Gear pump device

Abstract

The invention discloses a gear pump device which comprises a pump shell, a pumping module and a flow guide plate module, the pumping module comprises a driving assembly and a pumping wheel assembly arranged in the pump shell, and a driving drainage flow channel is formed in gear teeth of at least one pumping gear in the pumping wheel assembly; a high-pressure inlet and a low-pressure outlet of the driving drainage flow channel are formed in the two opposite tooth faces of the gear teeth correspondingly, and the flow guide plate module is installed on the low-pressure side of the gear teeth and suitable for adjusting the distance between the pressure difference between the high-pressure inlet and the low-pressure outlet and the low-pressure side of the gear teeth. The jet flow flowing out of the low-pressure outlet flows towards the tooth top gap along the gap between the flow guide plate module and the low-pressure side of the gear tooth so that the leaked jet flow can be disturbed, and the distance between the flow guide plate module and the low-pressure side of the gear tooth is set to be suitable for the adjustable pressure difference between the high-pressure inlet and the low-pressure outlet. It can be ensured that the gap dynamically responds to pressure difference changes, and the purposes of reducing leakage jet flow of the tooth top gap and improving operation efficiency are achieved.

Description

Technical Field

[0001] This invention belongs to the field of hydraulic transmission technology, and particularly relates to a gear pump device. Background Technology

[0002] Gear pumps are rotary pumps that transport or pressurize liquids by changing and moving the working volume between the pump cylinder and meshing gears. When the gears rotate, the volume of the space on the disengaged side increases, creating a vacuum that draws in liquid. Conversely, the volume of the space on the meshing side decreases, forcing the liquid into the pipeline. The core advantages of gear pumps include: relatively simple structure, facilitating mass production and maintenance; continuous operation, making them particularly suitable for applications requiring high volumetric flow rates; and relatively low manufacturing and application costs, effectively lowering the barrier to entry for industrial systems. Based on these significant advantages, gear pumps have become key power components in many industrial fields and are widely used in engineering machinery, agricultural machinery, petrochemical pipelines, aerospace hydraulic systems, and other applications.

[0003] However, the high reliability of gear pumps is largely limited by a key design parameter: the tooth tip clearance (the tiny gap between the tooth tip of the gear and the pump body wall or a specially designed baffle / meniscus). The fundamental purpose of this clearance design is to minimize the mechanical friction resistance and wear generated when the gear contacts the wall surface during high-speed rotation, which is a necessary design compromise. This design also introduces potential problems that are difficult to avoid. Specifically, as the gear teeth continue to rotate and gradually move towards the high-pressure zone (discharge side), a significant fluid pressure gradient will form on both sides of the teeth. Under this high pressure difference, the high-pressure fluid on the discharge side will inevitably flow backwards to the low-pressure zone (suction side) through the inherent tooth tip clearance, forming a high-velocity leakage jet. This reverse high-energy leakage jet inevitably interacts strongly with the forward-flowing main transport fluid. This interaction is highly likely to induce instability at the fluid dynamics level, mainly manifested as high-shear layer separation and violent turbulent mixing processes. The consequence is the generation of an extremely complex three-dimensional vortex structure inside the pump chamber. These disordered eddies dissipate a large amount of fluid kinetic energy, causing the energy that should have been effectively used for fluid transport to be dispersed and attenuated, ultimately leading to a significant decrease in the operating efficiency of the gear pump. Summary of the Invention

[0004] In view of the above-mentioned defects or deficiencies, the present invention provides a gear pump device, which aims to solve the technical problem that the operating efficiency of meshing gear pumps is significantly reduced due to leakage jets caused by tooth tip clearance.

[0005] To achieve the above objectives, the present invention provides a gear pump device, wherein the gear pump device includes a pump housing, a pumping module, and a guide vane module; the pumping module includes a drive assembly and a pumping wheel assembly disposed within the pump housing, the drive assembly being drivenly connected to the pumping wheel assembly and used to drive the pumping wheel assembly to rotate, and at least one pumping gear in the pumping wheel assembly having an active drainage channel formed on its teeth, the high-pressure inlet and low-pressure outlet of the active drainage channel being respectively disposed on two opposing tooth surfaces; the guide vane module is installed on the low-pressure side of the tooth and covers the low-pressure outlet, the guide vane module being used to adapt to the pressure difference adjustment between the high-pressure inlet and the low-pressure outlet and the spacing of the low-pressure side of the tooth.

[0006] In one embodiment of the present invention, the guide vane module is elastically reset and mounted on the low-pressure side of the gear teeth so as to adapt to the pressure difference between the high-pressure inlet and the low-pressure outlet through elastic deformation.

