Internal gear pump and integrated motor pump

Abstract

The application provides an internal gear pump and an integrated motor pump, which comprises a shell, a driving gear, a driven gear ring and a crescent-shaped partition plate, the driving gear and the driven gear ring are arranged in the shell, and a working cavity and a bias gap are formed between the driving gear and the driven gear ring; the crescent-shaped partition plate is arranged in the bias gap, the crescent-shaped partition plate comprises a main plate and a secondary plate, the driving gear and the main plate overlap each other, the driven gear ring and the secondary plate overlap each other, and transition zones are formed at the overlapping positions; the main plate is provided with a first arc surface section towards the driving gear, the secondary plate is provided with a second arc surface section towards the driven gear ring, the first arc surface section and the second arc surface section are provided with unloading channels, and the two ends of the unloading channels are connected with the transition zones and the working cavity correspondingly. The application can effectively control the instantaneous increase or release of pressure in the transition zone, reduce the impact and noise, and help to improve the working stability of the pump.

Description

Technical Field

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

[0002] During the operation of an internal gear pump, when the tooth tip of the gear or gear ring overlaps with the surface of the crescent-shaped partition, a transition area (transition zone) is formed between the two tooth surfaces and the partition. The volume of this transition zone changes periodically with gear rotation. During the oil suction phase, as the gear rotates, the volume of the transition zone gradually decreases, leading to a sharp increase in internal pressure. This can cause cavitation, accompanied by severe noise and vibration, reducing the pump's lifespan. During the oil discharge phase, a significant pressure difference exists at the moment the transition zone contacts the discharge chamber, causing oil pressure fluctuations and affecting pump stability. Summary of the Invention

[0003] This invention is based on the inventor's discoveries and understanding of the following facts and problems:

[0004] During gear rotation, when the tooth tip contacts the partition surface, the enclosed space formed by the two tooth surfaces and the partition is the transition region. As the gear continues to rotate, the volume change in this region exhibits a significant nonlinear characteristic. During the oil suction phase, the volume of the transition region decreases sharply, and the internal oil is compressed. When the pressure exceeds the air separation pressure of the oil, the gas dissolved in the oil rapidly precipitates, forming cavitation. The microbubbles generated by cavitation collapse with pressure fluctuations, releasing localized high temperatures and shock waves, leading to metal surface erosion, noise, and vibration, severely shortening the lifespan of critical components such as bearings and gears.

[0005] During the oil discharge phase: at the instant the transition zone contacts the discharge chamber, a significant pressure difference exists between the two. This difference arises because the discharge chamber typically maintains a higher pressure, while the transition zone, having just transitioned from the suction zone, may still be at a relatively lower pressure. This pressure difference causes severe pressure fluctuations as the oil passes through the transition zone into the discharge chamber. These pressure fluctuations not only affect the smooth flow of the oil but can also trigger vibrations and noise in the hydraulic system. In severe cases, they can even degrade pump performance, impacting the stability and reliability of the entire hydraulic system.

[0006] Therefore, the present invention provides an internal gear pump and an integrated motor pump, which can effectively control the instantaneous increase or release of pressure in the transition zone, reduce impact and noise, and help improve the working stability of the pump.

[0007] The internal gear pump provided by this invention includes:

[0008] case;

[0009] A driving gear and a driven gear ring are both disposed within the housing, and a working cavity and an offset clearance are formed between the driving gear and the driven gear ring;

[0010] The crescent-shaped partition is disposed within the offset gap. The crescent-shaped partition includes a main plate and a secondary plate. A transition zone is formed at the overlap between the driving gear and the main plate and at the overlap between the driven gear ring and the secondary plate.

[0011] The main board has a first arcuate section facing the driving gear, and the sub-board has a second arcuate section facing the driven gear. Both the first and second arcuate sections are provided with unloading channels, and the two ends of the unloading channels are connected to the transition area and the working cavity respectively.

[0012] In summary, the internal gear pump provided by this invention, by setting unloading channels on the main board and the sub-board, can effectively control the instantaneous increase or release of pressure in the transition zone, reduce impact and noise, and help improve the working stability of the pump.

[0013] In some embodiments, the unloading channel includes a first channel and a second channel. A first notch is provided at the axial end of the first arc segment, and the first notch and the tooth tip of the driving gear define the first channel. A second notch is provided at the axial end of the second arc segment, and the second notch and the tooth tip of the driven gear define the second channel.

