Gear pump

Abstract

The invention relates to the technical field of tooth crest gap leakage, discloses a gear pump, and aims to solve the problem that the performance, the operation efficiency and the operation stability of the gear pump are reduced due to leakage jet flow caused by a relatively large tooth crest gap in the gear pump. A driving gear and a driven gear of the gear pump are mounted in a pump body, are in meshed connection and are used for driving fluid to flow in the pump body. And at least one of the driving gear and the driven gear is provided with a jet flow channel at the gear teeth. The jet flow channel is provided with a flow inlet and a jet flow opening which communicate with each other, and when the gear teeth rotate towards the high-pressure side, the flow inlet is formed in the high-pressure side of the gear teeth and used for enabling part of fluid to enter the jet flow channel from the flow inlet and be sprayed out from the jet flow opening so as to increase the drainage resistance of the tooth top gap. The spontaneous jet flow jetted through the jet flow channel and the leakage jet flow of the tooth crest gap form convection flow, so that the flowing speed of the leakage jet flow is reduced, the leakage flow resistance is increased, and the performance, the operation efficiency and the operation stability of the gear pump are improved.

Description

Technical Field

[0001] The present application relates to the technical field of tooth tip clearance leakage, and in particular to a gear pump. Background Art

[0002] A gear pump is a positive displacement pump that uses the change in the volume of a sealed cavity to compress the fluid to perform work. Due to its simple structure, ability to perform work continuously and low cost, it is widely used in aerospace, agricultural engineering, petrochemical and other fields.

[0003] In order to reduce the friction resistance of the gears in the gear pump during rotation, a large gap (i.e., tooth tip gap) is reserved between the gears and the inner wall of the pump body or the meniscus. However, when the gear teeth rotate toward the high-pressure side, the fluid on both sides of the gear teeth has a large pressure gradient. Under the action of the large pressure gradient, the fluid will form a leakage jet from the high-pressure area to the low-pressure area through the tooth tip gap. The interaction between the leakage jet and the mainstream will form a complex flow vortex, thereby reducing the performance, operating efficiency and stability of the gear pump. Summary of the invention

[0004] The purpose of the present application is to provide a gear pump, aiming to solve the problem of leakage jet caused by a large tooth top clearance inside the gear pump, and the leakage jet will lead to reduced performance, operating efficiency and operating stability of the gear pump.

[0005] In order to achieve the above objectives, this application adopts the following technical solutions:

[0006] Some embodiments of the present application provide a gear pump, including a pump body, a driving gear and a driven gear, wherein the driving gear and the driven gear are installed in the pump body and meshedly connected to drive the fluid to flow in the pump body. At least one of the driving gear and the driven gear is provided with a jet channel at the gear tooth. The jet channel has a connected inlet and a jet port. When the gear tooth rotates toward the high-pressure side, the inlet is arranged on the high-pressure side of the gear tooth, so that part of the fluid enters the jet channel from the inlet and is ejected from the jet port to increase the leakage resistance of the tooth top clearance. In some embodiments, the jet port is arranged on the tooth top side of the gear tooth radially away from the axis.

[0007] In some embodiments, when the gear teeth rotate toward the high-pressure side, a portion of the jet channel close to the jet port is tilted toward the rotation direction of the gear teeth.

[0008] In some embodiments, the axis of the jet channel near the jet orifice coincides with one of the radial lines of the gear tooth.

[0009] In some embodiments, when the gear tooth rotates toward the high-pressure side, a jet port is provided at a position close to the tooth top on the high-pressure side of the gear tooth, and an inlet port is provided at a position close to the tooth root on the high-pressure side of the gear tooth.

[0010] In some embodiments, a plurality of jet channels are provided at one gear tooth. At one gear tooth, the plurality of jet channels are distributed at intervals along the axial direction of the gear tooth.

[0011] In some embodiments, in the same jet channel, the opening area of ​​the jet port is smaller than or equal to the opening area of ​​the inlet port.

[0012] In some embodiments, the cross-sectional shapes of the inlet and the jet port are circular.

[0013] Alternatively, at least the cross-sectional shape of the jet port is rectangular.

[0014] In some embodiments, the driving gear and the driven gear are externally meshed structures.

[0015] Alternatively, the gear pump further comprises a meniscus, the driving gear is radially located inside the driven gear, the meniscus is installed between the driving gear and the driven gear, and the driving gear and the driven gear are in an internal meshing structure.

[0016] In some embodiments, at least some of the gear teeth of the driving gear and the driven gear are provided with jet channels.