[0007] In one embodiment of the present invention, the deflector module includes a movable mounting body, a first deflector body, and a first elastic reset member. The movable mounting body is movably mounted on the gear tooth and located on the side of the low-pressure outlet away from the tip of the gear tooth. The first deflector body is connected to the movable mounting body and covers the low-pressure outlet. The first elastic reset member is mounted on the gear and connected to the movable mounting body or the first deflector body. The first elastic reset member is used to elastically support the first deflector body close to the gear tooth in the reset state, and to elastically deform when the movable mounting body drives the first deflector body to move away from the gear tooth.

[0008] In one embodiment of the present invention, the movable mounting body includes a mounting shaft, and the gear teeth have a shaft groove on the side of the low-pressure outlet away from the tooth tip, and the mounting shaft is rotatably mounted in the shaft groove.

[0009] In one embodiment of the present invention, the gear teeth are provided with a first limiting groove on the side of the shaft groove away from the low pressure outlet. The first limiting groove has an abutting sidewall facing the shaft groove. The first elastic reset member is an elastic sheet. The elastic sheet is located on the side of the mounting shaft away from the first guide plate body. One end of the elastic sheet is connected to the part of the mounting shaft that extends out of the first limiting groove, and the other end away from the mounting shaft is elastically pressed against the abutting sidewall.

[0010] In one embodiment of the present invention, the mounting shaft includes a shaft body and a connecting part connected to the shaft body. The shaft groove includes an inner cavity and an opening arranged sequentially along the thickness direction of the gear teeth. The inner cavity is for the shaft body to be rotatably mounted, and the opening is for the connecting part to extend out. The diameter of the opening is smaller than the diameter of the shaft body. A first guide plate and an elastic sheet are respectively arranged on opposite sides of the connecting part, and a first limiting groove is provided on the flat sidewall of the opening.

[0011] In one embodiment of the present invention, the guide plate module further includes a limiting block, which is connected to the side of the first guide plate body facing the gear teeth and located between the mounting shaft and the low-pressure outlet. The limiting block is configured to abut against the gear teeth in the reset state, so that an initial gap is formed between the first guide plate body located outside the second limiting groove and the gear teeth.

[0012] In one embodiment of the present invention, a second limiting groove is also provided on the gear tooth. The second limiting groove is located on the side of the shaft groove away from the first elastic reset member. A low-pressure outlet is opened on the bottom wall of the second limiting groove, and the bottom wall of the second limiting groove is bidirectionally through-type along the height direction of the gear tooth. The limiting block can extend into the second limiting groove and abut against the bottom wall of the second limiting groove in the reset state, so that an initial gap is formed between the first guide plate and the bottom wall of the second limiting groove.

[0013] In one embodiment of the present invention, the guide plate module includes a second guide plate body and a second elastic reset member. The second guide plate body is located on the low-pressure side of the gear tooth and covers the low-pressure outlet. The second elastic reset member is placed in the active venting channel and drivenly connected to the second guide plate body. The second elastic reset member is used to support the second guide plate body close to the gear tooth in the reset state, and to enter the elastic deformation state when the second guide plate body moves away from the gear tooth.

[0014] In one embodiment of the present invention, the guide plate module further includes a drive seat, and the second elastic reset member is connected to the second guide plate body through the drive seat.

[0015] In one embodiment of the present invention, the guide plate module includes a third guide plate body, the third guide plate body having an elastic portion covering the low-pressure outlet, the elastic portion adjusting the distance between itself and the low-pressure side of the gear teeth by elastic deformation.

[0016] In one embodiment of the present invention, the pump housing is divided into a driving chamber and a pumping chamber. The driving assembly includes a driving motor, a driving gear, and a driven gear. The driving gear and the driven gear are placed in the driving chamber and are configured to mesh with each other. The driving motor is drivenly connected to the driving gear. The pumping wheel assembly is placed in the pumping chamber and includes two pumping gears. The two pumping gears are coaxially connected to the driving gear and the driven gear respectively. The two pumping gears are configured to mesh with each other, and the contact stress between the two pumping gears is set to be less than the contact stress between the driving gear and the driven gear.

[0017] In one embodiment of the present invention, the pump housing includes an intermediate pump housing, a first end cover, and a second end cover. The intermediate pump housing has an open drive chamber and a pumping chamber on opposite sides. The first end cover and the second end cover respectively cover the drive chamber and the pumping chamber, and are both sealed and detachably connected to the intermediate pump housing. The intermediate pump housing is also provided with an oil inlet pipe and an oil outlet pipe, both of which are connected to the pumping chamber. The oil inlet pipe and the oil outlet pipe are respectively provided with the oil suction side and the oil pressure side in the pumping chamber.

