Gear pump and vehicle

Abstract

The utility model relates to the technical field of liquid pumps, in particular to a gear pump and a vehicle, the gear pump comprises a shell, a cover body, an inner gear, an outer gear, a crescent plate and a guide protrusion, the shell and the cover body are detachably connected to define a mounting space, an oil outlet is formed in the shell, an oil inlet is formed in the cover body, and the crescent plate is arranged in the mounting space; the inner gear, the outer gear and the crescent plate are arranged in the installation space, the crescent plate is arranged between the inner gear and the outer gear, notches are formed in the sides, facing the oil inlet or the oil outlet, of the end portions of the two sides of the outer arc section of the crescent plate, guide protrusions are arranged at the end portions of the two sides of the outer arc section of the crescent plate, and the end faces of the sides, facing the notches, of the guide protrusions are planes. And a guide area is defined by the guide bulge, the crescent plate and the outer gear. The utility model provides a gear pump to reduce pressure mutation of inlet and outlet oil and reduce vibration noise of the gear pump.

Description

Technical Field

[0001] This application relates to the field of liquid pump technology, and more particularly to a gear pump and vehicle. Background Technology

[0002] An internal gear pump is a type of pump that operates on the principle of internal gear meshing. It utilizes the meshing motion of internal gears to transport liquids. Its working principle involves the rotation of internal gears drawing liquid in through the inlet, then gradually compressing and pushing the liquid to the outlet under the action of gear meshing, forming a continuous fluid flow. Internal gear pumps have a simple and compact structure, providing stable flow and pressure output, and are commonly used in hydraulic systems, lubrication systems, and oil supply systems.

[0003] A low-vibration internal gear pump is proposed in related technologies. It reduces the fluctuation caused by pressure changes by setting damping grooves. However, it cannot solve the problem of gear vibration caused by pressure changes at the inlet and outlet oil ports. Summary of the Invention

[0004] This application provides a gear pump to reduce pressure fluctuations at the inlet and outlet of oil, thereby reducing vibration and noise. This application also proposes a vehicle.

[0005] The gear pump of this application embodiment includes:

[0006] A housing and a cover, the housing and the cover being detachably connected to form an installation space, the housing being provided with an oil outlet and the cover being provided with an oil inlet;

[0007] An internal gear, an external gear, and a crescent plate are arranged in an installation space. The crescent plate is positioned between the internal gear or the external gear, and the two ends of the outer arc segment of the crescent plate have notches on the side facing the oil inlet or the oil outlet.

[0008] The guide protrusions are provided on both ends of the outer arc segment of the crescent plate, and the side end of the guide protrusion facing the notch is flat, and the guide protrusion, the crescent plate and the external gear form a guide area.

[0009] This application provides a gear pump to reduce pressure fluctuations in the inlet and outlet oil and lower the vibration and noise of the gear pump.

[0010] In some embodiments, the crescent plate has an arcuate surface on the side opposite to the notch, and the radial dimension of the crescent plate in the internal gear gradually decreases as it approaches the oil outlet and oil inlet.

[0011] In some embodiments, one end face of the outer arc segment of the crescent plate that forms the guide area is a plane.

[0012] In some embodiments, both the oil inlet and the oil outlet include a first section and a second section. The inlet of the first section is used for the liquid to flow in and out. The outlet of the first section is connected to the inlet of the second section, and the outlet of the second section faces the guiding area.

[0013] The size of the axial section of the first section gradually increases in the direction close to the crescent plate.

[0014] The size of the axial section of the second section remains unchanged or gradually increases in the direction close to the crescent plate.

[0015] The radial dimension at the inlet of the first section is B, and the radial dimension at the inlet of the second section is C, and they satisfy: B < C, and 5 ≤ B ≤ 15 mm, 16 mm ≤ C ≤ 25 mm.

[0016] In some embodiments, a preset angle A is provided between the axis where the first section is located and the axis where the second section is located, and 100° ≤ A ≤ 160°.

