Internal gear pump, hydraulic system and vehicle

Abstract

An internal gear pump, a hydraulic system and a vehicle. The internal gear pump comprises: a housing, a ring gear, a gear and a partition block. The ring gear is rotationally mounted in the housing; the gear is eccentrically engaged with the ring gear, such that an accommodating space is formed between the ring gear and the gear; the partition block is mounted in the accommodating space and divides the accommodating space into a first chamber and a second chamber, a first oil groove is provided between the ring gear and the housing at a position corresponding to the first chamber, and is in communication with the first chamber; and a second oil groove is provided between the ring gear and the housing at a position corresponding to the second chamber, and is in communication with the second chamber.

Description

Internal gear pump, hydraulic system and vehicle

[0001] This application claims priority to Chinese Patent Application No. 202411048566.1, filed on July 31, 2024, the entire contents of which are incorporated herein by reference. TECHNICAL FIELD

[0002] The present disclosure relates to the technical field of internal gear pumps, and in particular to an internal gear pump, a hydraulic system and a vehicle. BACKGROUND

[0003] Internal gear pumps are widely used in various industries due to their wide speed range, high volumetric efficiency and low noise. An internal gear pump generally includes a pump body, a gear ring and a gear, the gear ring and the gear are arranged in eccentric engagement. A partition block is arranged between the gear and the gear ring to separate the non-engagement space left by the eccentric gear and gear ring into an oil suction area and an oil discharge area. SUMMARY

[0004] In one aspect, an internal gear pump is provided, which includes a housing, a gear ring, a gear and a partition block. The gear ring is rotatably mounted in the housing. The gear is eccentrically engaged with the gear ring to form an accommodation space between the gear ring and the gear. The partition block is mounted in the accommodation space and separates the accommodation space into a first chamber and a second chamber. A first oil groove is provided between the gear ring and the housing corresponding to the position of the first chamber, and the first oil groove is configured to accommodate pressure medium corresponding to the pressure of the first chamber. A second oil groove is provided between the gear ring and the housing corresponding to the position of the second chamber, and the second oil groove is configured to accommodate pressure medium corresponding to the pressure of the second chamber.

[0005] In some embodiments, the first oil groove is in communication with the first chamber, the second oil groove is in communication with the second chamber, the housing is provided with a first oil passage in communication between the first oil groove and the first chamber and a second oil passage in communication between the second oil groove and the second chamber.

[0006] In some embodiments, the housing has a first oil port in communication with the first chamber and a second oil port in communication with the second chamber, the first oil passage is in communication between the first oil groove and the first oil port, and the second oil passage is in communication between the second oil groove and the second oil port.

[0007] In some embodiments, the housing includes a body and a bushing mounted on the inner side of the body, the gear ring is rotatably mounted on the inner wall of the bushing, and the first oil groove and the second oil groove are respectively formed in the inner wall of the bushing.

[0008] In some embodiments, the inner wall of the bushing is coated with a wear-resistant layer.

[0009] In some embodiments, the bushing comprises an outer layer and an inner layer, the strength of the outer layer is greater than that of the inner layer, the wear resistance of the inner layer is greater than that of the outer layer, and the wear-resistant layer is arranged on the inner side of the inner layer.

[0010] In some embodiments, the depth H of the first oil groove and the second oil groove is respectively in the range of 0.5mm-0.8mm.

[0011] In some embodiments, the first chamber and the second chamber are symmetrically arranged on both sides of the partition block, and the first oil groove and the second oil groove are symmetrically arranged on both sides of the partition block.

[0012] In some embodiments, the first oil groove and the second oil groove are respectively an arc-shaped groove extending around the circumference of the gear ring, and the central angle of the arc corresponding to the first oil groove and the second oil groove is respectively in the range of 50°-120°.

[0013] In some embodiments, taking the position of the outer wall of the gear ring as the center point, the central angle of the arc between the position close to the center point of the first oil groove and the second oil groove and the center point is in the range of 18°-40°, and the central angle of the arc between the position away from the center point of the first oil groove and the second oil groove and the center point is in the range of 90°-138°.

[0014] In some embodiments, the partition block comprises a main partition block, a secondary partition block and an elastic member, the main partition block is arranged outside the gear. The secondary partition block is arranged between the main partition block and the gear ring. The elastic member is connected between the main partition block and the secondary partition block, and is configured to abut the main partition block to the gear and abut the secondary partition block to the gear ring. The main partition block and the secondary partition block are at least partially sealed and fitted.

[0015] In some embodiments, two ends of the main partition block are respectively formed with a boss protruding towards the gear ring, and the secondary partition block is positioned between the two bosses.

[0016] In some embodiments, the body comprises a pump shell and a pump cover mounted on the shaft end of the pump shell, the pump cover has a first oil port communicating with the first chamber and a second oil port communicating with the second chamber, and the bushing is mounted in the pump shell.

[0017] In some embodiments, the internal gear pump further comprises a first valve plate and two first special-shaped rings, the first valve plate abutting against a side of the gear ring facing the pump cover. The first valve plate is provided with a first through hole corresponding to the first chamber and a second through hole corresponding to the second chamber, and a side of the first valve plate facing the gear ring forms a first sealing groove which is covered in the side wall of the gear ring and communicates with the containing space. The two first special-shaped rings abut between the first valve plate and the pump cover, and the first oil port communicates with the first chamber through the first through hole and the corresponding first special-shaped ring. The second oil port communicates with the second chamber through the second through hole and the corresponding first special-shaped ring. The oil in the first special-shaped ring can generate a liquid pressure to press the first valve plate against the gear ring.

[0018] In some embodiments, the pump cover is provided with a first mounting groove, and the two first special-shaped rings are embedded in the first mounting groove.