[0018] Through the above technical solution, the gear pump device provided by the present invention has the following beneficial effects: When using the aforementioned gear pump device, which includes a pump housing, a pumping module, and a guide vane module, the driving component in the pumping module drives the pumping wheel assembly to rotate. At least one pumping gear in the pumping wheel assembly has an active drainage channel on its teeth. The high-pressure inlet and low-pressure outlet of the active drainage channel are located on two opposing tooth surfaces. The guide vane module is installed on the low-pressure side of the tooth and covers the low-pressure outlet. The guide vane module is suitable for adjusting the pressure difference between the high-pressure inlet and the low-pressure outlet and the distance between the high-pressure side of the tooth. Therefore, when the gear pump device is working, the rotation of the pumping wheel assembly creates a pressure difference on both sides of the pumping gear teeth. The fluid on the high-pressure side of the tooth will flow from the high-pressure side... The inlet enters the active venting channel and applies pressure to the guide plate module. The guide plate module is designed to adjust the distance between itself and the low-pressure side of the gear teeth according to the pressure difference between the two sides. This allows the jet flowing out from the low-pressure outlet to flow along the gap between the guide plate module and the low-pressure side of the gear teeth toward the tooth tip gap. This disturbs the leakage jet at the tooth tip gap, increasing the flow damping of the leakage jet at the tooth tip gap. At the same time, setting the distance between the guide plate module and the low-pressure side of the gear teeth to be adjustable for the pressure difference between the high-pressure inlet and the low-pressure outlet ensures that the gap dynamically responds to pressure difference changes, avoiding the limitations of a fixed gap. Ultimately, this achieves the goal of reducing reverse leakage jet at the tooth tip gap and improving operating efficiency.

[0019] Other features and advantages of the present invention will be described in detail in the following detailed description section. Attached Figure Description

[0020] The accompanying drawings are provided to further illustrate embodiments of the present invention and form part of the specification. They are used together with the following detailed description to explain the embodiments of the present invention, but do not constitute a limitation thereof. Those skilled in the art can obtain other drawings based on the structures shown in these drawings without any inventive effort. In the drawings: Figure 1 This is a schematic diagram of the disassembled structure of a gear pump device according to an embodiment of the present invention; Figure 2This is a schematic diagram of the guide vane module in a reset state on the gear teeth according to the first embodiment of the present invention; Figure 3 This is a schematic diagram of the gear teeth according to the first embodiment of the present invention; Figure 4 This is a schematic diagram of the flow guide plate module according to the first embodiment of the present invention from one perspective. Figure 5 This is a structural schematic diagram of the guide vane module according to the first embodiment of the present invention from another perspective; Figure 6 This is a schematic diagram of the guide vane module in a reset state on the gear teeth according to the third embodiment of the present invention; Figure 7 This is a schematic diagram of the guide vane module in a reset state on the gear teeth according to the fourth embodiment of the present invention; Figure 8 This is a schematic diagram of a pumping wheel assembly placed in a pump housing according to an embodiment of the present invention.

[0021] Explanation of reference numerals in the attached figures: Detailed Implementation

[0022] The specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are for illustration and explanation only and are not intended to limit the present invention.

[0023] Existing gear pumps generally suffer from efficiency reduction due to "passive leakage." This means that a significant fluid pressure gradient difference is formed on both sides of the gear teeth. Under the action of this fluid pressure gradient difference, the high-pressure fluid on the discharge side will inevitably flow backward to the low-pressure area through the inherent tooth tip gap, forming a high-velocity leakage jet. The leakage jet interacts strongly with the mainstream fluid flowing in the forward direction. This interaction causes the energy that should be effectively used for fluid transport to be needlessly dispersed and attenuated, ultimately leading to a decrease in efficiency.

[0024] To address the problems caused by "passive leakage," some gear pumps incorporate jet channels at the teeth of the driving and driven gears. These jet channels include an inlet located near the tooth root on the high-pressure side and a jet outlet located at the tooth tip, allowing high-pressure fluid to be introduced through the inlet and ejected from the jet outlet to form a self-excited jet. The self-excited jet interacts with the leakage jet passing through the tooth tip gap, creating a convective vortex system. This significantly increases the flow resistance of the leaking fluid, thereby improving the volumetric efficiency of the gear pump.

[0025] However, the structural design of this jet channel still suffers from limited dynamic adaptability. Specifically, this design is only optimized for specific operating conditions. When changes in gear pump speed cause nonlinear fluctuations in leakage flow, this structure cannot achieve effective dynamic adjustment. Increased pressure gradients caused by increased gear pump speed or load changes will exacerbate leakage jets and further worsen the sealing effect.

