Internal gear pump and integrated motor pump

Abstract

The utility model provides an internal gear pump and an integrated motor pump, the internal gear pump comprises a pump shell, a driving gear, a driven gear ring, a moon-shaped partition plate and a positioning component, the pump shell comprises a shell and a cover plate, the shell and the cover plate define a volume cavity, the driving gear and the driven gear ring are rotatably arranged in the volume cavity, and the moon-shaped partition plate is arranged in the volume cavity. An offset gap is formed between the driving gear and the driven gear ring, the moon-shaped partition plate is arranged in the offset gap and comprises a main plate and an auxiliary plate, the positioning assembly is provided with a positioning pin, in the rotating process of the driving gear, oil pressure in the pump shell enables the main plate to move in the radial direction of the driving gear relative to the auxiliary plate, and one end of the positioning pin is connected to the cover plate. The other end of the positioning pin is used for abutting against the main board so as to limit the maximum moving distance of the main board back to the auxiliary board. According to the utility model, tooth crest gaps can be reduced, liquid leakage is reduced, and the volume efficiency and performance of the pump are obviously improved.

Description

Technical Field

[0001] This utility model relates to the field of gear pump technology, specifically to an internal meshing gear pump and an integrated motor pump. Background Technology

[0002] During the operation of an internal gear pump, a precise fit clearance (tooth tip clearance) must be maintained between the gears and the crescent plate to ensure efficient pump operation. However, under different operating conditions, especially due to installation process, operator skill, and long-term wear, the tooth tip clearance can dynamically change.

[0003] In related technologies, internal gear pumps mostly employ a design where the main meniscus is fixed, while the secondary meniscus can float freely in the radial direction of the driving gear to achieve radial compensation for the tooth tip clearance. However, in practical applications, the main meniscus has no floating space, and the secondary meniscus has very little floating space. This results in insufficient compensation to effectively reduce the clearance when there are significant changes in the tooth tip clearance, making it difficult to meet the requirements for real-time compensation and affecting the pump's performance and reliability. Utility Model Content

[0004] This utility model is based on the inventor's discovery and understanding of the following facts and problems:

[0005] During the operation of an internal gear pump, if the tooth tip clearance is too large, the liquid in the high-pressure chamber can easily leak into the low-pressure chamber through the increased clearance during oil compression, resulting in a significant reduction in the pump's volumetric efficiency and output flow, failing to meet the system's operational requirements. If the tooth tip clearance is too small, it may cause interference between the gear and the crescent plate, leading to increased gear rotation resistance, accelerated wear, and even potential equipment failure.

[0006] However, in practical applications, the compensation method of the main and auxiliary meniscus plates working together has significant limitations. The main meniscus plate has no floating space, and the floating space of the auxiliary meniscus plate is generally small, which greatly limits its ability to compensate for changes in tooth tip clearance. When the tooth tip clearance changes significantly, such as due to long-term wear leading to a significant increase in clearance, or due to drastic changes in the working environment temperature causing large fluctuations in clearance, the lack of floating space of the main meniscus plate and the inability of the auxiliary meniscus plate to provide sufficient compensation to effectively reduce the clearance. Its limited floating range means that it can only adjust within a small range, making it difficult to cope with large changes in tooth tip clearance. This results in a situation where, during actual operation, when the tooth tip clearance change exceeds the compensation capacity of the auxiliary meniscus plate, the fluid leakage is still significant, failing to effectively prevent fluid from the high-pressure chamber from leaking into the low-pressure chamber, thus making it difficult to meet the requirements of real-time compensation.

[0007] Therefore, this utility model provides an internal gear pump and an integrated motor pump, which can improve the compensation capability for changes in tooth tip clearance and significantly improve the volumetric efficiency of the internal gear pump.