[0019] In some embodiments, the internal gear pump further comprises a second valve plate and two second special-shaped rings, the second valve plate abutting against a side of the gear ring facing the pump shell. The second valve plate is provided with a third through hole corresponding to the first chamber and a fourth through hole corresponding to the second chamber. A side of the second valve plate facing the gear ring forms a second sealing groove which is covered in the side wall of the gear ring and communicates with the containing space. The two second special-shaped rings abut between the second valve plate and the pump shell, and the pump shell is provided with a closed position corresponding to the second special-shaped ring. The oil in the second special-shaped ring can generate a liquid pressure to press the second valve plate against the gear ring.

[0020] In some embodiments, the pump shell is provided with a second mounting groove, and the two second special-shaped rings are embedded in the second mounting groove.

[0021] In another aspect, a hydraulic system is provided, comprising the internal gear pump described above.

[0022] In yet another aspect, a vehicle is provided, comprising the hydraulic system described above.

[0023] With the technical scheme, when the internal gear pump rotates in a forward direction, one of the first chamber and the second chamber constitutes a high-pressure chamber, and the other constitutes a low-pressure chamber, one of the first oil groove and the second oil groove is filled with high-pressure medium corresponding to the pressure of the high-pressure chamber, and the other is filled with low-pressure medium corresponding to the pressure of the low-pressure chamber. The oil groove filled with high-pressure medium can be used to balance the oil pressure of the high-pressure chamber on the gear ring in the radial outward direction, so as to solve the problem that the gear ring is subjected to a large outward radial force, thereby reducing the mixed friction loss of the gear ring and the inner wall of the shell, reducing the mutual solubility of the gear ring and the shell, and improving the overall efficiency of the internal gear pump. The oil groove filled with low-pressure oil can play a lubricating role to form an effective oil film between the shell and the gear ring, reduce the friction torque loss, and improve the efficiency of the gear pump. Similarly, when the internal gear pump rotates in a reverse direction, the functions of the first chamber and the second chamber are interchanged, the original high-pressure chamber becomes a low-pressure chamber, the original low-pressure chamber becomes a high-pressure chamber, the original oil groove filled with high-pressure medium is filled with low-pressure medium, and the original oil groove filled with low-pressure medium is filled with high-pressure medium, thereby achieving the same pressure balance of the high-pressure chamber and the lubricating effect on the corresponding position of the low-pressure chamber. That is, whether the internal gear pump rotates forward or reversely, the pressure balance of the high-pressure chamber and the lubricating effect on the position of the low-pressure chamber can be achieved, the extrusion force between the gear ring and the shell is reduced, the lubricating oil film between the shell and the gear ring is prevented from being broken, and the friction and mutual solubility between the shell and the gear ring are reduced.

[0024] Other features and advantages of the present disclosure will be described in detail in the following detailed description section. BRIEF DESCRIPTION OF DRAWINGS

[0025] The accompanying drawings are included to provide a further understanding of the present disclosure and constitute a part of the specification, and are used together with the following detailed description to explain the present disclosure, but do not constitute a limitation on the present disclosure. In the drawings:

[0026] FIG. 1 is an internal structure diagram of an internal gear pump according to some embodiments;

[0027] FIG. 2 is an exploded view of an internal gear pump according to some embodiments;

[0028] FIG. 3 is a sectional view of an internal gear pump according to some embodiments;

[0029] FIG. 4 is a structure diagram of a first angle of a bushing according to some embodiments;

[0030] FIG. 5 is a structure diagram of a second angle of the bushing shown in FIG. 4;

[0031] FIG. 6 is a top view of a pump cover according to some embodiments;

[0032] FIG. 7 is a top view of a pump shell according to some embodiments;

[0033] FIG. 8 is a block diagram of a hydraulic system, according to some embodiments;

[0034] FIG. 9 is a block diagram of a vehicle, according to some embodiments.

[0035] Reference signs: 1000-vehicle; 60-hydraulic system; 10-internal gear pump; 1-housing; 100-body; 110-pump cover; 120-pump shell; 101-first oil port; 102-second oil port; 200-ring gear; 300-gear; 400-separation block; 410-main separation block; 411-boss; 420-secondary separation block; 430-elastic member; 500-accommodation space; 510-first chamber; 520-second chamber; 610-first oil groove; 620-second oil groove; 700-bushing; 701-first throttling hole; 702-second throttling hole; 703-center point; 810-first oil passage; 820-second oil passage; 910-first port plate; 911-first through hole; 912-second through hole; 913-first sealing groove; 920-first profiled ring; 930-second port plate; 931-third through hole; 932-fourth through hole; 933-second sealing groove; 940-second profiled ring. DETAILED DESCRIPTION

[0036] The specific embodiments of the present disclosure will be described below in detail with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are merely intended to illustrate and explain the present disclosure, and are not intended to limit the present disclosure.

[0037] In the present disclosure, the orientation words such as “inner, outer” used without the opposite description can be based on the structure of the relevant components themselves, or can be based on the use state of the relevant components, for example: the housing includes a body and a bushing installed on the “inner side” of the body, where the “inner side” refers to the internal accommodation space of the body. The first oil groove and the second oil groove are respectively formed on the “inner wall” of the bushing, where the “inner wall” refers to the wall surface of the bushing adjacent to the ring gear. The bushing includes an “outer layer” and an “inner layer”, and the wear-resistant layer is arranged on the “inner side” of the “inner layer”, where the “inner layer” refers to a layer of the bushing adjacent to the ring gear, the “outer layer” refers to a layer of the bushing adjacent to the housing, and the “inner side of the inner layer” refers to the side of the inner layer close to the ring gear.

[0038] In the present disclosure, the terms “first”, “second”, and the like are used to distinguish one element from another element, and do not have sequential and important meanings. When the following description refers to the drawings, the same numbers in different drawings represent the same or similar elements, unless otherwise indicated.