[0014] In some embodiments, the working chamber includes an oil suction chamber and an oil discharge chamber, the main board has two symmetrical tips, the transition zone includes a first oil zone and a second oil zone, the first oil zone and the second oil zone are respectively located at the two tips, the first channel is provided in two, one of the two first channels connects the first oil zone and the oil suction chamber, and one of the second channels connects the second oil zone and the oil discharge chamber.

[0015] In some embodiments, the subplate includes a first single-pointed crescent plate and a second single-pointed crescent plate. The first single-pointed crescent plate is disposed on the side of the bias gap near the oil suction chamber, and the second single-pointed crescent plate is disposed on the side of the bias gap near the oil discharge chamber. Two second channels are provided, and the two second channels are respectively disposed on the first single-pointed crescent plate and the second single-pointed crescent plate.

[0016] In some embodiments, the flow cross-sectional area of ​​the unloading channel gradually increases from the transition zone toward the working chamber.

[0017] In some embodiments, the internal gear pump further includes a buffer chamber disposed between the main plate and the sub-plate. The main plate has a third arcuate section that fits against the sub-plate, and the sub-plate has a fourth arcuate section that mates with the third arcuate section. At least one of the third arcuate section and the fourth arcuate section is provided with an oil guide channel, which connects the buffer chamber and the working chamber.

[0018] In some embodiments, a third notch is provided at the axial end of the third arcuate segment, and a fourth notch is provided at the axial end of the fourth arcuate segment, the third notch and the fourth notch defining the oil guide channel.

[0019] In some embodiments, the internal gear pump further includes a cover plate and a stop pin. The cover plate covers the opening of the housing. The main plate is provided with a positioning groove. One end of the stop pin is fixed to the cover plate, and the other end of the stop pin is inserted into the positioning groove. 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 make the gap between the main plate and the sub-plate tend to increase.

[0020] In some embodiments, the stop pin further includes a third inclined surface, and the positioning groove has 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°.

[0021] Furthermore, the integrated motor pump provided by the present invention 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 drive gear is sleeved on the drive shaft. Attached Figure Description

[0022] Figure 1 This is a schematic diagram of the structure of an internal gear pump provided in an embodiment of the present invention.

[0023] Figure 2 This is a schematic diagram of the assembly of the crescent-shaped partition and the retaining pin in an internal gear pump according to an embodiment of the present invention.

[0024] Figure 3 This is a three-dimensional schematic diagram of the combination of a crescent-shaped partition and a retaining pin in an internal meshing gear pump provided by an embodiment of the present invention.

[0025] Figure 4 This is a schematic diagram of an example of an internal gear pump provided by an embodiment of the present invention, showing the combination of a crescent-shaped partition and a retaining pin at another angle.

[0026] Figure 5 This is a three-dimensional schematic diagram of the main board in the crescent-shaped partition of an internal gear pump provided in an embodiment of the present invention.

[0027] Figure 6 This is a schematic diagram of the structure of the retaining pin in an internal meshing gear pump provided by an embodiment of the present invention.

[0028] Figure label:

[0029] 10. Housing; 11. Driving gear; 13. Driven gear ring; 15. Working chamber; 151. Oil suction chamber; 152. Oil discharge chamber; 17. Offset clearance; 19. Buffer chamber;

[0030] 20. Transition zone; 211. Driving gear oil cavity; 212. Driven gear oil cavity; 231. First oil zone; 232. Second oil zone; 233. Third oil zone; 234. Fourth oil zone;

[0031] 30. Crescent-shaped partition; 31. Main board; 311. First arc segment; 312. First notch; 313. Tip; 314. Third arc segment; 315. Third notch; 316. Mounting groove; 317. Crescent-shaped plate; 318. Protrusion; 319. Positioning groove; 3191. Fourth inclined surface;

[0032] 33. Secondary board; 331. Second arc segment; 332. Second notch; 333. First single-pointed crescent board; 334. Second single-pointed crescent board; 335. Fourth arc segment; 336. Fourth notch; 337. Second slope;

[0033] 40. Unloading passage; 41. First passage; 43. Second passage;

[0034] 50. Oil guide channel;

[0035] 61. Sealing rod; 63. Elastic element;

[0036] 71. Stop pin; 711. First inclined plane; 712. Third inclined plane; 713. Cylindrical segment; 714. Parallelogram segment. Detailed Implementation

