduces the axial length of the active suspension electro-hydraulic pump assembly, further reducing the required installation space within the vehicle.

[0090] Example 5 This embodiment provides a chassis wheel axle based on the above-mentioned embodiments one to three, and the chassis wheel axle has two internally meshing linear conjugate gear pumps in the above-mentioned embodiment one or the internally meshing involute gear pumps in the above-mentioned embodiment two; or, the chassis wheel axle has two active suspension electro-hydraulic pump assemblies in the above-mentioned embodiment three; or, the chassis wheel axle has one active suspension electro-hydraulic pump assembly in the above-mentioned embodiment four.

[0091] The invention also comprises a first hydraulically adjustable shock absorber and a second hydraulically adjustable shock absorber, each of which is hydraulically connected to a hydraulic pump. The first hydraulically adjustable shock absorber and the second hydraulically adjustable shock absorber each have two dampers or pressure chambers, and the two electrohydraulic pumps are hydraulically connected to the pressure chambers of the two hydraulically adjustable shock absorbers. Thus, for example, "soft" or "hard" damping can be set by damping or throttling the electrohydraulic pump, such as more or less pressure shocks / pressure fluctuations from the pressure chambers. In this case, the respective motor-pump unit is thus driven hydraulically, so that the electric motor of the electrohydraulic pump can be operated as an electric generator and thus recover electrical energy (recovery). In addition, the zero position or rest position of the shock absorber can also be set actively or specifically, and can also be changed (continuously) during driving operation (active chassis).

[0092] The embodiments of the present invention have been described in detail above with reference to the accompanying drawings, but the present invention is not limited to the above embodiments. Even if various changes are made to the present invention, if these changes fall within the scope of the claims of the present invention and their equivalents, they still fall within the scope of protection of the present invention.

Claims

1. An internally meshing linear conjugate gear pump for an active suspension electro-hydraulic pump, comprising: a pump housing defining a working space therein, the pump housing being provided with a first fluid port and a second fluid port communicating with the working space; an internally meshing gear set arranged in the working space, comprising a first gear having external teeth and a second gear having internal teeth; The first gear is rotatably arranged along a first axis, and the first gear is configured to rotate under the drive of an external rotating shaft; The second gear is rotatably arranged along a second axis different from the first axis; The second gear is configured to mesh with the first gear in a meshing area and form a fluid space away from the meshing area between the first gear and the second gear; a filling member arranged in the fluid space and dividing the fluid space into a first fluid chamber and a second fluid chamber located on both sides thereof in a circumferential direction, wherein the first fluid chamber is connected to the first fluid port via a first fluid channel, and the second fluid chamber is connected to the second fluid port via a second fluid channel; It is characterized in that the first gear and the second gear have linear conjugate tooth shapes, and the number of teeth of the first gear and the number of teeth of the second gear are in a mutually prime tooth ratio.

2. The internal meshing linear conjugate gear pump for an active suspension electro-hydraulic pump according to claim 1, characterized in that: The gear parameters of the first gear and the second gear include: Tooth profile half angle β=25.5°~26.5°, pitch circle tooth thickness coefficient ks=4 / 15~2 / 5, tooth addendum height coefficient hax=0.58~0.59, tooth root height coefficient hfx=0.78~0.79, overlap degree ε=1.05~1.

15.

3. The internal meshing linear conjugate gear pump for an active suspension electro-hydraulic pump according to claim 1, characterized in that: It also includes two axial compensation units respectively arranged at the axial ends of the internally meshing gear set; both of the axial compensation units are configured to be axially attached to the internally meshing gear set under the action of the compensation force, and the axial compensation units close to the first fluid port and the second fluid port form the first fluid channel and the second fluid channel, wherein the axial compensation unit is attached to the first gear and / or the second gear.

4. The internally meshing linear conjugate gear pump for an active suspension electro-hydraulic pump according to claim 3, characterized in that: A third fluid cavity is also formed in the fluid space, located between the first fluid cavity and the second fluid cavity, and the fluid pressure in the third fluid cavity is located between the first fluid cavity and the second fluid cavity; wherein, the axial compensation unit is provided with an oil channel connected to the third fluid cavity, and the oil channel is configured to guide the oil in the third fluid cavity into the side of the axial compensation unit away from the internal meshing gear set, so as to balance the deflection force acting on the axial compensation unit by the fluid pressure difference between the first fluid cavity and the second fluid cavity.