[0039] In the related art, since the gear ring and the pump body are both made of iron as the base material, although various methods are used for processing, the material composition difference is small and the mutual solubility is high, especially under high pressure working environment, the lubricating oil film will break, causing the gear ring and the pump body to be easily engaged, worn and mutually soluble. Especially in the oil discharge area, since the pressure in the oil discharge area is high, the eccentric force acting on the gear ring is large, which can easily cause the gear ring to be tightly pressed in the inner cavity of the pump body to rotate. When the pressure is high to a certain extent, the oil film between the inner wall of the gear ring and the pump body breaks, causing direct friction between the gear ring and the pump body, thereby causing the gear ring and the pump body to be pulled, engaged and damaged.

[0040] To this end, some embodiments of the present disclosure provide an internal gear pump 10.

[0041] Referring to FIGS. 1-3, some embodiments of the present disclosure provide an internal gear pump 10, which includes a housing 1, a gear ring 200, a gear 300, and a partition block 400. The gear ring 200 is rotatably installed in the housing 1. The gear 300 is eccentrically engaged with the gear ring 200 to form an accommodation space 500 between the gear ring 200 and the gear 300. The partition block 400 is installed in the accommodation space 500 and separates the accommodation space 500 into a first chamber 510 and a second chamber 520. A first oil groove 610 is provided between the gear ring 200 and the housing 1 at a position corresponding to the first chamber 510, and the first oil groove 610 is configured to accommodate pressure medium corresponding to the pressure of the first chamber 510. A second oil groove 620 is provided between the gear ring 200 and the housing 1 at a position corresponding to the second chamber 520, and the second oil groove 620 is configured to accommodate pressure medium corresponding to the pressure of the second chamber 520.

[0042] The present disclosure does not limit the "pressure medium", for example, the pressure medium can be pressure oil, compressed gas, etc. The present disclosure also does not limit how the first oil groove 610 and the second oil groove 620 inject the pressure medium corresponding to the pressure of the respective chambers. For example, in some embodiments of the present disclosure, the first oil groove 610 and the second oil groove 620 can respectively communicate with the respective first chamber 510 and second chamber 520, so as to obtain the pressure medium corresponding to the pressure from the corresponding chamber. In addition, in some embodiments, a component configured to provide the pressure medium corresponding to the pressure to the first oil groove 610 and the second oil groove 620 can also be additionally provided, for example, an oil pump and an oil pipe, the oil pump is configured to pump the pressure oil through the oil pipe to the corresponding oil groove, and the pumping of the oil pump can be adjusted according to the demand.

[0043] The present disclosure does not limit how the gear ring 200 is rotatably installed in the housing 1, for example, the rotation can be achieved by installing the gear ring 200 on the inside of the bushing 700 mentioned below.

[0044] In some embodiments of the present disclosure, the first oil groove 610 and the second oil groove 620 can be arranged on the inner wall of the housing 1, for example, the inner wall of the liner 700 to be mentioned below. In addition, in some embodiments, the first oil groove 610 and the second oil groove 620 can also be arranged directly on the outer wall of the ring gear 200. It should be noted that the "position corresponding to the first chamber 510" means that the positions of the first oil groove 610 and the first chamber 510 in the circumferential direction of the ring gear 200 are generally opposite, in other words, in the radial direction of the ring gear 200, they at least form a partially overlapping area. The "position corresponding to the second chamber 520" means that the positions of the second oil groove 620 and the second chamber 520 in the circumferential direction of the ring gear 200 are generally opposite, in other words, in the radial direction of the ring gear 200, they at least form a partially overlapping area.

[0045] In some embodiments of the present disclosure, the gear 300 can be connected with the input shaft to drive the gear 300 to rotate the ring gear 200 in the forward direction and the reverse direction through the input shaft. In addition, in some embodiments, the ring gear 200 can also be configured as a driving wheel, and the present disclosure does not limit this.

[0046] By using the above technical solution, when the internal gear pump 10 rotates in the forward direction, one of the first chamber 510 and the second chamber 520 constitutes a high-pressure chamber, and the other constitutes a low-pressure chamber, one of the first oil groove 610 and the second oil groove 620 is filled with high-pressure pressure medium corresponding to the pressure of the high-pressure chamber, and the other is filled with low-pressure pressure medium corresponding to the pressure of the low-pressure chamber. The oil groove filled with high-pressure pressure medium can be used to balance the oil pressure of the high-pressure chamber on the ring gear 200 in the radial direction outward, so as to solve the problem that the ring gear 200 is subjected to a larger radial force outward, thereby reducing the possibility of mixed friction loss between the ring gear 200 and the inner wall of the housing 1, and reducing the occurrence of the mutual solubility of the ring gear 200 and the housing 1, thereby improving the overall efficiency of the internal gear pump 10. The oil groove filled with low-pressure pressure medium can play a lubricating role, forming an effective oil film between the housing 1 and the ring gear 200, thereby reducing the friction torque loss, so as to improve the efficiency of the internal gear pump 10.

[0047] Similarly, when the internal gear pump 10 rotates reversely, the functions of the first chamber 510 and the second chamber 520 are interchanged, the original high-pressure chamber becomes a low-pressure chamber, the original low-pressure chamber becomes a high-pressure chamber, the original oil groove filled with high-pressure medium is filled with low-pressure medium, and the original oil groove filled with low-pressure medium is filled with high-pressure medium, thereby achieving the balancing of the oil pressure of the high-pressure chamber and the lubrication of the corresponding position of the low-pressure chamber. That is, whether the internal gear pump 10 rotates forward or reversely, the pressure balancing of the high-pressure chamber and the lubrication of the position of the low-pressure chamber can be achieved, so that the extrusion force between the gear ring 200 and the housing 1 is reduced, the lubricating oil film between the housing 1 and the gear ring 200 is prevented from being broken, and the friction and mutual solubility between the housing 1 and the gear ring 200 are reduced.