[0026] Therefore, the present invention provides a gear pump device to solve the above-mentioned problems. The gear pump device of the present invention will now be described with reference to the accompanying drawings.

[0027] like Figure 1 , Figure 2 and Figure 6 As shown, the present invention provides a gear pump device, wherein the gear pump device includes: Pump housing 100; The pumping module includes a drive assembly 200 and a pumping wheel assembly 300 placed inside the pump housing 100. The drive assembly 200 is drivenly connected to the pumping wheel assembly 300 and is used to drive the pumping wheel assembly 300 to rotate. At least one pumping gear 310 in the pumping wheel assembly 300 has an active drainage channel 320 on its teeth. The high pressure inlet 321 and the low pressure outlet 322 of the active drainage channel 320 are respectively located on two tooth surfaces that are opposite to each other. A deflector module 400 is installed on the low-pressure side of the gear teeth and covers the low-pressure outlet 322. The deflector module 400 is used to adjust the pressure difference between the high-pressure inlet 321 and the low-pressure outlet 322 and the spacing between the low-pressure side of the gear teeth.

[0028] When the gear pump device described above is used, since it includes a pump housing 100, a pumping module, and a guide plate module 400, the drive component 200 in the pumping module is used to drive the pumping wheel assembly 300 to rotate, and at least one pumping gear 310 in the pumping wheel assembly 300 has an active drainage channel 320 on its teeth. The high-pressure inlet 321 and low-pressure outlet 322 of the active drainage channel 320 are respectively located on two opposing tooth surfaces. The guide plate module 400 is installed on the low-pressure side of the tooth and covers the low-pressure outlet 322. The guide plate module 400 is suitable for adjusting the pressure difference between the high-pressure inlet 321 and the low-pressure outlet 322 and the distance between the high-pressure side of the tooth. When the gear pump device is working, the rotation of the pumping wheel assembly 300 causes a pressure difference on both sides of the teeth of the pumping gear 310. Fluid enters the active venting channel 320 from the high-pressure inlet 321 and is pressurized onto the guide plate module 400. The guide plate module 400 is configured to adjust the distance between itself and the low-pressure side of the gear teeth according to the pressure difference between the two sides. This allows the jet flowing out from the low-pressure outlet 322 to flow along the gap between the guide plate module 400 and the low-pressure side of the gear teeth towards the tooth tip gap, thereby disturbing the leakage jet at the tooth tip gap and increasing the flow damping of the leakage jet at the tooth tip gap. Simultaneously, setting the distance between the guide plate module 400 and the low-pressure side of the gear teeth to be adjustable for the pressure difference between the high-pressure inlet and the low-pressure outlet ensures that the gap between the guide plate module 400 and the low-pressure side of the gear teeth dynamically responds to pressure difference changes, avoiding the limitations of a fixed gap. Ultimately, this achieves the goal of reducing reverse leakage jet at the tooth tip gap and improving operating efficiency. It should be noted that this invention is mainly described using an external gear pump as an example; however, if an internal gear pump uses the technical solution of this invention, it should fall within the protection scope of this invention.

[0029] Specifically, the leakage jet A formed by the inherent tooth tip gap is a passive leakage, while the jet B formed by the active leakage channel 320 and the guide plate module 400 in this invention is an active leakage compensation, which can suppress the formation of leakage jet at the tooth tip gap from the source.

[0030] In one embodiment of the present invention, the guide vane module 400 is elastically and restorably mounted on the low-pressure side of the gear teeth to adapt to the pressure difference between the high-pressure inlet 321 and the low-pressure outlet 322 through elastic deformation. Specifically, the guide vane module 400 has an elastic function, and the guide vane module 400 can achieve force balance under the action of hydraulic pressure difference and the elastic force provided by the elastic part. As the hydraulic pressure difference changes, the distance between the guide vane module and the low-pressure side of the gear teeth changes accordingly, and the elastic force provided by the elastic part changes accordingly. This dynamic adjustment structure can ensure stability and reliability. Of course, the present invention is not limited to this. The guide vane module 400 may also be equipped with an electrically controlled distance between the low-pressure side of the gear teeth, specifically by detecting the pressure difference between the high-pressure inlet 321 and the low-pressure outlet 322 through a pressure sensor, and controlling the guide vane module 400 to adjust the distance between itself and the low-pressure side of the gear teeth according to the detected pressure difference.