[0017] In some embodiments, the guiding protrusion and the crescent plate are integrally formed.

[0018] In some embodiments, two damping grooves are provided on one side of the crescent plate away from the oil inlet and the oil outlet. Two damping grooves are formed on the inner arc section of the crescent plate. The two damping grooves are oppositely arranged at both ends of the inner arc section of the crescent plate along the central axis of the crescent plate, and the width of the damping groove gradually decreases from the end of the crescent plate towards the middle.

[0019] The vehicle according to the embodiment of the present application includes: the gear pump as described in any one of the above.

[0020] The vehicle according to the embodiment of the present application adopts the above gear pump to reduce the sudden change of the oil inlet and outlet pressure and reduce the vibration and noise of the gear pump. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to illustrate the embodiments of the present application more clearly, the drawings required for use in the embodiments will be briefly introduced below. Obviously, the drawings in the following description are only some embodiments of the present application. For those of ordinary skill in the art, other drawings can also be obtained based on these drawings without creative efforts.

[0022] Figure 1 Schematic diagram of the crescent plate structure of the gear pump in the related art;

[0023] Figure 2 Cross-sectional view schematic diagram of a gear pump provided by an embodiment of the present application;

[0024] Figure 3A schematic diagram of the internal and external gears provided in the embodiments of this application;

[0025] Figure 4 A schematic diagram of the crescent plate provided in an embodiment of this application;

[0026] Figure 5 A schematic diagram of the notch provided in an embodiment of this application;

[0027] Figure 6 One of the schematic diagrams of an oil inlet provided in an embodiment of this application;

[0028] Figure 7 A second schematic diagram of the oil inlet provided in an embodiment of this application;

[0029] Figure 8 This is the third schematic diagram of the oil inlet provided in the embodiments of this application.

[0030] The above figures include the following reference numerals:

[0031] Casing 1, cover 2, oil inlet 21, first section 211, second section 212

[0032] Internal gear 3, external gear 4

[0033] Crescent-shaped plate 5, second plane 51, arc-shaped surface 52, notch 53.

[0034] Guide protrusion 6, first plane 61,

[0035] Guide area 7. Detailed Implementation

[0036] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of this application.

[0037] It should be noted that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential," etc., indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing this application 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, and therefore should not be construed as a limitation of this application. The terms "installed," "connected," and "linked" should be interpreted broadly, for example, they can be fixed connections, detachable connections, or integral connections; they can be mechanical connections or electrical connections; they can be direct connections or indirect connections through an intermediate medium; they can be internal connections between two elements. The terms "parallel," "perpendicular," and "equal" include the described situation and situations similar to the described situation, the range of which is within an acceptable deviation range, wherein the acceptable deviation range is determined by those skilled in the art taking into account the measurement under discussion and the error associated with the measurement of a particular quantity (i.e., the limitations of the measurement system). For example, "parallel" includes absolute parallelism and approximate parallelism, where an acceptable deviation range for approximate parallelism can be, for example, within 5°; "perpendicular" includes absolute perpendicularity and approximate perpendicularity, where an acceptable deviation range for approximate perpendicularity can also be, for example, within 5°. "Equal" includes absolute equality and approximate equality, where an acceptable deviation range for approximate equality can be, for example, a difference between the two equal items being less than or equal to 5% of either one. Those skilled in the art will understand the specific meaning of the above terms in this application based on the specific circumstances.

[0038] To enable those skilled in the art to better understand the present application, the present application will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0039] The gear pump of this embodiment includes: a guide protrusion 6, an internal gear 3, an external gear 4, a crescent plate 5, a housing 1, and a cover 2. The housing 1 and the cover 2 are detachably connected to form an installation space. The housing 1 is provided with an oil outlet, and the cover 2 is provided with an oil inlet 21. The internal gear 3, the external gear 4, and the crescent plate 5 are disposed within the installation space. The crescent plate 5 is disposed between the internal gear 3 or the external gear 4, and notches 53 are provided on both sides of the outer arc segment of the crescent plate 5 facing the oil inlet 21 or the oil outlet.