[0017] In this way, through the setting of the jet channel, in the process of the gear pump driving the fluid to transport and flow. When the gear teeth in the pump body rotate to a position close to the high-pressure side (i.e., the pressure flow area), the fluid located on the high-pressure side of the gear teeth enters the jet channel through the inlet, and is ejected from the jet port near the tooth top of the gear teeth to form a self-ejected flow. The self-ejected flow can be sprayed toward the inner wall of the pump body (such as an external gear pump), or it can be sprayed toward the meniscus (such as an internal gear pump), so that the self-ejected flow can form convection with the leakage jet at the tooth top gap, so that the two are mixed and form a vortex, so as to cooperate with the mainstream to further increase the impact loss of the leakage jet and reduce the flow velocity of the leakage jet. Based on this, the self-ejected flow formed by the jet channel can increase the leakage resistance at the tooth top gap, thereby reducing the flow velocity and leakage amount of the leakage jet, which is beneficial to improve the performance parameters such as the head, flow rate and flow rate of the gear pump and the operating efficiency.

[0018] Moreover, compared with the technical solutions of reducing the tooth top clearance radially or adding sealing components in the related art, the above-mentioned jet channel solution does not increase the friction resistance between the driving gear and the driven gear and the pump body or the meniscus, so that the driving gear and the driven gear in the pump body can rotate smoothly, thereby maintaining good operating stability of the gear pump. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required for use in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0020] Figure 1 A cross-sectional view of a gear pump with an external meshing structure provided in an embodiment of the present application;

[0021] Figure 2 for Figure 1 A partial enlarged view of the middle A;

[0022] Figure 3 for Figure 1 A partial enlarged view of point B in the middle;

[0023] Figure 4 A cross-sectional view of an internal meshing structure of a gear pump provided in an embodiment of the present application;

[0024] Figure 5 for Figure 1 A partial enlarged schematic diagram of the first gear tooth is shown in FIG.

[0025] Figure 6 for Figure 1 Another partial enlarged schematic diagram of the first gear tooth is shown in ;

[0026] Figure 7 for Figure 1 A partial enlarged schematic diagram of the first gear tooth along the radial direction is shown in FIG.

[0027] Figure 8 for Figure 1 Another partial enlarged schematic diagram along the radial direction of the first gear tooth is shown in .

[0028] Reference numerals:

[0029] 100. Gear pump;

[0030] 10. Pump body; 11. Inlet end; 12. Outlet end; 13. Suction flow area; 14. Pressure flow area;

[0031] 20. Driving gear; 21. First gear tooth;

[0032] 30. driven gear; 31. second gear teeth;

[0033] 40. jet channel; 41. flow inlet; 42. jet outlet;

[0034] 50. Meniscus. DETAILED DESCRIPTION

[0035] In order to make the above-mentioned purposes, features and advantages of the present application more obvious and easy to understand, the specific implementation methods of the present application are described in detail below in conjunction with the accompanying drawings. In the following description, many specific details are set forth to facilitate a full understanding of the present application. However, the present application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without violating the connotation of the present application, so the present application is not limited by the specific embodiments disclosed below.

[0036] In the description of the present application, it should be understood that if the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. appear, the orientation or position relationship indicated by these terms is based on the orientation or position relationship shown in the accompanying drawings, which is only for the convenience of describing the present application and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present application.

[0037] In addition, if the terms "first" or "second" appear, these terms are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include at least one of the features. In the description of this application, if the term "plurality" appears, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0038] In this application, unless otherwise clearly specified and limited, if the terms "installed", "connected", "connected", "fixed" and the like appear, these terms should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integrated connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to the specific circumstances.

[0039] It should be noted that if an element is referred to as being "fixed to" or "disposed on" another element, it may be directly on the other element or there may be a central element. If an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be a central element at the same time. If any, the terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used in this application are for illustrative purposes only and do not represent the only implementation method.

[0040] The present application embodiment provides a gear pump, Figures 1 to 8 The gear pump according to the embodiment of the present application is described in detail.

[0041] See also Figure 1 , Figure 1 A gear pump provided in an embodiment of the present application is a cross-sectional view of an external meshing structure. The embodiment of the present application provides a gear pump 100, including a pump body 10, a driving gear 20 and a driven gear 30. The driving gear 20 and the driven gear 30 are installed in the pump body 10 and meshedly connected. The driving gear 20 can drive the driven gear 30 to mesh and rotate in the pump body 10 through the drive of a driving member such as a motor, so as to drive the fluid to flow in the pump body 10. Through the rotational engagement and rotational separation of the driving gear 20 and the driven gear 30 along a preset direction, the internal space of the pump body 10 forms a suction flow area 13 (close to the inlet end 11 of the pump body 10) and a pressure flow area 14 (close to the outlet end 12 of the pump body 10).