[0031] See Figures 1 to 5In the first and second embodiments of the present invention, the guide plate module 400 includes a movable mounting body, a first guide plate body 420, and a first elastic reset member 430. The movable mounting body is movably mounted on the gear teeth and located on the side of the low-pressure outlet 322 away from the tooth tip. The first guide plate body 420 is connected to the movable mounting body and covers the low-pressure outlet 322. The first elastic reset member 430 is mounted on the gear teeth and connected to the movable mounting body or the first guide plate body 420. Specifically, when the first elastic reset member 430 is connected to the movable mounting body, it can be that the first elastic reset member 430 and the first guide plate body 420 are respectively disposed on the radial sides of the movable mounting body as in the first embodiment, or the first elastic reset member can be a torsion spring connected to the movable mounting body (e.g., mounting shaft 410). The first elastic reset member 430 is used to elastically support the first guide plate body 420 close to the gear teeth in the reset state, and to elastically deform when the movable mounting body drives the first guide plate body 420 to move away from the gear teeth. The stability of the first guide plate 420 in both the reset and deformed states is ensured by the movable mounting body on the gear teeth and the elastic support of the first elastic reset member 430 on the movable mounting body. Specifically, when the system pressure increases, the fluid entering the active venting channel 320 from the high-pressure inlet 321 will pressurize the first guide plate 420, causing the movable mounting body to move the first guide plate 420 away from the low-pressure outlet 322 and increase the gap between the first guide plate 420 and the low-pressure side of the gear teeth. At this time, the first elastic reset member 430 undergoes elastic deformation to accumulate the elastic potential energy required for reset. When the system pressure decreases, the pressure on the first guide plate 420 decreases, and the elastic potential energy accumulated by the first elastic reset member 430 can drive the movable mounting body and the first guide plate 420 to move in the reset direction until they reach the reset position. At this time, the first elastic reset member 430 enters the reset state and can stably support the movable mounting body and the first guide plate 420 in the reset position.

[0032] In the first and second embodiments of the present invention, the movable mounting body includes a mounting shaft 410. A shaft groove 330 is provided on the side of the low-pressure outlet 322 away from the tooth tip. The mounting shaft 410 is rotatably mounted within the shaft groove 330. By setting the movable mounting body as the mounting shaft 410, the movable mounting body is rotatably mounted on the tooth. A small rotation angle can achieve a large adjustment of the gap between the first guide plate 420 and the low-pressure side of the tooth. Furthermore, the depth of the shaft groove 330 is independent of the gap adjustment. This movable mounting structure is easy to manufacture and helps ensure the structural strength of the tooth. Of course, the present invention is not limited to this. The movable mounting body can also be a slider. The tooth has a groove on the low-pressure side that mates with the slider. The slider is slidably mounted within the groove to achieve the movable mounting of the movable mounting block on the tooth.

[0033] In the first embodiment of the present invention, a first limiting groove 340 is provided on the side of the shaft groove 330 away from the low-pressure outlet 322. The first limiting groove 340 has an abutting sidewall facing the shaft groove 330. The first elastic reset member 430 is an elastic sheet, preferably a metal sheet. The elastic sheet is located on the side of the mounting shaft 410 away from the first guide plate body 420. One end of the elastic sheet is connected to the part of the mounting shaft 410 that extends out of the first limiting groove 340, and the other end away from the mounting shaft 410 is elastically pressed against the abutting sidewall. Making the first elastic reset member 430 an integral elastic sheet can ensure stability within the pump housing 100 and facilitate connection with the mounting shaft 410 and installation on the gear teeth. The structure is simple and effective. Specifically, when fluid is applied to the first guide plate body 420, causing the mounting shaft 410 to rotate the first guide plate body 420 away from the low-pressure outlet 322, the elastic sheet undergoes continued compression elastic deformation and accumulates elastic potential energy. In addition, the mounting shaft 410 can be a metal column, and the first guide plate 420 can be a metal plate with a thickness greater than that of the elastic sheet. Neither the mounting shaft 410 nor the first guide plate 420 has an elastic function. One end of the elastic sheet can be connected to the mounting shaft 410 by welding. Of course, the mounting shaft 410 and the first guide plate 420 can also be made of other rigid components.

[0034] Furthermore, in the second embodiment of the present invention, the first elastic reset member 430 may also be configured as a spring member. The spring member and the low-pressure outlet 322 are both located on the same side of the movable mounting body, and the two ends of the spring member are respectively connected to the low-pressure side of the gear teeth and the first guide plate body 420.