[0040] Guide protrusions 6 are provided on both ends of the outer arc segment of the crescent plate 5, and the end face of the guide protrusion 6 facing the notch 53 is a plane, and the guide protrusion 6, the crescent plate 5 and the external gear 4 form a guide area 7. For example, the end face of the guide protrusion 6 facing the notch 53 is a first plane 61.

[0041] This application provides a gear pump to reduce pressure fluctuations in the inlet and outlet oil and lower the vibration and noise of the gear pump.

[0042] Specifically, such as Figures 1 to 8 As shown, the housing 1 and the cover 2 are detachably connected. The housing 1 is provided with an oil outlet, and the cover 2 is provided with an oil inlet 21. The internal gear 3, the external gear 4, and the crescent plate 5 are disposed inside the housing 1 and the cover 2 of the gear pump. The crescent plate 5 is disposed between the internal gear 3 and the external gear 4, that is, the internal gear 3 is eccentrically disposed relative to the external gear 4. One end of the crescent plate 5 is in contact with the internal gear 3, and the outer arc section of the crescent plate 5 is in contact with the inner wall surface of the external gear 4. The outer arc section of the crescent plate 5 is provided with a notch 53 facing the oil inlet 21 or the oil outlet to increase the volume of the oil inlet, reduce the flow resistance, make the pressure transition of the oil in and out of the gear tip smooth and reduce pressure sudden change, and reduce the vibration noise of the gear pump.

[0043] Meanwhile, the guide protrusion 6 is provided at both ends of the crescent plate 5. The side end face of the guide protrusion 6 facing the notch 53 is the first plane 61. The guide protrusion 6 and the outer gear 4 of the outer arc segment of the crescent plate 5 form a guide area 7, which can better guide the oil so that the oil flows to the preset area, reduce the turbulence when the oil flows, reduce vibration and noise, and improve the NVH performance of the vehicle when driving.

[0044] At the same time, the guide protrusion 6 fits into the external gear 4, making the contact surface of the guide protrusion 6 and the external gear 4 more tightly sealed, thereby preventing liquid leakage, improving the fluid sealing performance of the pump, and thus improving the volumetric efficiency of the gear pump.

[0045] The gear pump of this embodiment increases the volume of the oil inlet 21 and outlet by providing a notch 53 on the outer arc segment of the crescent plate 5. This allows for a smooth pressure transition when the oil enters and exits the tooth tips, reducing pressure spikes and lowering vibration noise. The guide protrusion 6 has a flat end face facing the notch 53, and it contacts the tooth tips of the external gear 4 to form a sealing surface to prevent oil leakage. The guide protrusion 6, the external gear 4, and the crescent plate 5 together form a guide area 7, limiting the oil flow range and guiding it. In the guide area 7, when the external gear 4 rotates, the tooth tips maintain line contact with the outer arc segment of the crescent plate 5 and the guide protrusion 6, achieving dynamic sealing in conjunction with the guide protrusion 6. The guide protrusion 6 guides the oil flow along the outer arc segment of the crescent plate 5, avoiding dead zones and eddies. Simultaneously, it evenly guides the sucked-in oil to the working chamber, ensuring sufficient flow in the gear meshing area. The guide protrusion 6 adjusts the flow channel cross-sectional area, creating a smooth transition from oil pressure.

[0046] In some embodiments, the crescent plate 5 has an arcuate surface 52 on the side opposite to the notch 53, and the radial dimension of the crescent plate 5 in the internal gear 3 gradually decreases as it approaches the oil outlet and the oil inlet 21.