[0042] Exemplarily, when the driving gear 20 and the driven gear 30 rotate in a preset direction, the gear teeth of the driving gear 20 and the driven gear 30 gradually withdraw from meshing to form a suction area 13 in the pump body 10. The suction area 13 is a negative pressure space, so that the pump body 10 can suck the external flow graph into the suction area 13 through the inlet end 11. As the driving gear 20 and the driven gear 30 rotate, the fluid in the suction area 13 enters the pressure flow area 14 driven by the rotating gear teeth. In the pressure flow area 14, the rotating gear teeth of the driving gear 20 and the driven gear 30 gradually mesh to reduce the volume of the grooves between the gear teeth, so as to increase the pressure in the cavity through the reduced volume and squeeze the fluid to the outlet end 12 of the pump body 10 for discharge, thereby realizing the conveying flow of the fluid.

[0043] The gear pump 100 changes the volume of the sealed cavity in the pump body 10 by rotating the teeth of the driving gear 20 and the driven gear 30, thereby compressing the fluid to perform work, thereby driving the fluid to flow in the pump body 10 and be discharged from the outlet end 12 of the pump body 10 to achieve the conveying flow of the fluid. Since the gear pump 100 has the advantages of simple structure, continuous work and low cost, it is widely used in aerospace, agricultural engineering, petrochemical and other fields.

[0044] In order to reduce the friction resistance of the internal gear of the gear pump 100 during rotation, a large gap (i.e., tooth top gap) is reserved between the gear teeth of the driving gear 20 and the driven gear 30 and the inner wall or meniscus of the pump body 10. However, when the gear teeth of the driving gear 20 and the driven gear 30 rotate toward the high-pressure side, since the fluid on both sides of the gear teeth has a large pressure gradient, the fluid will form a leakage jet from the high-pressure area to the low-pressure area through the tooth top gap under the action of the large pressure gradient. The interaction between the leakage jet and the mainstream will form a complex flow vortex system, thereby reducing the performance, operating efficiency and operating stability of the gear pump 100.

[0045] To solve the above problems, continue to refer to Figure 1 At least one of the driving gear 20 and the driven gear 30 is provided with a jet channel 40 at the gear teeth. Figure 2 , Figure 2 for Figure 1 The jet channel 40 has an inlet 41 and a jet port 42 connected to each other. For example, the gear teeth of the driving gear 20 are the first gear teeth 21, and the gear teeth of the driven gear 30 are the second gear teeth 31. The first jet channel disposed at the first gear teeth 21 and the second jet channel disposed at the second gear teeth 31 are both jet channels 40.

[0046] Based on this, when the first gear tooth 21 and the second gear tooth 31 rotate toward the high-pressure side (i.e., the pressure flow area 14), the inlet 41 is arranged on the high-pressure side of the gear tooth, so as to allow part of the fluid to enter the jet channel 40 from the inlet 41 and be ejected from the jet port 42, so as to increase the leakage resistance of the tooth top clearance.

[0047] Reference Figure 1 and Figure 2 Taking the driving gear 20 as an example, when the first gear tooth 21 of the driving gear 20 rotates toward the pressure flow area 14, the inlet 41 is arranged on the high-pressure side of the first gear tooth 21 (that is, the side of the first gear tooth 21 close to the pressure flow area 14 at this time), so as to allow part of the fluid to enter the jet channel 40 from the inlet 41 and be ejected from the jet port 42, so as to increase the leakage resistance of the tooth top clearance.

[0048] Reference Figure 1 and Figure 3 , Figure 3 for Figure 2 A partial enlarged view of the B in the middle. Taking the driven gear 30 as an example, when the second gear tooth 31 of the driven gear 30 rotates toward the pressure flow area 14, the inlet 41 is arranged on the high-pressure side of the second gear tooth 31 (i.e., the side of the second gear tooth 31 close to the pressure flow area 14 at this time), so as to allow part of the fluid to enter the jet channel 40 from the inlet 41 and be ejected from the jet port 42, so as to increase the leakage resistance of the tooth top clearance.