[0008] The internal gear pump provided by this utility model includes a pump housing, a driving gear, a driven gear ring, a crescent-shaped partition, and a positioning assembly. The pump housing includes a shell and a cover plate, which define a volumetric cavity. The driving gear and the driven gear ring are rotatably disposed within the volumetric cavity, and an offset gap is formed between the driving gear and the driven gear ring. The crescent-shaped partition is disposed within the offset gap and includes a main plate and a secondary plate. The positioning assembly has a positioning pin. During the rotation of the driving gear, the oil pressure in the pump housing causes the main plate to move relative to the secondary plate in the radial direction of the driving gear. One end of the positioning pin is connected to the cover plate, and the other end of the positioning pin is used to abut against the main plate to limit the maximum distance that the main plate moves away from the secondary plate.

[0009] In summary, the internal gear pump provided by this utility model, through the mobility of the main plate in the crescent-shaped partition in the radial direction of the driving gear, allows it to adjust its position in real time according to different working conditions, reducing the tooth tip clearance. This effectively solves the problems of small floating space and insufficient compensation capacity of the secondary crescent plate in the prior art, while also reducing liquid leakage and significantly improving the pump's volumetric efficiency and performance.

[0010] In some embodiments, the internal gear pump further includes a sealing assembly, which includes a sealing rod and an elastic element. The main plate is provided with a waist-shaped positioning hole and a mounting groove. The length direction of the waist-shaped positioning hole is consistent with the radial direction of the drive gear. The sealing rod is disposed in the mounting groove. The elastic element abuts between the sealing rod and the main plate so that the sealing rod abuts against the sub-plate. The waist-shaped positioning hole is disposed on the main plate and located between the end of the main plate and the mounting groove.

[0011] In some embodiments, the main board includes a crescent-shaped plate body, a first protrusion and a second protrusion, the first protrusion and the second protrusion being respectively disposed at both ends of the crescent-shaped plate body, the first protrusion, the crescent-shaped plate body, the second protrusion and the driven gear ring defining a limiting cavity, the sub-plate being crescent-shaped, and the sub-plate being movably disposed within the limiting cavity.

[0012] In some embodiments, the positioning component further includes a stop pin connected to the cover plate. The main plate includes a crescent-shaped plate body and a third protrusion. The third protrusion is disposed at one end of the crescent-shaped plate body, and the stop pin is disposed at the other end of the crescent-shaped plate body. The stop pin, the crescent-shaped plate body, the third protrusion, and the driven gear ring define a limiting cavity. The secondary plate is crescent-shaped and is movably disposed within the limiting cavity.

[0013] In some embodiments, the stop pin has a first inclined surface, the sub-plate has a second inclined surface, and the first inclined surface and the second inclined surface abut against each other to increase the gap between the main plate and the sub-plate.

[0014] In some embodiments, the stop pin further includes a third inclined surface, and the main board is provided with a fourth inclined surface that abuts against the third inclined surface. The third inclined surface intersects with the first inclined surface, and the angle of intersection between the third inclined surface and the first inclined surface is 10° to 180°.

[0015] In some embodiments, the stop pin has at least a parallelogram segment, one of two adjacent planes of the parallelogram segment abutting the main board, and the other of two adjacent planes of the parallelogram segment abutting the sub-board.

[0016] In some embodiments, the positioning component further includes a stop pin connected to the cover plate. The main plate includes a crescent-shaped plate body and a third protrusion. The third protrusion is located at one end of the crescent-shaped plate body, and the stop pin is located at the other end of the crescent-shaped plate body. The stop pin, the crescent-shaped plate body, the third protrusion, and the driven gear ring define a limiting cavity. The secondary plate is crescent-shaped and is movably disposed within the limiting cavity. The positioning pin and the stop pin are spaced apart in the circumferential direction of the driving gear. The positioning pin is located on the side of the main plate away from the stop pin and abuts against the third protrusion.

[0017] In some embodiments, there are two motherboards and two sub-boards, with the two motherboards symmetrically arranged within the offset gap, and the motherboards and sub-boards are arranged in a one-to-one correspondence.