[0037] Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0038] like Figures 1 to 6As shown, an embodiment of the present invention provides an internal gear pump, which includes a housing 10, a driving gear 11, a driven gear ring 13, and a crescent-shaped partition 30. The driving gear 11 and the driven gear ring 13 are both disposed within the housing 10, and a working cavity 15 and an offset gap 17 are formed between the driving gear 11 and the driven gear ring 13. The crescent-shaped partition 30 is disposed within the offset gap 17, and the crescent-shaped partition 30 includes a main plate 31 and a secondary plate 33. A transition region 20 is formed at the overlap between the driving gear 11 and the main plate 31, and at the overlap between the driven gear ring 13 and the secondary plate 33.

[0039] The main board 31 has a first arc section 311 facing the drive gear 11, and the secondary board 33 has a second arc section 331 facing the driven gear ring 13. Both the first arc section 311 and the second arc section 331 are provided with unloading channels 40, and the two ends of the unloading channels 40 are connected to the transition area 20 and the working cavity 15 respectively.

[0040] Specifically, the main plate 31 and the auxiliary plate 33 are arranged sequentially from the driving gear 11 toward the driven gear ring 13 along the radial direction of the driving gear 11, forming an arrangement of driving gear 11, main plate 31, auxiliary plate 33, and driven gear ring 13. During the operation of the internal gear pump, a transition zone 20 is formed at the instant when the tip 313 of the driving gear 11 overlaps with the tip 313 of the main plate 31. Similarly, a transition zone 20 is also formed at the instant when the tip 313 of the driven gear ring 13 overlaps with the tip 313 of the auxiliary plate 33.

[0041] The first arc-shaped section 311 of the main board 31 contacts the tooth tip of the drive gear 11. The first arc-shaped section 311 is provided with an unloading channel 40, which connects the transition zone 20 and the working chamber 15. This allows the fluid in the transition zone 20 to flow smoothly back to the working chamber 15 through the unloading channel 40, thereby effectively avoiding the impact and noise caused by the pressure accumulation and instantaneous release formed at the moment the drive gear 11 overlaps with the main board 31, which helps to improve the working stability of the pump.

[0042] In summary, the internal gear pump provided by the present invention can effectively control the instantaneous increase or release of pressure in the transition zone 20 by setting unloading channels 40 on the main board 31 and the sub-board 33, thereby reducing impact and noise and helping to improve the working stability of the pump.

[0043] In this embodiment, the flow cross-sectional area of ​​the unloading channel 40 gradually increases from the transition zone 20 towards the working chamber 15. This ensures a smoother acceleration process for the fluid as it passes through the unloading channel 40, reducing turbulence and energy loss caused by sudden changes in flow velocity. Secondly, with the increase in flow cross-sectional area, the pressure distribution of the fluid within the unloading channel 40 becomes more uniform, helping to reduce the impact and wear of the fluid on the channel walls and extend the channel's service life. The flow cross-sectional area can be understood as the width of the unloading channel 40, the width of the path available for fluid flow.

[0044] In addition, in some embodiments, two adjacent meshing teeth of the drive gear 11 and the main board 31 define a drive gear oil cavity 211, and the unloading channel 40 of the first arc segment 311 can connect at least two drive gear oil cavities 211. That is, during the rotation of the drive gear 11, at least two adjacent drive gear oil cavities 211 are connected to the working cavity 15 through the unloading channel 40.

[0045] Similarly, the two adjacent meshing teeth of the driven gear ring 13 and the sub-plate 33 define a driven gear oil cavity 212. The unloading channel 40 of the second arc section 331 can connect at least two driven gear oil cavities 212. That is, during the rotation of the driven gear ring 13, at least two adjacent driven gear oil cavities 212 are connected to the working cavity 15 through the unloading channel 40.

[0046] like Figure 1 , Figure 2 , Figure 3 and Figure 4 As shown, in some embodiments, the unloading channel 40 includes a first channel 41 and a second channel 43. A first notch 312 is provided at the axial end of the first arcuate segment 311. The first notch 312 and the tooth tip of the driving gear 11 define the first channel 41, which connects the transition area 20 (driving gear oil cavity 211) formed by the driving gear 11 and the main plate 31, and the working cavity 15. A second notch 332 is provided at the axial end of the second arcuate segment 331. The second notch 332 and the tooth tip of the driven gear ring 13 define the second channel 43, which connects the transition area 20 (driven gear oil cavity 212) formed by the driven gear ring 13 and the auxiliary plate 33, and the working cavity 15.