5. The internal meshing linear conjugate gear pump for an active suspension electro-hydraulic pump according to claim 4, characterized in that: The axial compensation unit includes an axial floating plate and an axial elastic member, with both ends of the axial elastic member respectively attached to the pump housing and the axial floating plate; the axial elastic member near the first fluid port and the second fluid port cooperates with the axial floating plate to form the first fluid channel and the second fluid channel, which are not connected to each other, and a pressure balance chamber located on the side of the axial floating plate away from the internal gear set; The oil channel is opened on the axial floating plate, and the pressure balance chamber is connected to the oil channel.

6. The internal meshing linear conjugate gear pump for an active suspension electro-hydraulic pump according to claim 5, characterized in that: An extended blind groove is provided on the mating surface of the axial floating plate toward the internal meshing gear set, which extends from the first fluid cavity and the second fluid cavity along the filling piece respectively, and each of the extended blind grooves is provided with a unloading groove group connected thereto, wherein the unloading grooves in each of the unloading groove groups cover the areas where the teeth of the first gear and the second gear are located.

7. The internally meshing linear conjugate gear pump for an active suspension electro-hydraulic pump according to claim 1, wherein: The filling piece includes a crescent plate, two radial compensation pieces and two floating plates; The crescent plate is rotatably mounted on the pump housing via a fixing pin, and floating grooves are respectively provided on both sides of the outer ring surface or the inner ring surface of the crescent plate in the circumferential direction; the floating plates are respectively arranged in the floating grooves; the radial compensation members are respectively arranged between the corresponding floating plates and the floating grooves, and the radial compensation members are configured to push the floating plates away from the crescent plate in the radial direction.

8. The internally meshing linear conjugate gear pump for an active suspension electro-hydraulic pump according to claim 7, characterized in that: The radial compensation member includes an adjustment pin and an adjustment spring. An adjustment slot with an opening toward the floating plate is provided in the floating slot. The adjustment pin and the adjustment spring are arranged in the adjustment slot, and the adjustment spring is configured to push the adjustment pin to fit tightly against the floating plate.

9. An internal meshing involute gear pump for an active suspension electro-hydraulic pump, comprising: a pump housing defining a working space therein, the pump housing being provided with a first fluid port and a second fluid port communicating with the working space; an internally meshing gear set arranged in the working space, comprising a third gear having external teeth and a fourth gear having internal teeth; The third gear is rotatably arranged along the first axis, and the third gear is configured to rotate under the drive of the external rotating shaft; The fourth gear is rotatably arranged along a second axis different from the first axis; The fourth gear is configured to mesh with the third gear in a meshing area and form a fluid space away from the meshing area between the third gear and the fourth gear; a filling member arranged in the fluid space and dividing the fluid space into a first fluid chamber and a second fluid chamber located on both sides thereof in a circumferential direction, wherein the first fluid chamber is connected to the first fluid port via a first fluid channel, and the second fluid chamber is connected to the second fluid port via a second fluid channel; It is characterized in that the third gear and the fourth gear have involute tooth profiles, and the number of teeth of the third gear and the number of teeth of the fourth gear are in a mutually prime tooth ratio.

10. The internal meshing involute gear pump for an active suspension electro-hydraulic pump according to claim 9, characterized in that: The gear parameters of the third gear and the fourth gear include: The pressure angle range is 24°~25°, the tooth top height coefficient is 0.85~0.95, the top clearance coefficient is 0.18~0.22, and the overlap range is 1.4~1.

55.

11. The internal meshing involute gear pump for an active suspension electro-hydraulic pump according to claim 9, characterized in that: It also includes two axial compensation units respectively arranged at the axial ends of the internally meshing gear set; both of the axial compensation units are configured to be axially attached to the internally meshing gear set under the action of the compensation force, and the axial compensation units close to the first fluid port and the second fluid port form the first fluid channel and the second fluid channel, wherein the axial compensation unit is attached to the third gear and / or the fourth gear.