[0018] Furthermore, the integrated motor pump provided by this utility model includes a motor module and an internal gear pump provided in any of the above embodiments. The motor module includes a drive shaft, and the driving gear is sleeved on the drive shaft. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the internal gear pump provided in the first embodiment of this utility model.

[0020] Figure 2This is an assembly diagram of the crescent-shaped partition and positioning assembly in the internal gear pump provided in the first embodiment of this utility model.

[0021] Figure 3 This is an assembly diagram of the crescent-shaped partition and positioning assembly in the internal gear pump provided in the second embodiment of this utility model.

[0022] Figure 4 This is an assembly diagram of the crescent-shaped partition and positioning assembly in the internal gear pump provided in the third embodiment of this utility model.

[0023] Figure 5 This is an assembly diagram of the crescent-shaped partition and positioning assembly in the internal gear pump provided in the fourth embodiment of this utility model.

[0024] Figure label:

[0025] 10. Pump casing; 11. Volumetric cavity; 111. Oil suction chamber; 112. Oil discharge chamber; 13. Offset clearance;

[0026] 21. Driving gear; 23. Driven gear ring;

[0027] 30. Crescent-shaped partition; 31. Waist-shaped positioning hole; 33. Main board; 331. Mounting groove; 332. Crescent-shaped plate body; 333. First protrusion; 334. Second protrusion; 335. Limiting cavity; 336. Third protrusion; 337. Fourth inclined surface; 35. Sub-plate; 351. Second inclined surface;

[0028] 40. Positioning component; 41. Positioning pin; 421. First inclined surface; 422. Third inclined surface; 42. Stop pin;

[0029] 50. Sealing assembly; 51. Sealing rod; 52. Elastic element. Detailed Implementation

[0030] The embodiments of this utility model are described in detail below, with examples of the embodiments shown in the accompanying drawings. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this utility model, and should not be construed as limiting this utility model.

[0031] like Figure 1 and Figure 2 As shown, one embodiment of this utility model provides an internal gear pump. Figure 1 This is a schematic diagram of the internal gear pump provided in the first embodiment of the present invention. Figure 2 This is a schematic diagram of the assembly of the crescent-shaped partition 30 and the positioning component 40 in the internal gear pump provided in the first embodiment of the present invention.

[0032] The internal gear pump provided by this utility model includes a pump housing 10, a driving gear 21, a driven gear ring 23, a crescent-shaped partition 30, and a positioning assembly 40. The pump housing 10 includes a shell and a cover plate, which define a volumetric cavity 11. The driving gear 21 and the driven gear ring 23 are rotatably disposed within the volumetric cavity 11, and an offset gap 13 is formed between the driving gear 21 and the driven gear ring 23. The crescent-shaped partition 30 is disposed within the offset gap 13 to divide the volumetric cavity 11 into two working chambers. One of the two working chambers can be an oil suction chamber 111, and the other can be an oil discharge chamber 112.

[0033] The crescent-shaped partition 30 includes a main plate 33 and a secondary plate 35. The positioning assembly 40 has a positioning pin 41. During the rotation of the drive gear 21, the oil pressure in the pump housing 10 makes the main plate 33 movable relative to the secondary plate 35 in the radial direction of the drive gear 21. One end of the positioning pin 41 is connected to the cover plate, and the other end of the positioning pin 41 is used to abut against the main plate 33 to limit the maximum distance that the main plate 33 moves away from the secondary plate 35.

[0034] Specifically, during pump operation, the main plate 33 in the crescent-shaped baffle 30 can flexibly adjust its position according to changes in the oil pressure inside the pump, thereby effectively controlling the oil flow path and flow rate, and improving pump efficiency. In other words, when the tooth tip clearance changes due to various factors, the crescent-shaped baffle 30 can automatically adjust its position in the radial direction of the drive gear 21 according to the change in clearance, thereby achieving radial compensation for the tooth tip clearance, reducing the tooth tip clearance, decreasing liquid leakage, and significantly improving the pump's volumetric efficiency and performance.