[0049] Thus, through the setting of the jet channel 40, in the process of the gear pump 100 driving the fluid to transport and flow. When the gear teeth in the pump body 10 rotate to a position close to the high-pressure side (i.e., the pressure flow area 14), the fluid located on the high-pressure side of the gear teeth enters the jet channel 40 through the inlet 41, and is ejected from the jet port 42 near the tooth top of the gear teeth to form a self-ejecting flow. The self-ejecting flow can be ejected toward the inner wall of the pump body 10 (such as an external gear pump), or it can be ejected toward the meniscus (such as an internal gear pump), so that the self-ejecting flow can form convection with the leakage jet at the tooth top gap, so that the two are mixed and form a vortex, so as to cooperate with the mainstream to further increase the impact loss of the leakage jet and reduce the flow velocity of the leakage jet. Based on this, the self-ejecting flow formed by the jet channel can increase the leakage resistance at the tooth top gap, thereby reducing the flow velocity and leakage amount of the leakage jet, which is beneficial to improve the performance parameters such as the head, flow rate and flow rate of the gear pump 100 and the operating efficiency.

[0050] Moreover, compared with the technical solutions of reducing the tooth top clearance radially or adding sealing components in the related art, the solution of the jet channel 40 does not increase the friction resistance between the driving gear 20 and the driven gear 30 and the pump body 10 or the meniscus, so that the driving gear 20 and the driven gear 30 in the pump body 10 can rotate smoothly, thereby maintaining good operating stability of the gear pump 100.

[0051] It should be noted that, in the embodiment of the present application, the gear pump 100 may be as follows: Figure 1 The external gear pump shown has an external gear structure in which the driving gear 20 and the driven gear 30 are in the pump body 10 .

[0052] Or, if Figure 4 As shown, Figure 4 The gear pump provided in the embodiment of the present application is a cross-sectional view of a meshing structure. That is, the gear pump 100 can also be Figure 4 In the internal meshing gear pump shown, the gear pump 100 also includes a meniscus 50. In the pump body, the driving gear 20 is an external meshing gear, and the driven gear 30 is an internal meshing gear. The driving gear 20 is located radially inside the driven gear 30, and the meniscus 50 is installed between the driving gear 20 and the driven gear 30, and the driving gear 20 and the driven gear 30 are an internal meshing structure.

[0053] In this way, Figure 4In the internal gear pump shown, the driving gear 20 drives the driven gear 30 to rotate counterclockwise as an example. Along the rotation direction of the driving gear 20, the area where the downstream end (such as the upper end) of the meniscus 50 is located is the pressure flow area 14, and the area where the upstream end (such as the lower end) of the meniscus 50 is located is the suction flow area 13. By providing the above-mentioned jet channel 40 at the gear teeth (such as the first gear teeth 21 or the second gear teeth 31) of at least one of the driving gear 20 and the driven gear 30, the leakage resistance of the tooth top clearance at the meniscus 50 can also be increased.

[0054] That is, the arrangement of the jet channel 40 is applicable to both external gear pumps and internal gear pumps, and can increase the leakage resistance at the tooth tip clearance. In the embodiments of the present application, unless otherwise specified, the structure of the external gear pump is generally used for description.

[0055] In the embodiment of the present application, the self-ejecting flow ejected from the jet port 42 can be radially ejected toward the inner wall of the pump body 10 or the meniscus 50. When the gear teeth rotate and approach the pressure flow area 14, the self-ejecting flow ejected from the jet port 42 can be arranged to be ejected obliquely toward the pressure flow area 14 (high pressure side) while being ejected toward the inner wall of the pump body 10 or the meniscus 50, which is beneficial to reduce the leakage of the self-ejecting flow through the gear gap.

[0056] In some embodiments, the jet port 42 is disposed on the tooth top side radially away from the axis.

[0057] For example, Figure 2 As shown, a jet port 42 is provided on the tooth top side of the first gear tooth 21. Figure 3 A jet port 42 may also be provided on the tooth top side of the second gear tooth 31 .

[0058] In this way, by providing the jet port 42 on the tooth top side, the self-ejecting flow ejected from the jet port 42 can flow directly to the tooth top gap, thereby increasing the leakage resistance of the leakage jet in the tooth top gap.

[0059] In some embodiments, when the gear teeth rotate toward the high-pressure side, the portion of the jet channel 40 close to the jet port 42 is tilted toward the rotation direction of the gear teeth.