[0035] See Figures 2 to 5In the first embodiment of the present invention, the mounting shaft 410 includes a shaft body portion 411 and a connecting portion 412 connected to the shaft body portion 411. The shaft groove 330 includes an inner cavity portion 331 and an opening portion 332 arranged sequentially along the thickness direction of the gear teeth. The inner cavity portion 331 is for the shaft body portion 411 to be rotatably mounted, and the opening portion 332 is for the connecting portion 412 to extend out. The diameter of the opening portion 332 is smaller than the diameter of the shaft body portion 411, thereby ensuring the stable installation of the mounting shaft 410 in the shaft groove 330. Specifically, the shaft groove 330 is bidirectionally arranged along the length direction of the gear teeth so that the mounting shaft 410 can be aligned and inserted from the end of the shaft groove 330. Meanwhile, the first guide plate 420 and the elastic sheet are respectively disposed on opposite sides of the connecting portion 412, and the first limiting groove 340 is disposed on the flat sidewall of the opening portion 332. By constructing the inner wall of the opening portion 332 as a flat sidewall, sufficient thickness is provided to facilitate the setting of the first limiting groove 340. Specifically, the length of the first limiting groove 340 is less than the length of the shaft groove 330, and it is centrally disposed in the length direction of the gear teeth. In addition to having an abutting sidewall facing the shaft groove 330, the first limiting groove 340 also has an abutting bottom wall and two limiting sidewalls, which are disposed on opposite sides of the abutting sidewall. Of course, the present invention is not limited to this, and the first limiting groove 340 may not be disposed on the shaft groove 330 structure.

[0036] In the first embodiment of the present invention, the guide plate module 400 further includes a limiting block 440. The limiting block 440 is connected to the side of the first guide plate body 420 facing the gear teeth and is located between the mounting shaft 410 and the low-pressure outlet 322. The limiting block 440 is configured to abut against the gear teeth in the reset state, so that an initial gap is formed between the first guide plate body 420 and the gear teeth. That is, the limiting block 440 can limit the first guide plate body 420 in the reset rotation direction by abutting against the gear teeth, and an initial gap is formed in the reset state, so that overload will not occur under high pressure conditions.

[0037] In the first embodiment of the present invention, a second limiting groove 350 is also provided on the gear tooth. The second limiting groove 350 is located on the side of the shaft groove 330 away from the first elastic reset member 430. A low-pressure outlet 322 is opened on the bottom wall of the second limiting groove 350, and the bottom wall of the second limiting groove 350 is bidirectionally through-type along the height direction of the gear tooth. Specifically, one end of the second limiting groove 350 passes through the top of the gear tooth, and the other end passes through the shaft groove 330. The limiting block 440 can extend into the second limiting groove 350 and abut against the bottom wall of the second limiting groove 350 in the reset state, so that an initial gap is formed between the first guide plate 420 located outside the second limiting groove 350 and the bottom wall of the second limiting groove 350. Through the construction of the second limiting groove 350, the existence of the initial gap is ensured in the reset state, and the first guide plate 420 is positioned closer to the gear tooth.

[0038] See Figure 6 In the third embodiment of the present invention, the guide plate module 400 includes a second guide plate body 450 and a second elastic reset member 460. The second guide plate body 450 is located on the low-pressure side of the gear tooth and covers the low-pressure outlet 322. The second elastic reset member 460 is placed in the active venting channel 320 and drivenly connected to the second guide plate body 450. The second elastic reset member 460 is used to support the second guide plate body 450 close to the gear tooth in the reset state, and to enter the elastic deformation state when the second guide plate body 450 moves away from the gear tooth. By placing the second elastic reset member 460 in the active venting channel 320, the second guide plate body 450 can be aligned with the low-pressure outlet 322, and the energy storage movement and reset movement of the second elastic reset member 460 can be guided, thereby ensuring the stability of the movement of the second guide plate body 450. Specifically, the second elastic reset member 460 includes, but is not limited to, a compression spring. The first end of the second elastic reset member 460 can be placed inside the active venting channel 320 or can extend out from the high pressure inlet 321. The present invention does not limit this. The first end of the second elastic reset member 460 is configured to be connected to the gear teeth, and the second end is configured to be connected to the second guide plate body 450.

[0039] In a third embodiment of the present invention, the guide plate module 400 further includes a drive seat 470, and the second elastic reset member 460 is connected to the second guide plate body 450 through the drive seat 470. Compared with the direct connection between the second elastic reset member 460 and the second guide plate body 450, establishing a connection through the drive seat 470 can significantly improve the stability of the movement. Specifically, one end of the drive seat 470 is connected to the second guide plate body 450, and the other end passes through the second elastic reset member 460. Furthermore, the outer peripheral wall of the drive seat 470 can be circumferentially connected to the second elastic reset member 460, and the end face of the drive seat 470 can be connected to the second guide plate body 450.