[0035] The positioning component ensures the stable operation of the crescent-shaped partition. During the rotation of the drive gear 21, the oil pressure inside the pump housing constantly changes. This pressure change attempts to push the main plate 33 to move away from or towards the secondary plate 35. The presence of the positioning pin 41 limits the maximum distance the main plate 33 can move away from the secondary plate 35, preventing damage to the main plate 33 due to excessive movement or affecting the normal operation of the pump, thus ensuring stable and reliable pump operation under various working conditions.

[0036] In summary, the internal gear pump provided by this invention, through the mobility of the main plate 33 of the crescent-shaped partition 30 in the radial direction of the driving gear 21, allows it to adjust its position in real time according to different working conditions, reducing the tooth tip clearance. This effectively solves the problems of small floating space and insufficient compensation capacity of the secondary crescent plate in the prior art, while also reducing liquid leakage and significantly improving the pump's volumetric efficiency and performance. Furthermore, the positioning component 40 ensures the stability and reliability of the movement of the crescent-shaped partition 30, guaranteeing the long-term stable operation of the pump.

[0037] In some embodiments, the internal gear pump further includes a sealing assembly 50, which includes a sealing rod 51 and an elastic member 52. The main plate 33 is provided with a waist-shaped positioning hole 31 and a mounting groove 331. The length direction of the waist-shaped positioning hole 31 is consistent with the radial direction of the drive gear 21. The sealing rod 51 is disposed in the mounting groove 331, and the elastic member 52 abuts between the sealing rod 51 and the main plate 33 so that the sealing rod 51 abuts against the sub-plate 35. The waist-shaped positioning hole 31 is disposed on the main plate 33 and is located between the end of the main plate 33 and the mounting groove 331.

[0038] Specifically, the crescent-shaped partition 30 is provided with a waist-shaped positioning hole 31. The length direction of the waist-shaped positioning hole 31 is completely consistent with the radial direction of the drive gear 21, so that the crescent-shaped partition 30 can move along the radial direction of the drive gear 21 within the length range of the waist-shaped positioning hole 31, thereby guiding the main board to move and improving the movement accuracy of the main board.

[0039] As can be imagined, the size of the waist-shaped positioning hole 31 can be selected according to the structural strength and working pressure of the crescent-shaped partition 30, so as to ensure that the crescent-shaped partition 30 has sufficient moving space while ensuring its stability and reliability during the movement process.

[0040] Furthermore, when the pump operates and the internal pressure changes or the crescent-shaped baffle 30 moves, the elastic element 52 can automatically adjust its elastic force according to the pressure change, ensuring that the sealing rod 51 always maintains good contact with the auxiliary plate 35, achieving a reliable seal. This elastic sealing method can not only adapt to pressure changes of the pump under different operating conditions, but also compensate for gaps caused by the movement of the crescent-shaped baffle 30 or the slight deformation of the auxiliary plate 35, effectively preventing liquid leakage.

[0041] Furthermore, the waist-shaped positioning hole 31 is provided on the main board 33 and located between the end of the main board 33 and the mounting groove 331, so that the waist-shaped positioning hole 31 will not interfere with the installation of the sealing rod 51 and the function of the elastic element 52, and can also ensure that the crescent-shaped partition 30 will not be restricted by the sealing assembly 50 when it moves in the radial direction along the drive gear 21.

[0042] Meanwhile, the position of the waist-shaped positioning hole 31 can also cooperate with the sealing assembly 50. That is, when the tooth tip clearance changes, the crescent-shaped partition 30 can move freely within the range of the waist-shaped positioning hole 31. Through the tight contact between the sealing rod 51 and the sub-plate 35, radial compensation of the tooth tip clearance is achieved, while ensuring that the sealing performance is not affected.

[0043] Optionally, the elastic element 52 can be a spring sheet.

[0044] refer to Figure 2In this embodiment, the main board 33 includes a crescent-shaped plate body 332, a first protrusion 333, and a second protrusion 334, which are respectively disposed at both ends of the crescent-shaped plate body 332. The first protrusion 333, the crescent-shaped plate body 332, the second protrusion 334, and the driven gear ring 23 define a limiting cavity 335. The sub-plate 35 is crescent-shaped and is movably disposed within the limiting cavity 335.