[0047] The first notch 312 and the second notch 332 are both located at the axial end, which not only facilitates machining but also reduces the formation of turbulence and eddies, thus helping to reduce energy loss and noise.

[0048] Furthermore, the working chamber 15 includes an oil suction chamber 151 and an oil discharge chamber 152. The main board 31 has two symmetrical tips 313. The transition zone 20 includes a first oil zone 231 and a second oil zone 232. The first oil zone 231 and the second oil zone 232 are respectively located at the two tips 313. There are two first channels 41. One of the two first channels 41 connects the first oil zone 231 and the oil suction chamber 151, and one of the second channels 43 connects the second oil zone 232 and the oil discharge chamber 152.

[0049] Specifically, the oil suction chamber 151 and the oil discharge chamber 152 are located on opposite sides of the crescent-shaped partition 30, meaning that oil enters the oil discharge chamber 152 through the oil suction chamber 151, the tooth groove of the driving gear 11, and the tooth groove of the driven gear ring 13. The main board 31 has two symmetrical tips 313, that is, the main board 31 is designed as a double-headed crescent-shaped structure, used for dynamically sealing the oil suction chamber 151 and the oil discharge chamber 152. One of the two tips 313 is located on one side of the oil suction chamber 151, and the other of the two tips 313 is located on one side of the oil discharge chamber 152, thereby forming the first oil zone 231 and the second oil zone 232 respectively.

[0050] Furthermore, the subplate 33 includes a first single-pointed crescent plate 333 and a second single-pointed crescent plate 334. The first single-pointed crescent plate 333 is located on the side of the offset gap 17 near the oil suction chamber 151, and the second single-pointed crescent plate 334 is located on the side of the offset gap 17 near the oil discharge chamber 152. There are two second channels 43, which are respectively located on the first single-pointed crescent plate 333 and the second single-pointed crescent plate 334.

[0051] That is, the transition zone 20 may include a third oil zone 233 and a fourth oil zone 234. The first single-pointed crescent plate 333 and the driven gear ring 13 define the third oil zone 233. The second channel 43 on the first single-pointed crescent plate 333 can connect the third oil zone 233 and the oil suction chamber 151. The second single-pointed crescent plate 334 and the driven gear ring 13 define the fourth oil zone 234. The second channel 43 on the second single-pointed crescent plate 334 can connect the fourth oil zone 234 and the oil discharge chamber 152. The two second channels 43 are correspondingly arranged with the first single-pointed crescent plate 333 and the second single-pointed crescent plate 334, that is, the two second channels 43 are symmetrical to each other.

[0052] It should be noted that the first single-cusped crescent 333 and the second single-cusped crescent 334 can be configured as a crescent shape. It is conceivable that in some embodiments, the first single-cusped crescent 333 can also be referred to as the first crescent 334, and the second single-cusped crescent 334 can be referred to as the second crescent 334.

[0053] In some embodiments of this application, the main board 31 may also be configured as a crescent-shaped structure, and correspondingly, the secondary board 33 is provided. Furthermore, since the main board 31 has only one tip 313, and the tip 313 is located on the side of the bias gap 17 near the oil suction chamber 151, the unloading channel 40 on the main board 31 can be adjusted accordingly. For example, the main board 31 may have only one unloading channel 40.

[0054] Furthermore, it should be clarified that both the first arc segment 311 and the second arc segment 331 have two axial ends. Correspondingly, the first channel 41 and the second channel 43 can be selected to be located at least one of the two axial ends as needed. In this embodiment, the first channel 41 and the second channel 43 are provided at both axial ends to form a dual-end channel system.

[0055] Furthermore, from a fluid flow perspective, providing channels at both axial ends creates a smoother and more efficient fluid flow path. When fluid flows inside the pump body, the channels at both ends can be fully utilized for diversion and convergence, thereby reducing flow resistance, improving flow efficiency, helping to reduce pump energy consumption, and enhancing overall operating efficiency.

[0056] Secondly, the dual-end channel system enhances the structural stability of the pump body. Because the channels are distributed at both ends, they can collectively bear the pressure and impact forces generated by fluid flow, thereby dispersing stress concentration and improving the pump body's durability and reliability. This structural layout helps extend the pump's service life and reduces the likelihood of failure.