12. The internal meshing involute gear pump for an active suspension electro-hydraulic pump according to claim 11, wherein: A third fluid cavity is also formed in the fluid space, located between the first fluid cavity and the second fluid cavity, and the fluid pressure in the third fluid cavity is located between the first fluid cavity and the second fluid cavity; wherein, the axial compensation unit is provided with an oil channel connected to the third fluid cavity, and the oil channel is configured to guide the oil in the third fluid cavity into the side of the axial compensation unit away from the internal meshing gear set, so as to balance the deflection force acting on the axial compensation unit by the fluid pressure difference between the first fluid cavity and the second fluid cavity.

13. The internal meshing involute gear pump for an active suspension electro-hydraulic pump according to claim 12, wherein: The axial compensation unit includes an axial floating plate and an axial elastic member, with both ends of the axial elastic member respectively attached to the pump housing and the axial floating plate; the axial elastic member near the first fluid port and the second fluid port cooperates with the axial floating plate to form the first fluid channel and the second fluid channel, which are not connected to each other, and a pressure balance chamber located on the side of the axial floating plate away from the internal gear set; The oil channel is opened on the axial floating plate, and the pressure balance chamber is connected to the oil channel.

14. The internal meshing involute gear pump for an active suspension electro-hydraulic pump according to claim 13, wherein: At least two unloading groove groups are provided on the mating surface of the axial floating plate facing the internal meshing gear group, and the two unloading groove groups are respectively arranged corresponding to the first fluid cavity and the second fluid cavity, and the unloading grooves in each unloading groove group cover the areas where the teeth of the third gear and the fourth gear are located.

15. The internal meshing involute gear pump for an active suspension electro-hydraulic pump according to claim 9, characterized in that: The filling piece includes a crescent plate, two radial compensation pieces and two floating plates; The crescent plate is rotatably mounted on the pump housing via a fixing pin, and floating grooves are respectively provided on both sides of the outer ring surface or the inner ring surface of the crescent plate in the circumferential direction; the floating plates are respectively arranged in the floating grooves; the radial compensation members are respectively arranged between the corresponding floating plates and the floating grooves, and the radial compensation members are configured to push the floating plates away from the crescent plate in the radial direction.

16. The internal meshing involute gear pump for an active suspension electro-hydraulic pump according to claim 15, wherein: The radial compensation member includes an adjustment pin and an adjustment spring. An adjustment slot with an opening toward the floating plate is provided in the floating slot. The adjustment pin and the adjustment spring are arranged in the adjustment slot, and the adjustment spring is configured to push the adjustment pin to fit tightly against the floating plate.

17. An active suspension electro-hydraulic pump assembly, characterized in that: Including electric motor; Also includes the internal meshing linear conjugate gear pump according to any one of claims 1 to 8, or the internal meshing involute gear pump according to any one of claims 9 to 16; The rotating shaft of the motor extends into the working space and is transmission-connected with the first gear or the third gear.

18. An active suspension electro-hydraulic pump assembly, characterized in that: Includes two electric motors; Also includes two internal meshing linear conjugate gear pumps according to any one of claims 1 to 8, or two internal meshing involute gear pumps according to any one of claims 9 to 16; The two motors are both arranged in a common housing, and the rotating shafts of the two motors respectively extend into the corresponding working spaces and are transmission-connected to the first gear or the third gear.

19. A chassis axle, characterized in that: An internally meshing linear conjugate gear pump for two active suspension electro-hydraulic pumps according to any one of claims 1 to 8, or an internally meshing involute gear pump for two active suspension electro-hydraulic pumps according to any one of claims 9 to 16; or Having two active suspension electro-hydraulic pump assemblies as claimed in claim 17; or, An active suspension electro-hydraulic pump assembly as claimed in claim 18; A first hydraulically adjustable shock absorber and a second hydraulically adjustable shock absorber are respectively hydraulically connected to the internally meshing linear conjugate gear pump.

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