[0045] Specifically, the first protrusion 333 and the second protrusion 334 can both extend from the crescent plate body 332 toward the driven gear ring 23 in the radial direction of the driving gear 21. That is, the crescent plate body 332, the first protrusion 333 and the second protrusion 334 can form a U-shaped structure, thereby defining and forming a limiting cavity 335. In turn, the limiting cavity 335 restricts the movement range of the secondary plate 35, ensuring that the secondary plate 35 will not detach from the main plate 33 during the operation of the pump, thus ensuring the integrity and stability of the overall structure of the crescent-shaped partition 30.

[0046] Furthermore, the first protrusion 333, the crescent-shaped plate 332, and the second protrusion 334 can be integrated into one unit, which can enhance the overall strength and rigidity of the main board 33.

[0047] Furthermore, two main plates 33 and two auxiliary plates 35 are provided. The two main plates 33 are symmetrically arranged within the bias gap 13, with each main plate 33 and auxiliary plate 35 corresponding to the other. One of the two main plates 33 is located on the side of the bias gap 13 closer to the oil suction chamber 111, and the other of the two main plates 33 is located on the side of the bias gap 13 closer to the oil discharge chamber 112. Similarly, one of the two auxiliary plates 35 is located on the side of the bias gap 13 closer to the oil suction chamber 111, and the other of the two main plates 33 is located on the side of the bias gap 13 closer to the oil discharge chamber 112, allowing the crescent-shaped baffle 30 to form a highly efficient and stable working system within the pump. They not only effectively separate the volumetric chamber 11, achieving separation of the oil suction and discharge processes, but also improve the pump's volumetric efficiency and reliability through radial compensation and sealing functions. During actual pump operation, the coordinated work of the main plates 33 and auxiliary plates 35 ensures smoother liquid flow within the pump, reduces energy loss, and improves the overall performance of the pump.

[0048] refer to Figure 3This is a schematic diagram of the assembly of the crescent-shaped partition and positioning component in the internal gear pump provided in the second embodiment of this utility model. The differences between the internal gear pump provided in the second embodiment and the internal gear pump provided in the first embodiment are as follows: The positioning component 40 further includes a stop pin 42, which is connected to the cover plate. The main plate 33 includes a crescent-shaped plate body 332 and a third protrusion 336. The third protrusion 336 is located at one end of the crescent-shaped plate body 332, and the stop pin 42 is located at the other end of the crescent-shaped plate body 332. The stop pin 42, the crescent-shaped plate body 332, the third protrusion 336, and the driven gear ring 23 define a limiting cavity 335. The secondary plate 35 is crescent-shaped and is movably disposed within the limiting cavity.

[0049] Specifically, in the second embodiment of this utility model, the internal gear pump eliminates the first protrusion in the first embodiment, but retains the third protrusion 336 (the second protrusion 334). The third protrusion 336 can be integrated with the crescent-shaped plate body 332. The function of the first protrusion is achieved by the stop pin 42, which serves to limit and guide the movement of the auxiliary plate 35.

[0050] Furthermore, compared to the first embodiment, the arrangement of the stop pin 42 makes the structure of the positioning component more flexible. That is, in the first embodiment, the first protrusion is directly integrated on the main board 33, and its position and shape are relatively fixed; while in the second embodiment, the stop pin 42 is connected to the cover plate as an independent component, and its position can be adjusted and replaced according to actual needs, providing more possibilities for the design and optimization of the pump.

[0051] Similarly, in the second embodiment, there may be two main boards 33 and two sub-boards 35, with the two main boards 33 symmetrically arranged in the offset gap 13, and the main boards 33 and sub-boards 35 arranged in a one-to-one correspondence.