[0060] For example, Figure 2 As shown, when the first gear tooth 21 rotates toward the pressure flow area 14 (ie, the high pressure side), the portion of the jet channel 40 close to the jet port 42 is inclined toward the rotation direction of the first gear tooth 21 .

[0061] Correspondingly, such as Figure 3 As shown, when the second gear tooth 31 rotates toward the pressure flow area 14 , the portion of the jet channel 40 close to the jet port 42 is tilted toward the rotation direction of the second gear tooth 31 .

[0062] It should be noted that, for the gear pump 100 with an external meshing structure, the rotation directions of the driving gear 20 and the driven gear 30 are opposite. Figure 1 and Figure 2 As shown, when the gear pump 100 is in operation, the driving gear 20 on the left rotates in a clockwise direction, and the driven gear on the right rotates in a counterclockwise direction. At this time, the jet channel 40 in the first gear 21 and the second gear 31 is tilted toward the outlet end 12 of the middle pump body 10 in the rotation direction at the portion close to the jet port 42.

[0063] In this way, the jet channel 40 is arranged to be inclined toward the rotation direction of the gear by arranging the distribution near the jet port 42, so that the self-ejected flow ejected from the jet port 42 and the leakage jet at the tooth tip clearance form a convection with a smaller angle. For example, compared with the radial line at the jet port 42, the larger the inclination angle of the jet channel 40 near the jet port 42, the smaller the convection angle between the self-ejected flow and the leakage jet, that is, the more obvious the obstruction effect of the self-ejected flow on the leakage jet, which is conducive to further increasing the leakage resistance at the tooth tip clearance.

[0064] In some other embodiments, such as Figure 5 As shown, Figure 5 for Figure 1 A partial enlarged schematic diagram of the first gear tooth 21 is shown in FIG. The axis of the jet channel 40 near the jet port 42 coincides with one of the radial lines of the gear tooth (eg, the first gear tooth 21 ).

[0065] It can be understood that due to processing errors and other reasons, the definition of "coincidence" in the embodiments of the present application means that the minimum angle between the axis and the corresponding radial line is less than or equal to 5°, which can be regarded as the coincidence of the axis and the corresponding radial line.

[0066] As the fluid enters the jet channel 40 from the inlet 41 and is ejected from the jet port 42, the fluid changes its flow direction under the action of the inner wall of the jet channel 40 so that the self-ejected flow ejected from the jet port 42 forms a convection or vortex system with the leakage jet at the tooth top gap. Through the above structure, the bending angle of the jet channel 40 can be reduced, thereby reducing the change of direction angle of the fluid in the jet channel, which is conducive to increasing the flow rate of the self-ejected flow ejected from the jet port 42. In this way, the self-ejected flow can form an obstacle to the leakage jet at the tooth top gap by increasing the flow rate, and can also increase the leakage resistance of the leakage jet at the tooth top gap.

[0067] It should be noted that the above-mentioned inclination angle setting scheme of the jet channel 40 close to the jet port 42 is also applicable to the second gear teeth 31 of the driven gear 30 , and will not be described in detail here.

[0068] In some other embodiments, when the gear tooth rotates toward the high-pressure side (i.e., the pressure flow area 14), a jet port 42 is provided near the tooth top on the high-pressure side of the gear tooth, and an inlet port 41 is provided near the tooth root on the high-pressure side of the gear tooth.

[0069] For example, Figure 6 As shown, Figure 6 for Figure 1 Another partial enlarged schematic diagram of the first gear tooth 21 is shown in FIG. When the first gear tooth 21 rotates clockwise toward the high-pressure side, a jet port 42 is provided at a position near the tooth top on the high-pressure side of the first gear tooth 21. Correspondingly, an inlet port 41 is provided at a position near the tooth root on the high-pressure side of the first gear tooth 21.

[0070] Alternatively, taking the driven gear 30 as an example, when the second gear tooth 31 rotates counterclockwise toward the high-pressure side, a jet port 42 is provided near the tooth top on the high-pressure side of the second gear tooth 31. Correspondingly, an inlet port 41 is provided near the tooth root on the high-pressure side of the second gear tooth 31.

[0071] When the gear teeth rotate toward the high-pressure side, on the high-pressure side of the gear teeth, the roots of the first gear teeth 21 and the second gear teeth 31 first mesh, and then the tops of the first gear teeth 21 and the second gear teeth 31 mesh accordingly. In this way, in the process of the driving gear 20 driving the driven gear 30 to mesh and rotate so that the gear teeth rotate toward the high-pressure side, since the position of the gear teeth near the root of the gear teeth meshes first, the position of the gear teeth near the root of the gear teeth on the high-pressure side has a greater fluid pressure, so that part of the fluid flows into the jet channel 40 from the inlet 41 and ejects a self-ejecting flow from the jet port 42 near the top of the gear, so that a vortex is formed at the tooth top gap by the high-speed self-ejecting flow, which can also increase the leakage resistance at the tooth top gap.