[0057] like Figure 1 , Figure 2 , Figure 3 and Figure 4 As shown, in some embodiments, the internal gear pump further includes a buffer chamber 19, which is disposed between the main plate 31 and the sub-plate 33. The main plate 31 has a third arcuate section 314 that fits against the sub-plate 33, and the sub-plate 33 has a fourth arcuate section 335 that mates with the third arcuate section 314. At least one of the third arcuate section 314 and the fourth arcuate section 335 is provided with an oil guide channel 50, which connects the buffer chamber 19 and the working chamber 15, so that the fluid in the buffer chamber 19 can flow smoothly into or out of the working chamber 15 as needed, thereby achieving fine control of fluid flow.

[0058] In other words, during the operation of the internal gear pump, the fluid pressure in the working chamber 15 changes periodically due to the meshing and rotation of the gears. The buffer chamber 19, connected to the working chamber 15 through the oil guide channel 50, can absorb excess fluid when the pressure rises and release the stored fluid when the pressure drops, thereby effectively balancing the pressure fluctuations in the working chamber 15 and reducing the impact and noise caused by pressure changes.

[0059] Furthermore, a third notch 315 is provided at the axial end of the third arcuate segment 314, and a fourth notch 336 is provided at the axial end of the fourth arcuate segment 335. The third notch 315 and the fourth notch 336 define an oil guiding channel 50. Specifically, the third notch 315 and the fourth notch 336 can form complementary flow paths, allowing the fluid to maintain a relatively stable flow velocity and direction when passing through the oil guiding channel 50.

[0060] Furthermore, both the third notch 315 and the fourth notch 336 are located at the axial ends, which not only facilitates machining and reduces production costs, but also improves the compactness and overall integrity of the structure. In other words, since the notches are located at the ends, they do not interfere with other functional areas of the main plate 31 and the sub-plate 33, nor do they increase the additional space occupied, making the entire internal gear pump structure more compact and efficient.

[0061] In some embodiments, the internal gear pump further includes a sealing rod 61 and an elastic member 63. The main plate 31 is provided with a mounting groove 316, the sealing rod 61 is disposed in the mounting groove 316, and the elastic member 63 abuts between the sealing rod 61 and the main plate 31 so that the sealing rod 61 abuts against the sub-plate 33, thereby forming an elastic sealing support between the main plate 31 and the sub-plate 33.

[0062] That is, when the pump starts working, periodic pressure changes occur inside the pump as the driving gear 11 and driven gear ring 13 rotate. These pressure changes act on the sealing rod 61, attempting to force it out of the mounting groove 316. However, due to the presence of the elastic element 63, it applies a continuous elastic force to the sealing rod 61, ensuring that the sealing rod 61 remains tightly pressed against the sub-plate 33. This dynamic contact mechanism ensures the continuous stability of the sealing performance inside the pump body, effectively preventing fluid leakage.

[0063] Furthermore, the elastic properties of the elastic element 63 allow the sealing rod 61 to adapt to minor deformations and vibrations during pump operation. When the pump body is subjected to external vibrations or internal pressure fluctuations, the elastic element 63 can absorb this energy through its elastic deformation, thereby maintaining a tight fit between the sealing rod 61 and the auxiliary plate 33. This self-adaptive capability enables the pump body to maintain stable sealing performance under various complex operating conditions.

[0064] Optionally, the elastic element 63 can be a spring sheet.

[0065] Furthermore, the main board 31 includes a crescent-shaped plate 317 and a protrusion 318. The protrusion 318 is located at the tip 313 of the crescent-shaped plate 317 and extends from the crescent-shaped plate 317 toward the driven gear ring 13 in the radial direction of the driving gear 11. The crescent-shaped plate 317, the protrusion 318, and the driven gear ring 13 can limit the movement position of the sub-plate 33 to ensure that the sub-plate 33 is always in contact with the main board 31. The buffer chamber 19 is located between the sealing rod 61 and the protrusion 318. Correspondingly, the connection between the oil guide channel 50 and the buffer chamber 19 is located between the protrusion 318 and the sealing rod 61. In this embodiment, there are two protrusions 318, which are respectively located at both ends of the crescent-shaped plate 317, thereby limiting the position of the sub-plate 33.