[0048] Referring to FIGS. 1-3, in some embodiments of the present disclosure, the first oil groove 610 can be communicated with the first chamber 510, and the second oil groove 620 can be communicated with the second chamber 520. The housing 1 can be provided with a first oil path 810 communicated between the first oil groove 610 and the first chamber 510, and a second oil path 820 communicated between the second oil groove 620 and the second chamber 520. In this way, when the internal gear pump 10 rotates forward, one of the first chamber 510 and the second chamber 520 is a high-pressure chamber, and the other is a low-pressure chamber. One of the first oil groove 610 and the second oil groove 620 communicated with the high-pressure chamber can be filled with high-pressure oil from the high-pressure chamber through the corresponding oil path to balance the oil pressure of the high-pressure chamber outwardly radially to the gear ring 200. The other of the first oil groove 610 and the second oil groove 620 communicated with the low-pressure chamber can be filled with low-pressure oil from the low-pressure chamber through the other oil path to be able to play a lubricating role. When the internal gear pump 10 reverses, the high-pressure chamber and the low-pressure chamber are switched, and the pressure of the pressure oil in the first oil groove 610 and the second oil groove 620 is switched to continue to play a role in balancing the pressure of the high-pressure chamber and lubricating the position of the low-pressure chamber. This design can achieve real-time synchronous switching of the pressure oil in the first oil groove 610 and the second oil groove 620 following the forward and reverse rotation of the internal gear pump 10, and does not require additional oil supply equipment, thereby simplifying the structure of the internal gear pump 10.

[0049] The present disclosure does not limit the forming manner of the first oil path 810 and the second oil path 820. In some embodiments, the body 100 of the housing 1 can be provided with passages serving as the first oil path 810 and the second oil path 820. In this case, referring to FIGS. 1, 6 and 7, the first oil path 810 and the second oil path 820 can respectively include multiple segments formed on the pump cover 110 of the housing 1 and the pump housing 120 of the housing 1, and adjacent two segments can be communicated to combine to form the corresponding first oil path 810 or second oil path 820. In addition, in some embodiments, the first oil path 810 and the second oil path 820 can also be formed by oil pipes.

[0050] Referring to FIGS. 1-3, in some embodiments of the present disclosure, the housing 1 can have a first oil port 101 communicating with the first chamber 510 and a second oil port 102 communicating with the second chamber 520, the first oil passage 810 can be communicated between the first oil groove 610 and the first oil port 101, and the second oil passage 820 can be communicated between the second oil groove 620 and the second oil port 102. The first oil port 101 and the second oil port 102 are used as the oil inlet and the oil outlet of the internal gear pump 10, respectively.

[0051] In addition, in some embodiments, the first oil groove 610 can be directly communicated with the first chamber 510 through the first oil passage 810. The second oil groove 620 can be directly communicated with the second chamber 520 through the second oil passage 820.

[0052] Alternatively, in some embodiments, the oil passage configured to communicate the corresponding oil groove and chamber can also be directly formed on the gear ring 200. In this case, a plurality of oil passages need to be formed on the gear ring 200 to ensure that there is always an oil passage to communicate the first oil groove 610 and the first chamber 510 and there is also always an oil passage to communicate the second oil groove 620 and the second chamber 520 when the gear ring 200 rotates.

[0053] The present disclosure does not limit the positions of the first oil groove 610 and the second oil groove 620. Referring to FIGS. 1-5, in some embodiments of the present disclosure, the housing 1 can include a body 100 and a bushing 700, such as a bearing bush, mounted on the inner side of the body 100. The gear ring 200 is rotatably mounted on the inner side of the bushing 700, and the first oil groove 610 and the second oil groove 620 can be formed on the inner wall of the bushing 700. In this way, one of the first oil groove 610 and the second oil groove 620 can be filled with high-pressure oil, and the other can be filled with low-pressure oil, thereby balancing the radial pressure of the high-pressure chamber on the gear ring 200 and lubricating the relative rotation between the bushing 700 and the gear ring 200. As mentioned above, in some embodiments, the first oil groove 610 and the second oil groove 620 can also be formed on the outer wall of the gear ring 200.

[0054] In this case, in order to enable the first oil groove 610 and the second oil groove 620 to communicate with the corresponding first chamber 510 or second chamber 520, referring to FIG. 3, in some embodiments of the present disclosure, the bushing 700 can be provided with a first throttling hole 701 communicating with the first oil groove 610 and a second throttling hole 702 communicating with the second oil groove 620, the first oil passage 810 is communicated between the first throttling hole 701 and the first chamber 510, and the second oil passage 820 is communicated between the second throttling hole 702 and the second chamber 520. In this way, the first oil groove 610 can be communicated with the first chamber 510 through the first throttling hole 701 and the first oil passage 810, and the second oil groove 620 can be communicated with the second chamber 520 through the second throttling hole 702 and the second oil passage 820.

[0055] Referring to FIGS. 1 and 3, in the case where the internal gear pump 10 includes the first oil port 101 and the second oil port 102 described above, the first oil passage 810 can be communicated between the first throttling hole 701 and the first oil port 101, and the second oil passage 820 can be communicated between the second throttling hole 702 and the second oil port 102. It should be noted that one of the first oil port 101 and the second oil port 102 can be used as an oil inlet port, and the other can be used as an oil outlet port, the first chamber 510 or the second chamber 520 connected to the oil inlet port is a low-pressure chamber, and the first chamber 510 or the second chamber 520 connected to the oil outlet port is a high-pressure chamber.

[0056] In some embodiments of the present disclosure, the inner wall of the bushing 700 can be coated with a wear-resistant layer. By providing a wear-resistant layer, the wear resistance of the bushing 700 can be improved, and the service life can be improved. For example, the wear-resistant layer can be a plastic layer. By providing a plastic layer, the mutual dissolution of similar metal materials in the bushing 700 and the gear ring 200 can be prevented, greatly improving the anti-adhesive wear, anti-scratch, and anti-seizure capabilities of the bushing 700. In addition, the plastic layer can increase the ability to adsorb lubricating oil on the surface compared to metal materials, thereby improving the lubrication performance between the bushing 700 and the gear ring 200.