[0052] refer to Figure 4 This is a schematic diagram of the assembly of the crescent-shaped partition 30 and the positioning component 40b in the internal gear pump provided in the third embodiment of this utility model. The differences between the internal gear pump provided in the third embodiment and the internal gear pump provided in the above embodiments can be referred to as follows: The positioning component 40 also includes a stop pin 42, which is connected to the cover plate. The main plate 33 includes a crescent-shaped plate body 332 and a third protrusion 336. The third protrusion 336 is located at one end of the crescent-shaped plate body 332, and the stop pin 42 is located at the other end of the crescent-shaped plate body 332. The stop pin 42, the crescent-shaped plate body 332, the third protrusion 336 and the driven gear ring 23 define a limiting cavity 335. The secondary plate 35 is crescent-shaped and is movably disposed in the limiting cavity 335. The positioning pin 41 and the stop pin 42 are spaced apart in the circumferential direction of the driving gear 21. The positioning pin 41 is located on the side of the main plate 33 away from the stop pin 42 and abuts against the third protrusion 336.

[0053] Specifically, the positioning pin 41 can cooperate with the stop pin 42 to form a double positioning in the radial direction of the drive gear 21, restricting the movement of the main plate 33 and the auxiliary plate 35, preventing excessive displacement of the main plate 33 in the radial direction, and ensuring that the main plate 33 and the auxiliary plate 35 are always in the correct working position, thereby ensuring the normal operation of the pump.

[0054] Similarly, in the third embodiment, there are two main boards 33 and two sub-boards 35. The two main boards 33 are symmetrically arranged in the offset gap, and the main boards 33 and sub-boards 35 are arranged in a one-to-one correspondence.

[0055] It should be noted that, in the scheme protected in this application, the stop pin can be as follows: Figure 4 The position settings shown can also be configured as follows: Figure 1 The structural setup shown is sufficient as long as it limits the maximum distance the motherboard can move away from the sub-board.

[0056] refer to Figure 5 This is a schematic diagram of the assembly of the crescent-shaped partition and positioning assembly in the internal gear pump provided in the fourth embodiment of this utility model. The difference between the internal gear pump provided in the fourth embodiment of this utility model and the above embodiments is that the stop pin 42 has a first inclined surface 421, and the sub-plate 35 has a second inclined surface 351. The first inclined surface 421 and the second inclined surface 351 abut against each other to make the gap between the main plate 33 and the sub-plate 35 tend to increase.

[0057] Specifically, during operation, as the driving gear 21 and driven gear ring 23 rotate, the mutual contact of the first inclined surface 421 and the second inclined surface 351, through a wedge effect, changes the force direction on the main plate 33 and the secondary plate 35. This causes the main plate 33 and the secondary plate 35 to tend to move away from each other under force, meaning the gap between the main plate 33 and the secondary plate 35 tends to increase. For the main plate 33, it moves towards the driving gear 21 in the radial direction. This movement effectively reduces the gap between the tooth tip of the driving gear 21 and the main plate 33. This reduction in gap directly improves the sealing performance of this area, preventing fluid leakage from the gap between the tooth tip and the main plate 33.

[0058] Similarly, the secondary plate 35 also moves radially toward the driven gear ring 23 in the direction of the driving gear 21. This movement not only reduces the gap between the tooth tip of the driven gear ring 23 and the secondary plate 35, but also enhances the sealing effect in this area. Through the synergistic effect of the main plate 33 and the secondary plate 35, the sealing performance inside the pump body is significantly improved, thereby ensuring the efficient and stable operation of the pump.

[0059] Furthermore, this inclined surface design also possesses a certain degree of self-adaptability. Under different operating conditions, such as changes in flow rate and pressure fluctuations, the gap between the main plate 33 and the secondary plate 35 can be finely adjusted through the mutual contact of the inclined surfaces to adapt to these changes. This self-adaptability allows the pump body to maintain stable sealing performance and efficient operation under various complex working conditions.