[0047] Specifically, such as Figures 1 to 8 As shown, the inner arc segment of the crescent plate 5 is provided with an arc-shaped surface 52. It can be understood that the crescent plate 5 has arc-shaped surfaces 52 at both ends in the extending direction to further guide the oil flowing out of the guide area 7 to the preset area. The arc-shaped surface 52 and the guide area 7 adopt a rounded transition to reduce flow resistance. The arc-shaped surface 52 guides the oil in the guide area 7 and reduces local eddies.

[0048] Furthermore, one end face of the outer arc segment of the crescent plate 5 that forms the guiding area 7 is flat. This facilitates the processing and manufacturing of the crescent plate 5, and the planar structure at the notch 53 eliminates flow velocity fluctuations caused by changes in end face curvature, resulting in smoother oil flow. For example, one end face of the outer arc segment of the crescent plate 5 that forms the guiding area 7 is flat, and this flat surface is set as a second plane 51, which can restrict and guide the oil.

[0049] In some embodiments, both the oil inlet 21 and the oil outlet include a first section 211 and a second section 212. The inlet of the first section 211 is used for the inlet and outlet of liquid, and the outlet of the first section 211 is connected to the inlet of the second section 212. The outlet of the second section 212 faces the guide area 7.

[0050] The size of the axial section of the first segment 211 gradually increases along the direction closer to the crescent plate 5.

[0051] Specifically, such as Figures 1 to 8As shown, the inlet of the first section 211 is suitable for oil inlet and outlet. When the gear rotates forward, oil is input into the first section 211; when the gear rotates in reverse, oil is output from the first section 211. The size of the shaft cross-section of the first section 211 gradually increases along the direction close to the crescent plate 5, which is beneficial for oil pressure buffering, reducing oil resistance, reducing pressure surges, and reducing vibration and noise of the gear pump. The outlet of the second section 212 faces the guide area 7, and the radial dimension of the second section 212 is always greater than or equal to the radial dimension of the first section 211. It can be understood that the radial dimension of the first section 211 gradually increases from the inlet of the first section 211 towards the connection between the first section 211 and the second section 212, and the radial dimension of the connection between the second section 212 and the first section 211 is the same, so as to gradually guide the oil and reduce pressure surges, reduce flow resistance, and at the same time make the oil flow smoother and reduce noise.

[0052] Furthermore, the first segment 211 can be shaped like a frustum, a hemisphere, or a trumpet. The frustum-shaped structure has smooth sidewalls, and during the flow of the oil, its flow area gradually changes uniformly along the flow direction. When the oil enters the frustum-shaped first segment 211 from the inlet, the flow area gradually increases, and the oil can adapt to this change relatively smoothly, resulting in a more uniform pressure transition in space and effectively avoiding abrupt pressure changes caused by sudden changes in flow area.

[0053] When the oil enters the first section 211 of the hemispherical structure, it first enters a relatively large volume area. This area can buffer the oil pressure, allowing for initial adjustment and stabilization. Like a pressure-regulating "reservoir," it absorbs and releases pressure fluctuations, thus reducing the possibility of sudden pressure changes. The smooth, curved surface of the hemispherical shape also reduces eddies and turbulence generated during oil flow. The hemispherical structure guides the oil along a smoother path, reducing the generation of eddies and turbulence, and consequently minimizing sudden pressure changes.

[0054] The first section 211 of the trumpet-shaped structure allows for a relatively smooth adjustment of the oil flow direction and velocity during the guiding process, reducing pressure shocks caused by sudden changes in flow direction and minimizing local pressure loss. The inclination angle of the sidewalls of the trumpet-shaped structure can be optimized according to the oil flow characteristics, minimizing local pressure loss during flow. As the oil passes through the trumpet-shaped structure, the flow area gradually changes, allowing the oil to smoothly adapt to this change and avoiding pressure loss and sudden pressure changes caused by sudden contraction or expansion of the flow area.