[0057] The present disclosure does not limit the material of the plastic layer, which can be, for example, polyether ether ketone (PEEK). Alternatively, it can also be polytetrafluoroethylene (PTFE).

[0058] In some embodiments of the present disclosure, the bushing 700 can include an outer layer and an inner layer, the strength of the outer layer can be greater than the strength of the inner layer, the wear resistance of the inner layer can be greater than the wear resistance of the outer layer, and a wear-resistant layer can be arranged on the inner side of the inner layer. The present disclosure does not limit the materials of the inner layer and the outer layer. For example, the material of the outer layer can be cold-rolled steel, which has low cost and high strength, and can be used as the outer layer (base material) of the bushing 700. The material of the inner layer can be copper-tin alloy, which has good wear resistance and thus can improve the service life of the bushing 700. For example, after the wear-resistant layer on the inner side of the inner layer of the bushing 700 is worn, the inner layer made of copper-tin alloy can ensure the service life of the internal gear pump 10.

[0059] In some embodiments of the present disclosure, the bushing 700 can be a cylindrical structure formed by rolling a sheet material, and the first throttle hole 701, the second throttle hole 702, the first oil groove 610, and the second oil groove 620 can be formed in the sheet material before the sheet material is rolled. In this way, the manufacturing process of the bushing 700 can be simplified, and secondary machining is not required after the sheet material is rolled. Moreover, forming the throttle holes and the oil grooves in advance can ensure tolerances, improve machining accuracy, and reduce machining difficulty.

[0060] The present disclosure does not limit the depth of the first oil groove 610 and the second oil groove 620. For example, referring to FIG. 3, in some embodiments of the present disclosure, the depth H of the first oil groove 610 and the second oil groove 620 can be in the range of 0.5 mm-0.8 mm. For example, the depth of the first oil groove 610 and the second oil groove 620 can be 0.5 mm, 0.55 mm, 0.6 mm, 0.65 mm, 0.7 mm, 0.75 mm, or 0.8 mm, etc. It should be noted that the present disclosure does not require the depth of the first oil groove 610 and the second oil groove 620 to be the same. The upper limit of the depth of the first oil groove 610 and the second oil groove 620 is to ensure the strength of the bushing 700, so as to avoid the bushing 700 from being insufficient in strength due to the first oil groove 610 and the second oil groove 620 being too deep. The lower limit of the depth of the first oil groove 610 and the second oil groove 620 is to ensure that the hydraulic oil in the first oil groove 610 and the second oil groove 620 can provide sufficient radial pressure to balance the pressure in the high-pressure cavity and meet the basic oil lubrication requirement. In some embodiments, the depth of the first oil groove 610 and the second oil groove 620 can be 0.4 mm-0.7 mm. For example, the depth of the first oil groove 610 and the second oil groove 620 can be 0.4 mm, 0.45 mm, 0.5 mm, 0.55 mm, 0.6 mm, 0.65 mm, or 0.7 mm, etc. The depth of the first oil groove 610 and the second oil groove 620 can be adaptively designed according to actual conditions.

[0061] Referring to FIG. 3, in some embodiments of the present disclosure, the first chamber 510 and the second chamber 520 can be symmetrically arranged on both sides of the partition block 400, and the first oil groove 610 and the second oil groove 620 can be symmetrically arranged on both sides of the partition block 400. In this way, when the internal meshing gear pump 10 is rotated forward and reversely, the functions and related parameters (such as oil pressure, displacement, etc.) of the first chamber 510 and the second chamber 520, and the functions and related parameters (such as oil pressure, displacement, etc.) of the first oil groove 610 and the second oil groove 620 are completely reversed, and the flexibility is strong. In this way, the above-mentioned functions and related parameters can be randomly switched between forward rotation and reverse rotation, and only one side of the parameters needs to be designed during design, which reduces the design difficulty.

[0062] In some embodiments of the present disclosure, the first oil groove 610 and the second oil groove 620 can be arc-shaped grooves extending around the circumference of the gear ring 200, and the central angles corresponding to the arcs where the first oil groove 610 and the second oil groove 620 are located can range from 50° to 120°, respectively. For example, the central angles corresponding to the arcs where the first oil groove 610 and the second oil groove 620 are located can be 50°, 60°, 70°, 80°, 90°, 100°, 110°, or 120°. By limiting the upper and lower limits of the central angles corresponding to the arcs where the first oil groove 610 and the second oil groove 620 are located, they can be matched with the corresponding first chamber 510 or second chamber 520 to provide appropriate balance pressure.

[0063] For example, if the central angles corresponding to the arcs where the first oil groove 610 and the second oil groove 620 are located are too small, the range of balance pressure provided may be too small to meet the pressure balance of the high-pressure chamber. If the central angles corresponding to the arcs where the first oil groove 610 and the second oil groove 620 are located are too large, the range of balance pressure provided may be too large, so that part of the gear ring 200 will be subjected to pressure along the radial direction of the gear ring 200 inward, causing a problem of large extrusion force between the outer side of the gear ring 200 and the inner wall of the housing 1.

[0064] In addition, in some embodiments, the central angles corresponding to the arcs where the first oil groove 610 and the second oil groove 620 are located can range from 70° to 130°, for example, the central angles corresponding to the arcs where the first oil groove 610 and the second oil groove 620 are located can be 70°, 80°, 90°, 100°, 110°, 120°, or 130°, which is not limited in the present disclosure.