[0060] Furthermore, when the stop pin 42 is provided with a first inclined surface 421, the stop pin 42 also includes a third inclined surface 422, and the main board 33 is provided with a fourth inclined surface 337 that abuts against the third inclined surface 422. This can improve the motion effect of the main board 33 and the sub-board 35, increase the motion tendency, and also improve the response efficiency of the main board 33 and the sub-board 35 when subjected to force. That is, when the stop pin is subjected to force, the abutting relationship between the third inclined surface 422 and the fourth inclined surface 337 will cause the main board 33 to generate a specific motion tendency, which not only allows the main board 33 to better adapt to the rotational motion of the drive gear 21.

[0061] Furthermore, the third inclined plane 422 intersects the first inclined plane 421, and the intersection angle between the third inclined plane 422 and the first inclined plane 421 is between 10° and 180°. For example, 10°, 20°, 50°, 110°, 150°, etc. It should be noted that the intersection angle between the third inclined plane 422 and the first inclined plane 421 can be selected as needed according to the pump's working pressure, structural strength, and other scenarios. In this embodiment, to ensure that the stop pin has a pushing effect on the main plate 33 and the sub-plate 35, the intersection angle between the third inclined plane 422 and the first inclined plane 421 is less than 180°.

[0062] In this embodiment, the sealing rod 51 and the elastic element 52 can be used in conjunction with the first inclined surface 421 and the third inclined surface 422. The pushing direction of the elastic element 52 on the sealing rod 51 is intersected with the action direction of the first inclined surface 421 and the second inclined surface 351. Similarly, the pushing direction of the elastic element 52 on the sealing rod 51 is also intersected with the action direction of the third inclined surface 422 and the fourth inclined surface 337, forming a dynamic mechanical balance to construct a mechanically intersecting action system.

[0063] Specifically, when the elastic element 52 attempts to separate the main board 33 and the sub-board 35, the inclined system guides the movement while also offsetting part of the separation force, keeping the main board 33 and the sub-board 35 within a relatively stable distance. This allows for automatic adjustment of the distance and force state between the main board 33 and the sub-board 35, thereby maintaining optimal working performance.

[0064] Furthermore, since the main board 33 is designed with a double-headed crescent-shaped structure, there are also two sub-boards 35. The stop pin 42 is located on the line of symmetry of the main board 33, and the two sub-boards 35 are symmetrically located on both sides of the stop pin 42. The first inclined surface 421 on the stop pin 42 is provided in two corresponding positions.

[0065] Optionally, the retaining pin 42 has at least a parallelogram segment, with one of two adjacent planes of the parallelogram segment abutting against the main plate 33 and the other of two adjacent planes of the parallelogram segment abutting against the secondary plate 35. That is, the four planes of the parallelogram segment can correspondingly form the first inclined surface 421 and the third inclined surface 422. The parallel relationship between the two planes can improve the sealing effect and response efficiency of the main plate 33 to the tooth tip of the driving gear 21 and the secondary plate 35 to the tooth tip of the driven gear ring 23.

[0066] It should be noted that, in order to ensure the smooth movement between the motherboard and the sub-board, a smooth transition surface is provided at the connection between the first and second inclined surfaces of the parallelogram segment. Therefore, in some embodiments, the parallelogram segment can also be referred to as a similar parallelogram segment.

[0067] In addition, one embodiment of this utility model also provides an integrated electric motor pump, which includes a motor module and the internal gear pump provided in any of the above embodiments. The motor module includes a drive shaft, and a drive gear is sleeved on the drive shaft. It should be noted that the internal gear pump provided in this application embodiment can be applied to this integrated electric motor pump. Therefore, the implementation principle and technical effects not mentioned in the integrated electric motor pump embodiment can be referred to the corresponding content in the aforementioned internal gear pump embodiment.