[0072] It should be noted that, in the above embodiment, when the gear rotates toward the high-pressure side, the portion of the jet channel 40 near the jet port 42 is tilted toward the rotation direction of the gear, so that the self-ejecting jet can form a vortex with the leakage jet near the tooth tip clearance, which is beneficial to further increase the leakage resistance of the leakage jet through convection.

[0073] In the embodiment of the present application, a jet channel 40 may be provided at the first gear tooth 21 of the driving gear 20 alone to increase the leakage resistance at the tooth top clearance of the driving gear 20. Alternatively, a jet channel 40 may be provided at the second gear tooth 31 of the driven gear 30 alone to increase the leakage resistance at the tooth top clearance of the driven gear 30.

[0074] In addition, a jet channel 40 may be provided at the first gear teeth 21 of the driving gear 20 and at the second gear teeth 31 of the driven gear 30 to increase the leakage resistance at the tooth top gap of the driving gear 20 and the driven gear 30 at the same time.

[0075] In some embodiments, a jet channel 40 is disposed at at least some of the gear teeth of the driving gear 20 and the driven gear 30 .

[0076] For example, along the circumference of the driving gear 20, the jet channel 40 may be arranged at intervals of one or more first gear teeth 21. Along the circumference of the driven gear 30, the jet channel 40 may also be arranged at intervals of one or more second gear teeth 31. The structure is simple, and the production and processing of the gear pump 100 is convenient.

[0077] Or, if Figure 1 As shown, in the driving gear 20, each first gear tooth 21 is provided with one or more jet channels 40. In the driven gear 30, each second gear tooth 31 is provided with one or more jet channels. In the process that the driving gear 20 drives the driven gear 30 to rotate, the leakage resistance at each tooth top gap can be increased through the jet channel 40. Thereby reducing the flow velocity and leakage amount of the leakage jet, it is beneficial to improve the performance parameters such as the head and flow rate of the gear pump 100 and the operating efficiency. In some embodiments, a plurality of jet channels 40 are provided at a gear tooth, and at a corresponding gear tooth, the plurality of jet channels 40 are distributed at intervals along the axial direction of the gear tooth.

[0078] For example, Figure 7 As shown, Figure 7 for Figure 1 A partial enlarged schematic diagram of the radial direction of the first gear tooth 21 is shown in FIG. A plurality of jet channels 40 are provided at each first gear tooth 21 , and the plurality of jet channels 40 are spaced apart and distributed along the axial direction (ie, X direction) of the first gear tooth 21 (ie, the driving gear 20 ).

[0079] Correspondingly, a plurality of jet channels 40 are disposed at each second gear tooth 31 , and the plurality of jet channels 40 are distributed at intervals along the axial direction of the second gear tooth 31 (ie, the driven gear 30 ).

[0080] In this way, by arranging a plurality of jet channels 40 at intervals along the axial direction, a plurality of self-ejected jets ejected at the tooth top gap can be distributed along the axial direction to form a dense flow-blocking area along the axial direction of the tooth top gap, thereby enabling the tooth top gap to form an effective barrier to the leakage jet, thereby effectively reducing the flow velocity and leakage amount of the leakage jet at the tooth top gap, which is beneficial to improving the performance parameters such as the head and flow rate and the operating efficiency of the gear pump 100. Among them, the jet channel 40 is a smoothly extended curved structure or a broken line structure. For example, between two parts of the jet channel 40 of the straight structure, they can be connected and conducted by a smooth rounded structure. Thereby reducing the flow resistance of the fluid in the jet channel 40.

[0081] In some embodiments, in the same jet channel 40 , the opening area of ​​the jet port 42 is smaller than or equal to the opening area of ​​the inlet port 41 .

[0082] Exemplarily, in the same jet channel 40, the opening area of ​​the jet port 42 is equal to the opening area of ​​the inlet port 41. That is, the jet channel 40 can be set as a flow channel with a constant cross section, so that the fluid can maintain a stable flow rate in the jet channel 40, and the setting of the jet channel 40 is convenient.