[0040] Understandably, when the system pressure increases, the fluid entering the active venting channel 320 from the high-pressure inlet 321 will pressurize the drive seat 470, causing the drive seat 470 to push the second guide plate 450 away from the low-pressure outlet 322 and increase the gap between the second guide plate 450 and the low-pressure side of the gear teeth. At this time, the second elastic reset member 460 undergoes tensile elastic deformation and enters a tensile energy storage state to accumulate the elastic potential energy required for reset. When the system pressure decreases, the pressure on the drive seat 470 decreases, and the elastic potential energy accumulated by the second elastic reset member 460 in the energy storage state can drive the drive seat 470 to move the second guide plate 450 in the reset direction until it reaches the reset position. At this time, the second elastic reset member 460 enters the reset state and can stably support the drive seat 470 and the second guide plate 450 in the reset position.

[0041] See Figure 7 In the fourth embodiment of the present invention, the guide plate module 400 includes a third guide plate body 480, which has an elastic portion 490 covering the low-pressure outlet 322. The elastic portion 490 adjusts the distance between itself and the low-pressure side of the gear teeth through elastic deformation. The portion of the third guide plate body 480 covering the low-pressure outlet 322 can be directly designated as the elastic portion 490. The elastic portion 490 is made of an elastic material, so that when pressure is applied, the elastic portion 490 deforms away from the gear teeth, and when the pressure decreases, the elastic portion 490 returns to its original shape. It should be noted that the third guide plate body 480 can be either a portion covering the low-pressure outlet 322 that is designated as the elastic portion 490, or the entire third guide plate body 480 can be designated as an elastic plate.

[0042] See Figure 1 and Figure 8 In one embodiment of the present invention, the pump housing 100 is divided into a drive chamber and a pumping chamber 111. The drive assembly 200 includes a drive motor 210, a drive gear 220, and a driven gear 230. The drive gear 220 and the driven gear 230 are placed in the drive chamber and are configured for meshing transmission. The drive motor 210 is drivenly connected to the drive gear 220. The pumping wheel assembly 300 is placed in the pumping chamber 111 and includes two pumping gears 310. The two pumping gears 310 are coaxially connected to the drive gear 220 and the driven gear 230 respectively, and the two pumping gears 310 are configured for meshing contact. The contact stress between the two pumping gears 310 is set to be less than the contact stress between the drive gear 220 and the driven gear 230. This physically isolates the power transmission area from the fluid working area, and the two pumping gears 310 only need to ensure fluid operation without considering power transmission, thereby avoiding wear on the tooth surfaces of the two pumping gears 310 due to excessive contact stress. Of course, the present invention is not limited to this. The drive component 200 is only configured as a drive motor 210, and one of the two pumping gears 310 is driven and connected to the drive motor 210. It is also possible for the two pumping gears 310 to be configured as meshing transmission.

[0043] In one embodiment of the present invention, the pump housing 100 includes an intermediate pump housing 110, a first end cover 120, and a second end cover 130. The intermediate pump housing 110 has an open drive chamber and a pumping chamber 111 on opposite sides. The first end cover 120 and the second end cover 130 respectively seal the drive chamber and the pumping chamber 111, and are both detachably connected to the intermediate pump housing 110 in a sealed manner. This facilitates disassembly and replacement, and by integrating the drive chamber and the pumping chamber 111 on the intermediate pump housing 110, it reduces manufacturing costs and improves installation reliability. Furthermore, the intermediate pump housing 110 also has an inlet pipe section 112 and an outlet pipe section 113, both communicating with the pumping chamber 111. The inlet pipe section 112 and the outlet pipe section 113 are respectively provided corresponding to the oil suction side and the oil pressure side in the pumping chamber 111. The addition of the inlet pipe section 112 and the outlet pipe section 113 facilitates connection with upstream and downstream oil pipes.

[0044] In the description of this invention, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0045] 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.

[0046] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present 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.

[0047] 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. A gear pump device, characterized in that, include: Pump housing (100); The pumping module includes a drive assembly (200) and a pumping wheel assembly (300) disposed in the pump housing (100). The drive assembly (200) is drivenly connected to the pumping wheel assembly (300) and is used to drive the pumping wheel assembly (300) to rotate. At least one pumping gear (310) in the pumping wheel assembly (300) has an active drainage channel (320) on its teeth. The high-pressure inlet (321) and low-pressure outlet (322) of the active drainage channel (320) are respectively disposed on two tooth surfaces opposite to each other. A deflector module (400) is installed on the low-pressure side of the gear teeth and covers the low-pressure outlet (322). The deflector module (400) is used to adjust the pressure difference between the high-pressure inlet (321) and the low-pressure outlet (322) and the distance between the deflector module and the low-pressure side of the gear teeth.