[0055] Furthermore, the size of the axial section of the second section 212 remains unchanged or gradually increases in the direction closer to the crescent plate 5. When the size of the axial section remains unchanged, the size of the flow channel of the oil in the second section 212 is stable, and the oil can flow at a certain speed and direction, reducing the additional resistance caused by sudden changes in the channel. The stable axial section size can avoid pressure shocks caused by sudden reduction or expansion of the channel when the oil is flowing, thereby reducing the vibration of the gear pump and further reducing the noise during the operation of the gear pump.

[0056] If the axial section gradually increases, during the flow of the oil, the flow area gradually expands, the flow velocity of the oil will decrease correspondingly, and the pressure loss will also decrease, thereby reducing the flow resistance during the entire flow process. The gradually increasing axial section can also gradually release the pressure of the oil, avoiding sudden changes in pressure, which is beneficial to the smooth flow of the oil in the gear pump, thereby improving the NVH performance of the gear pump.

[0057] In some embodiments, the radial dimension at the inlet of the first section 211 is B, and the radial dimension at the inlet of the second section 212 is C, and the following is satisfied: B < C, and 5 ≤ B ≤ 15 mm, 15 mm < C ≤ 25 mm.

[0058] Specifically, as Figures 1 to 8 shown, the radial dimension at the inlet of the first section 211 is the position where the minimum radial dimension of the first section 211 is located.

[0059] B < C can be understood as that the radial dimension of the first section 211 gradually increases along the direction closer to the radial dimension of the second section 212. The radial dimension of the second section 212 can remain unchanged, or the radial dimension of the second section 212 gradually increases along the direction away from the first section 211. That is, the radial dimension at the connection between the second section 212 and the first section is the same as the radial dimension at the connection between the first section 211 and the second section 212. Then, the radial dimension of the first section 211 gradually decreases along the direction away from the second section 212, and the radial dimension of the second section 212 gradually increases along the direction away from the first section 211.

[0060] B can be 5 mm, 6 mm, 7 mm, 8 mm, 9 mm, 10 mm, 11 mm, 12 mm, 13 mm, 14 mm, 15 mm. Avoiding the radial dimension at the inlet of the first section 211 being too small may cause too high flow velocity when the fluid enters, resulting in large pressure loss and easily causing cavitation phenomenon, damaging the internal components of the equipment. On the other hand, if B is greater than 15 mm, due to the sudden decrease in the radial dimension between the first section 211 and the second section 212, it is easy to cause pressure fluctuations and generate noise.

[0061] C can be 16mm, 17mm, 18mm, 19mm, 20mm, 21mm, 22mm, 23mm, 24mm, or 25mm. Different sizes of the second section 212 can be used depending on different situations. However, when C is greater than 25mm, it will not only increase the manufacturing cost and volume of the equipment, but may also cause the fluid to flow too slowly in the second section 212, affecting the overall working efficiency of the equipment.

[0062] In some embodiments, a preset angle A is provided between the axis of the first segment 211 and the axis of the second segment 212, where 100°≤A≤160°. When A is less than 100°, the fluid flow or power transmission path between the first segment 211 and the second segment 212 may become too tortuous, increasing flow resistance or power loss. Simultaneously, an excessively small angle may also reduce the space utilization efficiency within the device, increasing its size and weight. If A is greater than 160°, the connection structure between the first segment 211 and the second segment 212 becomes more complex, increasing design and manufacturing costs and installation difficulty, and reducing the reliability and lifespan of the device.

[0063] Within the range of 100°≤A≤160°, the fluid can flow from the first segment 211 to the second segment 212 in a relatively smooth path, reducing fluid turbulence and eddy currents, reducing energy loss, and improving fluid transport efficiency.

[0064] In some embodiments, the guide protrusion 6 is integrally formed with the crescent plate 5 to improve the stability and safety of the connection between the crescent plate 5 and the guide protrusion 6.