[0083] Alternatively, in the same jet channel 40, the opening area of ​​the jet port 42 is set to be smaller than the opening area of ​​the inlet port 41. For example, the cross-sectional area of ​​the jet channel 40 may be reduced only at the jet port 42, or the cross-sectional area of ​​at least part of the jet channel 40 near the jet port 42 may be gradually reduced along the flow direction of the fluid. This allows the self-ejected jet ejected from the jet port 42 to have a higher jet velocity, which is beneficial to further increase the leakage resistance at the tooth tip clearance.

[0084] The cross-sectional shapes of the inlet 41 and the jet port 42 may be any shapes such as circle, triangle, rectangle, square, pentagon, hexagon, etc.

[0085] If the jet channel 40 is a flow channel with a constant cross section, that is, the cross-sectional shape and cross-sectional area of ​​the inlet 41 and the jet port 42 are the same.

[0086] If the jet channel 40 is a flow channel of non-uniform cross-section, that is, the cross-sectional shapes of the inlet 41 and the jet port 42 can be the same or different. Even if the cross-sectional shapes of the inlet 41 and the jet port 42 are the same, the cross-sectional area of ​​the jet port 42 can be set to be smaller than the cross-sectional area of ​​the inlet 41.

[0087] Exemplarily, the cross-sectional shapes of the inlet 41 and the jet port 42 are both set to be circular, that is, the cross-sectional shape of the jet channel 40 is circular, which is conducive to reducing the flow resistance of the fluid in the jet channel 40 and simplifying the processing steps of the jet channel 40 .

[0088] Take the case where the cross-sectional shapes of the inlet 41 and the jet port 42 are both circular holes as an example.

[0089] The diameter of the inlet 41 can be set to 0.2-5 mm. For example, the diameter of the inlet 41 can be 0.2 mm, 0.25 mm, 0.3 mm, 0.35 mm, 0.4 mm, 0.45 mm, 0.5 mm, 0.55 mm, 0.6 mm, 0.65 mm, 0.7 mm, 0.75 mm, 0.8 mm, 0.85 mm, 0.9 mm, 0.95 mm, 1.0 mm, 1.5 mm, 2.0 mm, 2.5 mm, 3.0 mm, 3.5 mm, 4.0 mm, 4.5 mm or 5.0 mm, etc.

[0090] The diameter of the jet port 42 is set to be 0.2-5 mm. For example, the diameter of the jet port 42 can be 0.2 mm, 0.25 mm, 0.3 mm, 0.35 mm, 0.4 mm, 0.45 mm, 0.5 mm, 0.55 mm, 0.6 mm, 0.65 mm, 0.7 mm, 0.75 mm, 0.8 mm, 0.85 mm, 0.9 mm, 0.95 mm, 1.0 mm, 1.5 mm, 2.0 mm, 2.5 mm, 3.0 mm, 3.5 mm, 4.0 mm, 4.5 mm or 5.0 mm.

[0091] Among them, the diameter size of the jet port 42 can be equal to the diameter size of the inlet port 41, or it can be slightly smaller than the diameter size of the inlet port 41. The diameter size of the inlet port 41 can be adapted and set according to the axial size of the driving gear 20 and the driven gear 30 and the width size of the gear teeth along the axial direction on the tooth top side. If the diameter size of the jet port 42 is less than 0.2mm, more jet channels 40 need to be arranged at intervals at the gear teeth along the axial direction, which greatly increases the complexity of the structure. If the diameter size of the jet port 42 is greater than 5mm, the structure of the gear teeth at the tooth top will be narrower along the circumferential direction, thereby reducing the structural strength of the gear teeth at the tooth top.

[0092] For example, the first gear teeth 21 and the second gear teeth 31 may be provided with 3-7 jet channels 40 along the axial direction. For example, the number of the jet channels 40 at each gear tooth may be three, four, five, six or seven.

[0093] Exemplarily, the first gear teeth 21 and the second gear teeth 31 are provided with five jet channels 40 spaced apart in the axial direction. While effectively reducing the leakage of the jet at the tooth tip clearance, it is avoided that more jet channels 40 greatly increase the complexity of the structure of the driving gear 20 and the driven gear 30, and it is beneficial to maintain the good structural strength of the driving gear 20 and the driven gear 30.

[0094] In some embodiments, at least the cross-sectional shape of the jet port 42 is rectangular. Figure 8 , Figure 8 for Figure 1 Another partial enlarged schematic diagram of the first gear tooth along the radial direction is shown in . The cross-sectional shape of the jet port 42 at the first gear tooth 21 is a rectangle.