[0065] Referring to FIGS. 3-5, in some embodiments of the present disclosure, the center point 703 can be located at a position of the outer wall of the ring gear 200 (or the inner wall of the bushing 700) that is between the first oil groove 610 and the second oil groove 620 and away from the partition block 400. Along the outer wall of the ring gear 200, the range of the central angle of the arc between the position of the first oil groove 610 and the second oil groove 620 close to the center point 703 and the center point 703 (e.g., a1 shown in FIG. 5) can be 18°-40°, for example, the central angle of the arc between the position of the first oil groove 610 and the second oil groove 620 close to the center point 703 and the center point 703 can be 18°, 20°, 25°, 30°, 35°, or 40°. Along the outer wall of the ring gear 200, the range of the central angle of the arc between the position of the first oil groove 610 and the second oil groove 620 away from the center point 703 and the center point 703 (e.g., a2 shown in FIG. 5) can be 90°-138°, for example, the central angle of the arc between the position of the first oil groove 610 and the second oil groove 620 away from the center point 703 and the center point 703 can be 90°, 100°, 110°, 120°, 130°, or 138°.

[0066] It should be noted that by limiting the lower limit of the central angle of the arc between the position of the first oil groove 610 and the second oil groove 620 close to the center point 703 and the center point 703, it is to avoid that the first oil groove 610 and the second oil groove 620 are too close to each other, and thus the first oil groove 610 and the second oil groove 620 are connected through the gap between the ring gear 200 and the bushing 700, thereby damaging the internal pressure of the first oil groove 610 and the second oil groove 620.

[0067] By limiting the upper limit of the central angle of the arc between the position of the first oil groove 610 and the second oil groove 620 close to the center point 703 and the center point 703, it is to ensure that the first oil groove 610 and the second oil groove 620 can be located at the corresponding positions of the first chamber 510 and the second chamber 520, so as to provide a suitable balance pressure. If the central angle of the arc is too large, there can be a problem of "offset" between the oil groove and the chamber, i.e., a large area of misalignment (only a part of overlap), so as to cause the oil groove to be unable to provide a suitable balance pressure. It can be understood that by limiting the upper limit and the lower limit of the central angle of the arc between the position of the first oil groove 610 and the second oil groove 620 away from the center point 703 and the center point 703, it is also to limit the positional relationship between the oil groove and the chamber, so as to ensure that the chamber can provide a suitable balance pressure, i.e., to avoid that the radial pressures provided by the oil groove and the chamber are misaligned and thus unable to achieve pressure balance.

[0068] The present disclosure does not limit the structure of the partition block 400. For example, in some embodiments of the present disclosure, referring to FIG. 3, the partition block 400 can include a main partition block 410, at least one auxiliary partition block 420, and an elastic member 430. The main partition block 410 is arranged outside the gear 300. The auxiliary partition block 420 is arranged between the main partition block 410 and the gear ring 200. The elastic member 430 is connected between the main partition block 410 and the auxiliary partition block 420, and is configured to abut the main partition block 410 against the gear 300 and abut the auxiliary partition block 420 against the gear ring 200. The main partition block 410 and the auxiliary partition block 420 can be at least partially sealed and fitted.

[0069] In this way, by arranging the elastic member 430, when the main partition block 410 and the auxiliary partition block 420 relatively micro-move along the circumference of the gear ring 200, the supporting effect of the elastic member 430 can always make the main partition block 410 and the auxiliary partition block 420 abut against the gear ring 200 and the gear 300, respectively, to avoid gaps between the main partition block 410 and the gear 300 and between the auxiliary partition block 420 and the gear ring 200.

[0070] It can be understood that, when the elastic member 430 elastically supports, the part of the auxiliary partition block 420 close to the elastic member 430 abuts against the gear ring 200, and in addition, the part of the auxiliary partition block 420 close to the end of the main partition block 410 abuts against the main partition block 410 to maintain a sealed relationship with the main partition block 410. The main partition block 410 abuts against the gear 300. For example, the elastic member 430 can include a spring sheet fixed to the main partition block 410, and a rod arranged on the spring sheet and abutting against the auxiliary partition block 420, so that the contact sealing between the partition block 400 and the gear ring 200 and the gear 300 is always in a floating state.

[0071] It should be noted that, in some embodiments of the present disclosure, the at least one auxiliary partition block 420 can include one auxiliary partition block 420 or two auxiliary partition blocks 420, and of course, the at least one auxiliary partition block 420 can also include more auxiliary partition blocks 420.

[0072] In some embodiments of the present disclosure, the two ends of the main partition block 410 can be formed with bosses 411 protruding towards the gear ring 200, respectively, and the auxiliary partition block 420 can be positioned between the two bosses 411 to prevent the auxiliary partition block 420 from moving out of position with the main partition block 410.

[0073] Referring to FIG. 1 and FIG. 2, in some embodiments of the present disclosure, the body 100 can include a pump shell 120 and a pump cover 110 mounted at the shaft end of the pump shell 120, the pump cover 110 can have a first oil port 101 communicating with the first chamber 510 and a second oil port 102 communicating with the second chamber 520, and a bushing 700 is mounted in the pump shell 120. By forming the first oil port 101 and the second oil port 102 on the pump cover 110, it is convenient to supply and discharge liquid from the end of the internal gear pump 10, and the structure of the pump shell 120 can be simplified to ensure the use strength of the pump shell 120.