[0065] Furthermore, two damping grooves are provided on the side of the crescent plate 5 away from the oil inlet 21 and the oil outlet. Two damping grooves are formed on the inner arc segment of the crescent plate 5, and are positioned opposite each other at both ends of the inner arc segment along the central axis of the crescent plate 5. The width of the damping grooves gradually decreases from the ends of the crescent plate 5 towards the middle. That is, the damping grooves extend along the extension direction of the crescent plate 5 on the inner arc segment, and the width direction of the damping grooves extends axially upwards along the internal gear 3 or the external gear 4. The gradually changing width of the damping grooves can adapt to different fluid flow rates or vibration frequencies under different operating conditions, providing adaptive buffering capability. The damping grooves are existing damping grooves and will not be described in detail here.

[0066] The vehicle in this application embodiment includes: a gear pump as described in any of the above.

[0067] The vehicle in this application embodiment uses the aforementioned gear pump to reduce pressure fluctuations in the oil entering and exiting the pump, thereby reducing vibration and noise. A detailed description of the method provided in this application has been given above. Specific examples have been used to illustrate the principles and implementation methods of this application. The descriptions of the above embodiments are merely for the purpose of helping to understand the method and core ideas of this application. It should be noted that those skilled in the art can make various improvements and modifications to this application without departing from its principles, and these improvements and modifications also fall within the protection scope of the claims of this application.

Claims

1. A gear pump, characterized in that, Comprising: A housing and a cover body, the housing and the cover body are detachably connected to enclose an installation space, an oil outlet is provided on the housing, and an oil inlet is provided on the cover body; An internal gear, an external gear and a crescent plate, the internal gear, the external gear and the crescent plate are arranged in the installation space, the crescent plate is arranged between the internal gear or the external gear, and gaps are provided on both ends of the outer arc section of the crescent plate on the side facing the oil inlet or the oil outlet; A guiding protrusion, guiding protrusions are provided on both ends of the outer arc section of the crescent plate, and the end face of the guiding protrusion facing the gap is a plane, and the guiding protrusion and the crescent plate and the external gear enclose a guiding area.

2. The gear pump according to claim 1, characterized in that, An arc surface is provided on the side of the crescent plate背离 the gap, and the radial dimension of the crescent plate in the internal gear gradually decreases along the direction close to the oil outlet and the oil inlet.

3. The gear pump according to claim 1, characterized in that, The end face of the outer arc section of the crescent plate enclosing the guiding area is a plane.

4. The gear pump according to claim 1, characterized in that, Both the oil inlet and the oil outlet include a first section and a second section, the inlet of the first section is used for liquid inlet and outlet, the outlet of the first section is connected to the inlet of the second section, and the outlet of the second section faces the guiding area, The size of the axial section of the first section gradually increases along the direction close to the crescent plate.

5. The gear pump according to claim 4, characterized in that, The size of the axial section of the second section remains unchanged or gradually increases along the direction close to the crescent plate.

6. The gear pump according to claim 4, characterized in that, The radial dimension at the inlet of the first section is B, the radial dimension at the inlet of the second section is C, and it satisfies: B < C, and 5 ≤ B ≤ 15mm, 16mm ≤ C ≤ 25mm.

7. The gear pump according to claim 4, characterized in that, A preset angle A is provided between the axis where the first section is located and the axis where the second section is located, and 100° ≤ A ≤ 160°.

8. The gear pump according to claim 1, characterized in that, The guiding protrusion and the crescent plate are integrally formed.

9. The gear pump according to claim 1, characterized in that, Two damping grooves are provided on the side of the crescent plate away from the oil inlet and the oil outlet, and two damping grooves are provided on the inner arc section of the crescent plate. The two damping grooves are oppositely arranged at both ends of the inner arc section of the crescent plate along the central axis of the crescent plate, and the width of the damping groove gradually decreases from the end of the crescent plate towards the middle.

10. A vehicle, characterized in that, Comprising: The gear pump according to any one of claims 1-9.

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