[0066] Furthermore, the cross-sectional area of ​​the oil guide channel 50 gradually increases from the buffer chamber 19 toward the working chamber 15, and its effect is similar to that of the unloading channel 40, which will not be elaborated here.

[0067] like Figure 1 , Figure 2 , Figure 3 , Figure 4 , Figure 5 and Figure 6 As shown, in some embodiments, the internal gear pump further includes a cover plate and a stop pin 71. The cover plate covers the opening of the housing 10 to define a space for accommodating components such as the driving gear 11, the driven gear ring 13, and the crescent-shaped partition 30. The main plate 31 is provided with a positioning groove 319. One end of the stop pin 71 is fixed to the cover plate, and the other end of the stop pin 71 is inserted into the positioning groove 319. Furthermore, the stop pin 71 has a first inclined surface 711, and the secondary plate 33 has a second inclined surface 337. The first inclined surface 711 and the second inclined surface 337 abut against each other to increase the gap between the main plate 31 and the secondary plate 33.

[0068] Specifically, during pump operation, as the driving gear 11 and driven gear ring 13 rotate, the mutual contact of the first inclined surface 711 and the second inclined surface 337, through a wedge effect, changes the force direction of the main plate 31 and the secondary plate 33. This causes the main plate 31 and the secondary plate 33 to tend to move away from each other under force, meaning the gap between them tends to increase. For the main plate 31, it moves towards the driving gear 11 in the radial direction, effectively reducing the gap between the tooth tip of the driving gear 11 and the main plate 31. 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 31.

[0069] Similarly, the auxiliary plate 33 also moves radially toward the driven gear ring 13 in the direction of the driving gear 11. This movement not only reduces the gap between the tooth tip of the driven gear ring 13 and the auxiliary plate 33, but also enhances the sealing effect in this area. Through the synergistic effect of the main plate 31 and the auxiliary plate 33, the sealing performance inside the pump body is significantly improved, thereby ensuring the efficient and stable operation of the pump.

[0070] 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 31 and the secondary plate 33 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.

[0071] Furthermore, the stop pin 71 also includes a third inclined surface 712, and the positioning groove 319 has a fourth inclined surface 3191 that abuts against the third inclined surface 712. This can improve the movement effect of the main board 31 and the sub-board 33, increase the movement tendency, and also improve the response efficiency of the main board 31 and the sub-board 33 when subjected to force. That is, when the stop pin 71 is subjected to force, the abutting relationship between the third inclined surface 712 and the fourth inclined surface 3191 will cause the main board 31 to generate a specific movement tendency, which not only allows the main board 31 to better adapt to the rotational movement of the drive gear 11.

[0072] Furthermore, the third inclined plane 712 intersects the first inclined plane 711, and the intersection angle between the third inclined plane 712 and the first inclined plane 711 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 712 and the first inclined plane 711 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 71 has a pushing effect on the main board 31 and the sub-board 33, the intersection angle between the third inclined plane 712 and the first inclined plane 711 is less than 180°.

[0073] In this embodiment, the sealing rod 61 and the elastic element 63 can be used in conjunction with the first inclined surface 711 and the third inclined surface 712. The pushing direction of the elastic element 63 on the sealing rod 61 is intersected with the action direction of the first inclined surface 711 and the second inclined surface 337. Similarly, the pushing direction of the elastic element 63 on the sealing rod 61 is also intersected with the action direction of the third inclined surface 712 and the fourth inclined surface 3191, forming a dynamic mechanical balance to construct a mechanically intersecting action system.

[0074] Specifically, when the elastic element 63 attempts to separate the main board 31 and the sub-board 33, the inclined system guides the movement while also offsetting part of the separation force, keeping the main board 31 and the sub-board 33 within a relatively stable distance. This allows for automatic adjustment of the distance and force state between the main board 31 and the sub-board 33, thereby maintaining optimal working performance.

[0075] In this embodiment, the main board 31 is designed with a double-headed crescent-shaped structure, and therefore two sub-boards 33 are also provided. The stop pin 71 is located on the line of symmetry of the main board 31, and the two sub-boards 33 are symmetrically located on both sides of the stop pin 71. The first inclined surface 711 on the stop pin 71 is provided in two corresponding positions.