[0074] Referring to FIG. 2, in some embodiments of the present disclosure, the internal gear pump 10 can further include a first distribution disc 910 and two first special-shaped rings 920, the first distribution disc 910 abuts against the side of the gear ring 200 facing the pump cover 110. The first distribution disc 910 is provided with a first through hole 911 corresponding to the first chamber 510 and a second through hole 912 corresponding to the second chamber 520. The side of the first distribution disc 910 facing the gear ring 200 forms a first sealing groove 913, which covers the side wall of the gear ring 200 and communicates with the containing space 500. The two first special-shaped rings 920 abut between the first distribution disc 910 and the pump cover 110, the first oil port 101 can communicate with the first chamber 510 through the first through hole 911 and the corresponding first special-shaped ring 920, and the second oil port 102 can communicate with the second chamber 520 through the second through hole 912 and the corresponding first special-shaped ring 920. The oil in the first special-shaped ring 920 can generate a liquid pressure to press the first distribution disc 910 tightly against the gear ring 200. In this way, oil can enter the first chamber 510 through the first oil port 101, the corresponding first special-shaped ring 920 and the first through hole 911, and be discharged to the second chamber 520 through internal meshing, and the oil in the second chamber 520 can be discharged through the second through hole 912, the corresponding first special-shaped ring 920 and the second oil port 102.

[0075] The first sealing groove 913 communicates with the containing space 500, so that the first sealing groove 913 is filled with oil to achieve sealing. The pressure difference between the first special-shaped ring 920 and the first distribution disc 910 can be realized by oil, which can press the first distribution disc 910 tightly against the gear ring 200 to ensure sealing. Since the special-shaped ring and the distribution disc are conventional components of the internal gear pump 10, and the oil flow and the pressure difference to press the distribution disc tightly against the gear ring 200 are realized by the special-shaped ring and the distribution disc, which are well known to those skilled in the art, and will not be described in detail here. The improvement of the present disclosure is not here.

[0076] In some embodiments of the present disclosure, in order to seal the first special-shaped ring 920 to the pump cover 110, the pump cover 110 can be provided with a first mounting groove, and the two first special-shaped rings 920 are embedded in the first mounting groove.

[0077] Referring to FIG. 2, in some embodiments of the present disclosure, the internal gear pump 10 can further include a second valve plate 930 abutting a side of the gear ring 200 facing the pump housing 120, and two second profiled rings 940. The second valve plate 930 can be provided with a third through hole 931 corresponding to the first chamber 510, and a fourth through hole 932 corresponding to the second chamber 520. A side of the second valve plate 930 facing the gear ring 200 can form a second sealing groove 933, which can be covered on the side wall of the gear ring 200 and communicated with the containing space 500. The two second profiled rings 940 are abutted between the second valve plate 930 and the pump housing 120, and the positions of the pump housing 120 corresponding to the second profiled rings 940 are provided in a closed manner. The oil in the second profiled rings 940 can generate a liquid pressure to press the second valve plate 930 tightly to the gear ring 200.

[0078] The second sealing groove 933 is communicated with the containing space 500, so that the second sealing groove 933 is filled with oil to achieve a sealing effect. The pressure difference between the second profiled ring 940 and the second valve plate 930 can be achieved by oil, which can press the second valve plate 930 tightly to the gear ring 200 to ensure sealing. Since the profiled ring and the valve plate are conventional components of the internal gear pump 10, and the oil flow and the pressure difference to press the valve plate tightly to the gear ring 200 are achieved by the profiled ring and the valve plate, which are well known to those skilled in the art, and the improvement of the present disclosure is not here.

[0079] In some embodiments of the present disclosure, in order to seal the second profiled ring 940 to the pump housing 120, the pump housing 120 can be provided with a second mounting groove, and the two second profiled rings 940 are embedded in the second mounting groove.

[0080] Here, it needs to be emphasized again that in the internal gear pump 10, the valve plate and the profiled ring are provided on both sides of the gear ring 200 to achieve the flow of oil and the sealing of the gear ring 200 and the valve plate, which is a conventional means in the art, and its structure and principle are well known to those skilled in the art, and the present disclosure does not make too much introduction on this point, and the improvement of the present disclosure is not here.

[0081] As shown in FIG. 8, some embodiments of the present disclosure further provide a hydraulic system 60, which includes the above-mentioned internal gear pump 10. Since the hydraulic system 60 has all the beneficial effects of the above-mentioned internal gear pump 10, no further description is given here.

[0082] As shown in FIG. 9, some embodiments of the present disclosure further provide a vehicle 1000, which includes the above-mentioned hydraulic system 60. Since the vehicle 1000 has all the beneficial effects of the above-mentioned hydraulic system 60, no further description is given here.

[0083] The preferred embodiments of the present disclosure are described in detail above with reference to the drawings, but the present disclosure is not limited to the specific details in the above-described embodiments. Various simple modifications can be made to the technical solutions of the present disclosure within the technical concept of the present disclosure, and these simple modifications all belong to the protection scope of the present disclosure.

[0084] In addition, it should be noted that each specific technical feature described in the above specific embodiments can be combined in any appropriate manner without contradiction. In order to avoid unnecessary repetition, various possible combinations are not described again in the present disclosure.

[0085] In addition, various different embodiments of the present disclosure can also be combined in any appropriate manner, as long as they do not deviate from the idea of the present disclosure, and they should also be considered as disclosed in the present disclosure.

Claims

1. An internal gear pump (10) comprising: a housing (1); a ring gear (200) rotatably mounted in the housing (1); a gear (300) eccentrically engaged with the ring gear (200) to form an accommodation space (500) between the ring gear (200) and the gear (300); and a partition block (400) mounted in the accommodation space (500) and separating the accommodation space (500) into a first chamber (510) and a second chamber (520); wherein a first oil groove (610) corresponding to the first chamber (510) is provided between the ring gear (200) and the housing (1), and the first oil groove (610) is configured to accommodate a pressure medium corresponding to the pressure of the first chamber (510); and a second oil groove (620) corresponding to the second chamber (520) is provided between the ring gear (200) and the housing (1), and the second oil groove (620) is configured to accommodate a pressure medium corresponding to the pressure of the second chamber (520).

2. The internal gear pump (10) of claim 1, wherein, The first oil groove (610) is in communication with the first chamber (510), and the second oil groove (620) is in communication with the second chamber (520), and the housing (1) is provided with a first oil passage (810) in communication between the first oil groove (610) and the first chamber (510) and a second oil passage (820) in communication between the second oil groove (620) and the second chamber (520).