[0068] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "lateral", "upper", "lower", "front", "rear", "left", "right", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0069] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this utility model, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0070] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between them; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0071] In this utility model, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0072] In this utility model, the terms "one embodiment," "some embodiments," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of this utility model. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0073] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. An internal gear pump, characterized in that, The pump includes a pump housing, a drive gear, a driven gear ring, a crescent-shaped partition, and a positioning assembly. The pump housing includes a shell and a cover plate, which define a volumetric cavity. The drive gear and the driven gear ring are rotatably disposed within the volumetric cavity, and an offset gap is formed between the drive gear and the driven gear ring. The crescent-shaped partition is disposed within the offset gap and includes a main plate and a secondary plate. The positioning assembly has a positioning pin. During the rotation of the drive gear, the oil pressure in the pump housing causes the main plate to move relative to the secondary plate in the radial direction of the drive gear. One end of the positioning pin is connected to the cover plate, and the other end of the positioning pin is used to abut against the main plate to limit the maximum distance the main plate can move away from the secondary plate.

2. The internal gear pump according to claim 1, characterized in that, It also includes a sealing assembly, which includes a sealing rod and an elastic element. The main board is provided with a waist-shaped positioning hole and a mounting groove. The length direction of the waist-shaped positioning hole is consistent with the radial direction of the drive gear. The sealing rod is disposed in the mounting groove. The elastic element abuts between the sealing rod and the main board so that the sealing rod abuts against the sub-plate. The waist-shaped positioning hole is disposed on the main board and is located between the end of the main board and the mounting groove.

3. The internal gear pump according to claim 2, characterized in that, The main board includes a crescent-shaped plate body, a first protrusion and a second protrusion. The first protrusion and the second protrusion are respectively disposed at both ends of the crescent-shaped plate body. The first protrusion, the crescent-shaped plate body, the second protrusion and the driven gear ring define a limiting cavity. The sub-plate is crescent-shaped and is movably disposed in the limiting cavity.

4. The internal gear pump according to claim 2, characterized in that, The positioning component further includes a stop pin connected to the cover plate. The main board includes a crescent-shaped plate body and a third protrusion. The third protrusion is located at one end of the crescent-shaped plate body, and the stop pin is located at the other end of the crescent-shaped plate body. The stop pin, the crescent-shaped plate body, the third protrusion, and the driven gear ring define a limiting cavity. The secondary plate is crescent-shaped and is movably disposed within the limiting cavity.

5. The internal gear pump according to claim 4, characterized in that, The stop pin has a first inclined surface, and the sub-plate has a second inclined surface. The first inclined surface and the second inclined surface abut against each other to increase the gap between the main plate and the sub-plate.

6. The internal gear pump according to claim 5, characterized in that, The stop pin also includes a third inclined surface, and the main board is provided with a fourth inclined surface that abuts against the third inclined surface. The third inclined surface intersects with the first inclined surface, and the angle of intersection between the third inclined surface and the first inclined surface is 10° to 180°.

7. The internal gear pump according to claim 6, characterized in that, The stop pin has at least a parallelogram segment, one of two adjacent planes of the parallelogram segment abuts against the main plate, and the other of two adjacent planes of the parallelogram segment abuts against the sub-plate.

8. The internal gear pump according to claim 1, characterized in that, The positioning component further includes a stop pin connected to the cover plate. The main board includes a crescent-shaped plate and a third protrusion. The third protrusion is located at one end of the crescent-shaped plate, and the stop pin is located at the other end of the crescent-shaped plate. The stop pin, the crescent-shaped plate, the third protrusion, and the driven gear ring define a limiting cavity. The secondary plate is crescent-shaped and is movably disposed within the limiting cavity. The positioning pin and the stop pin are spaced apart in the circumferential direction of the driving gear. The positioning pin is located on the side of the main board away from the stop pin and abuts against the third protrusion.

9. The internal gear pump according to claim 3, 4, or 8, characterized in that, There are two main boards and two sub-boards. The two main boards are symmetrically arranged within the offset gap, and the main boards and sub-boards are arranged in a one-to-one correspondence.

10. An integrated electric motor pump, characterized in that, The invention includes a motor module and an internal gear pump according to any one of claims 1 to 9, wherein the motor module includes a drive shaft and the drive gear is sleeved on the drive shaft.

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