[0095] The cross-sectional shape of the jet opening 42 at the second gear tooth 31 may also be set to be a rectangle.

[0096] If there are multiple jet channels 40, the cross-sectional shape of the jet port 42 can be rectangular or square, and the jet ports 42 of the multiple jet channels 40 are spaced apart along the axial direction. The jet ports 42 with rectangular or square structures can reduce the axial spacing area between two adjacent jet ports 42, so that the self-ejected jets ejected from the jet ports 42 cover more space areas of the tooth top gap along the axial direction, so as to effectively prevent the leakage flow at the tooth top gap.

[0097] If the number of the jet channel 40 is one, the length direction of the rectangular jet port 42 is parallel to the axial direction, so that the self-ejected jet ejected from the rectangular jet port 42 can occupy more tooth tip gap space along the axial direction to effectively prevent leakage at the tooth tip gap.

[0098] In some embodiments, since the inlet 41 is disposed close to the tooth root, the axis of the inlet 41 may be parallel to the tangent line at the inlet 41, or the inlet 41 may be disposed inclined toward the tooth top.

[0099] Alternatively, the inlet 41 may be arranged to be inclined toward the tooth root. In this case, in the jet channel 40, when the fluid flows from the inlet 41 to the jet port 42, the angle of change of the direction of the fluid in the jet channel 40 is minimal, which is conducive to making the self-ejected flow ejected from the jet port 42 have a higher ejection speed, thereby increasing the leakage resistance at the tooth top gap.

[0100] The technical features of the above-described embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the technical features in the above-described embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0101] The above-described embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be construed as limiting the scope of the patent application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the protection scope of the patent application shall be subject to the attached claims.

Claims

1. A gear pump, characterized in that: The gear pump comprises a pump body (10), a driving gear (20) and a driven gear (30); the driving gear (20) and the driven gear (30) are installed in the pump body (10) and meshingly connected, and are used to drive a fluid to flow in the pump body (10); At least one of the driving gear (20) and the driven gear (30) is provided with a jet channel (40) at the gear teeth; The jet channel (40) has an inlet (41) and a jet port (42) that are connected. When the gear tooth rotates toward the high-pressure side, the inlet (41) is arranged on the high-pressure side of the gear tooth, so that part of the fluid enters the jet channel (40) through the inlet (41) and is ejected from the jet port (42), thereby increasing the leakage resistance of the tooth top clearance.

2. The gear pump according to claim 1, characterized in that: The jet port (42) is arranged on the tooth top side of the gear tooth radially away from the axis.

3. The gear pump according to claim 2, characterized in that: When the gear tooth rotates towards the high-pressure side, the portion of the jet channel (40) close to the jet port (42) is arranged to be inclined towards the rotation direction of the gear tooth.

4. The gear pump according to claim 2, characterized in that: The axis of the jet channel (40) near the jet port (42) coincides with one of the radial lines of the gear tooth.

5. The gear pump according to claim 1, characterized in that: When the gear tooth rotates toward the high-pressure side, the jet port (42) is provided at a position close to the tooth top on the high-pressure side of the gear tooth, and the inlet port (41) is provided at a position close to the tooth root on the high-pressure side of the gear tooth.

6. The gear pump according to any one of claims 1 to 5, characterized in that A plurality of the jet channels (40) are provided at one gear tooth; At one of the gear teeth, a plurality of the jet channels (40) are distributed at intervals along the axial direction of the gear tooth.

7. The gear pump according to any one of claims 1 to 5, characterized in that In the same jet channel (40), the opening area of ​​the jet port (42) is smaller than or equal to the opening area of ​​the inlet port (41).

8. The gear pump according to any one of claims 1 to 5, characterized in that The cross-sectional shapes of the inlet (41) and the jet port (42) are circular; Alternatively, at least the cross-sectional shape of the jet port (42) is rectangular.

9. The gear pump according to any one of claims 1 to 5, characterized in that: The driving gear (20) and the driven gear (30) are external meshing structures; Alternatively, the gear pump further comprises a meniscus (50), the driving gear (20) is radially located inside the driven gear (30), the meniscus (50) is installed between the driving gear (20) and the driven gear (30), and the driving gear (20) and the driven gear (30) are in an internal meshing structure.

10. The gear pump according to claim 9, characterized in that The jet channel (40) is provided at at least a portion of the gear teeth of the driving gear (20) and the driven gear (30).

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