3. The internal gear pump (10) of claim 2, wherein, The housing (1) has a first oil port (101) in communication with the first chamber (510) and a second oil port (102) in communication with the second chamber (520), the first oil passage (810) is in communication between the first oil groove (610) and the first oil port (101), and the second oil passage (820) is in communication between the second oil groove (620) and the second oil port (102).

4. The internal gear pump (10) according to any one of claims 1-3, wherein, The housing (1) comprises a body (100) and a bushing (700) mounted on the inner side of the body (100), and the ring gear (200) is rotatably mounted on the inner wall of the bushing (700), wherein the first oil groove (610) and the second oil groove (620) are respectively formed in the inner wall of the bushing (700).

5. The internal gear pump (10) of claim 4, wherein, The inner wall of the bushing (700) is coated with a wear-resistant layer.

6. The internal gear pump (10) of claim 5, wherein, The bushing (700) comprises an outer layer and an inner layer, the strength of the outer layer is greater than that of the inner layer, the wear resistance of the inner layer is greater than that of the outer layer, and the wear-resistant layer is arranged on the inner side of the inner layer.

7. The internal gear pump (10) according to any one of claims 1-6, wherein, The depth H of the first oil groove (610) and the second oil groove (620) is respectively within the range of 0.5mm-0.8mm.

8. The internal gear pump (10) according to any one of claims 1-7, wherein, The first chamber (510) and the second chamber (520) are symmetrically arranged on both sides of the partition block (400), and the first oil groove (610) and the second oil groove (620) are symmetrically arranged on both sides of the partition block (400).

9. The internal gear pump (10) of claim 8, wherein, The first oil groove (610) and the second oil groove (620) are arc-shaped grooves extending around the circumference of the ring gear (200), and the central angles of the arcs corresponding to the first oil groove (610) and the second oil groove (620) are respectively in the range of 50°-120°.

10. The internal gear pump (10) according to claim 8 or 9, wherein, With the center point (703) being the position of the outer wall of the ring gear (200) and being located between the first oil groove (610) and the second oil groove (620) and away from the partition block (400), the central angles of the arcs between the positions close to the center point (703) of the first oil groove (610) and the second oil groove (620) and the center point (703) are in the range of 18°-40°, and the central angles of the arcs between the positions away from the center point (703) of the first oil groove (610) and the second oil groove (620) and the center point (703) are in the range of 90°-138°.

11. The internal gear pump (10) according to any one of claims 1-10, wherein, The partition block comprises: a main partition block (410) arranged outside the gear (300); a sub-partition block (420) arranged between the main partition block (410) and the ring gear (200); and a resilient member (430) connected between the main partition block (410) and the sub-partition block (420) and configured to abut the main partition block (410) against the gear (300) and abut the sub-partition block (420) against the ring gear (200); wherein the main partition block (410) and the sub-partition block (420) are at least partially sealed and fitted.

12. The internal gear pump (10) of claim 11, wherein, The two ends of the main partition block (410) are respectively formed with bosses protruding towards the ring gear (200), and the sub-partition block (420) is positioned between the two bosses.

13. The internal gear pump (10) according to any one of claims 4-12, wherein, The body (100) of the housing (1) comprises a pump shell (120) and a pump cover (110) mounted at the shaft end of the pump shell (120), the pump cover (110) has a first oil port (101) communicating with the first chamber (510) and a second oil port (102) communicating with the second chamber (520), and the bushing (700) of the housing (1) is mounted in the pump shell (120).

14. The internal gear pump (10) according to claim 13, further comprising: a first port plate (910) abutting against the side of the ring gear (200) facing the pump cover (110), the first port plate (910) being provided with a first through hole (911) corresponding to the first chamber (510) and a second through hole (912) corresponding to the second chamber (520); the side of the first port plate (910) facing the ring gear (200) is formed with a first sealing groove (913) covering the side wall of the ring gear (200) and communicating with the containing space (500); and Two first special-shaped rings (920) are abutted between the first porting disc (910) and the pump cover (110), the first oil port (101) is communicated with the first chamber (510) through the first through hole (911) and the corresponding first special-shaped ring (920); the second oil port (102) is communicated with the second chamber (520) through the second through hole (912) and the corresponding first special-shaped ring (920); Wherein, the oil liquid in the two first special-shaped rings (920) can generate a liquid pressure to press the first porting disc (910) to the gear ring (200).

15. The internal gear pump (10) of claim 14, wherein, The pump cover (110) is provided with a first mounting groove, and the two first special-shaped rings (920) are embedded in the first mounting groove.

16. The internal gear pump (10) according to claim 14 or 15, further comprising: A second porting disc (930) is abutted to one side of the gear ring (200) facing the pump housing (120), the second porting disc (930) is provided with a third through hole (931) corresponding to the first chamber (510), and a fourth through hole (932) corresponding to the second chamber (520); one side of the second porting disc (930) facing the gear ring (200) forms a second sealing groove (933), the second sealing groove (933) is covered on the side wall of the gear ring (200) and communicated with the containing space (500); and Two second special-shaped rings (940) are abutted between the second porting disc (930) and the pump housing (120), the positions of the pump housing (120) corresponding to the two second special-shaped rings (940) are provided in a closed manner; Wherein, the oil liquid in the two second special-shaped rings (940) can generate a liquid pressure to press the second porting disc (930) to the gear ring (200).

17. The internal gear pump (10) of claim 16, wherein, The pump housing (120) is provided with a second mounting groove, and the two second special-shaped rings (940) are embedded in the second mounting groove.

18. A hydraulic system (60) comprising the internal gear pump (10) according to any one of claims 1-17.

19. A vehicle (1000) comprising the hydraulic system (60) according to claim 18.

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