[0076] Optionally, such as Figure 6 As shown, the stop pin 71 may have a cylindrical section 713 and a parallelogram section 714 connected to each other. The cylindrical section 713 is inserted into the cover plate, and the parallelogram section 714 is inserted into the positioning groove 319 and abuts against the sub-plate 33. Furthermore, the four planes of the parallelogram section 714 can correspondingly form a first inclined surface 711 and a third inclined surface 712. Through the parallel relationship between the two, the sealing effect and response efficiency of the main plate 31 and the sub-plate 33 on the tooth tips (the main plate 31 on the tooth tip of the driving gear 11, and the sub-plate 33 on the tooth tip of the driven gear ring 13) can be improved.

[0077] 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 714. Therefore, in some embodiments, the parallelogram segment 714 may also be referred to as a similar parallelogram segment.

[0078] In addition, one embodiment of the present invention 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 11 is sleeved on the drive shaft. It should be noted that the internal gear pump provided in the embodiments of this application can be applied to the integrated electric motor pump. Therefore, the implementation principle and technical effects not mentioned in the integrated electric motor pump embodiments can be referred to the corresponding content in the aforementioned internal gear pump embodiments.

[0079] In the description of this invention, it should be understood that the terms "center", "length", "width", "thickness", "upper", "lower", "front", "rear", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing this invention and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention.

[0080] 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 technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0081] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," 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 invention according to the specific circumstances.

[0082] In this invention, 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," "over," and "on top" of 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.

[0083] In this invention, 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 the invention. 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.

[0084] 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, include: case; A driving gear and a driven gear ring are both disposed within the housing, and a working cavity and an offset clearance are formed between the driving gear and the driven gear ring; The crescent-shaped partition is disposed within the offset gap. The crescent-shaped partition includes a main plate and a secondary plate. A transition zone is formed at the overlap between the driving gear and the main plate and at the overlap between the driven gear ring and the secondary plate. The main board has a first arcuate section facing the driving gear, and the sub-board has a second arcuate section facing the driven gear. Both the first and second arcuate sections are provided with unloading channels, and the two ends of the unloading channels are connected to the transition area and the working cavity respectively.

2. The internal gear pump according to claim 1, characterized in that, The unloading channel includes a first channel and a second channel. A first notch is provided at the axial end of the first arc segment, and the first notch and the tooth tip of the driving gear define the first channel. A second notch is provided at the axial end of the second arc segment, and the second notch and the tooth tip of the driven gear define the second channel.

3. The internal gear pump according to claim 2, characterized in that, The working chamber includes an oil suction chamber and an oil discharge chamber. The main board has two symmetrical tips. The transition zone includes a first oil zone and a second oil zone. The first oil zone and the second oil zone are respectively located at the two tips. There are two first channels. One of the two first channels connects the first oil zone and the oil suction chamber, and one of the second channels connects the second oil zone and the oil discharge chamber.

4. The internal gear pump according to claim 3, characterized in that, The subplate includes a first single-pointed crescent plate and a second single-pointed crescent plate. The first single-pointed crescent plate is located on the side of the offset gap near the oil suction chamber, and the second single-pointed crescent plate is located on the side of the offset gap near the oil discharge chamber. There are two second channels, which are respectively located on the first single-pointed crescent plate and the second single-pointed crescent plate.

5. The internal gear pump according to claim 1, characterized in that, The cross-sectional area of ​​the unloading channel gradually increases from the transition zone toward the working chamber.

6. The internal gear pump according to claim 1, characterized in that, It also includes a buffer chamber, which is located between the main board and the sub-board. The main board has a third arc-shaped section that fits into the sub-board, and the sub-board has a fourth arc-shaped section that mates with the third arc-shaped section. At least one of the third arc-shaped section and the fourth arc-shaped section is provided with an oil guiding channel, which connects the buffer chamber and the working chamber.

7. The internal gear pump according to claim 6, characterized in that, The third arc segment has a third notch at its axial end, and the fourth arc segment has a fourth notch at its axial end. The third notch and the fourth notch define the oil guide channel.

8. The internal gear pump according to claim 1, characterized in that, It also includes a cover plate and a stop pin. The cover plate covers the opening of the housing. The main board has a positioning groove. One end of the stop pin is fixed to the cover plate, and the other end of the stop pin is inserted into the positioning groove. 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 make the gap between the main board and the sub-plate tend to increase.

9. The internal gear pump according to claim 8, characterized in that, The stop pin further includes a third inclined surface, and the positioning groove has 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°.

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.

Images