2. The gear pump device according to claim 1, characterized in that, The guide vane module (400) is elastically reset and mounted on the low-pressure side of the gear teeth to adapt to the pressure difference between the high-pressure inlet (321) and the low-pressure outlet (322) through elastic deformation.

3. The gear pump device according to claim 2, characterized in that, The guide plate module (400) includes a movable mounting body, a first guide plate body (420), and a first elastic reset member (430). The movable mounting body is movably mounted on the gear tooth and located on the side of the low-pressure outlet (322) away from the tooth tip. The first guide plate body (420) is connected to the movable mounting body and covers the low-pressure outlet (322). The first elastic reset member (430) is mounted on the gear tooth and connected to the movable mounting body or the first guide plate body (420). The first elastic reset member (430) is used to elastically support the first guide plate body (420) close to the gear tooth in the reset state, and to elastically deform when the movable mounting body drives the first guide plate body (420) to move away from the gear tooth.

4. The gear pump device according to claim 3, characterized in that, The movable mounting body includes a mounting shaft (410), and the gear teeth are provided with a shaft groove (330) on the side of the low-pressure outlet (322) away from the tooth tip. The mounting shaft (410) is rotatably mounted in the shaft groove (330).

5. The gear pump device according to claim 4, characterized in that, The gear teeth are provided with a first limiting groove (340) on the side of the shaft groove (330) away from the low pressure outlet (322). The first limiting groove (340) has an abutting sidewall facing the shaft groove (330). The first elastic reset member (430) is an elastic sheet. The elastic sheet is located on the side of the mounting shaft (410) away from the first guide plate body (420). One end of the elastic sheet is connected to the part of the mounting shaft (410) that extends out of the first limiting groove (340), and the other end away from the mounting shaft (410) is elastically pressed against the abutting sidewall.

6. The gear pump device according to claim 5, characterized in that, The mounting shaft (410) includes a shaft body (411) and a connecting part (412) connected to the shaft body (411). The shaft groove (330) includes an inner cavity (331) and an opening (332) arranged sequentially along the thickness direction of the gear teeth. The inner cavity (331) is for the shaft body (411) to be rotatably mounted. The opening (332) is for the connecting part (412) to extend out. The diameter of the opening (332) is smaller than the diameter of the shaft body (411). The first guide plate (420) and the elastic sheet are respectively disposed on opposite sides of the connecting part (412), and the first limiting groove (340) is disposed on the straight sidewall of the opening (332).

7. The gear pump device according to claim 4, characterized in that, The guide plate module (400) further includes a limiting block (440), which is connected to the side of the first guide plate body (420) facing the gear teeth and located between the mounting shaft (410) and the low-pressure outlet (322). The limiting block (440) is configured to abut against the gear teeth in the reset state, so that an initial gap is formed between the first guide plate body (420) and the gear teeth.

8. The gear pump device according to claim 7, characterized in that, The gear tooth is also provided with a second limiting groove (350), which is located on the side of the shaft groove (330) away from the first elastic reset member (430). The bottom wall of the second limiting groove (350) is provided with the low pressure outlet (322), and the bottom wall of the second limiting groove (350) is bidirectionally through the height direction of the gear tooth. The limiting block (440) can extend into the second limiting groove (350) and abut against the bottom wall of the second limiting groove (350) in the reset state, so that the first guide plate body (420) located outside the second limiting groove (350) and the bottom wall of the second limiting groove (350) form the initial gap.

9. The gear pump device according to claim 2, characterized in that, The guide plate module (400) includes a second guide plate body (450) and a second elastic reset member (460). The second guide plate body (450) is located on the low-pressure side of the gear tooth and covers the low-pressure outlet (322). The second elastic reset member (460) is placed in the active venting channel (320) and drivenly connected to the second guide plate body (450). The second elastic reset member (460) is used to support the second guide plate body (450) close to the gear tooth in the reset state, and to enter an elastic deformation state when the second guide plate body (450) moves away from the gear tooth.

10. The gear pump device according to claim 9, characterized in that, The guide plate module (400) also includes a drive base (470), and the second elastic reset member (460) is driven to be connected to the second guide plate body (450) through the drive base (470).

11. The gear pump device according to claim 2, characterized in that, The guide plate module (400) includes a third guide plate body (480), which has an elastic portion (490) covering the low-pressure outlet (322). The elastic portion (490) adjusts the distance between itself and the low-pressure side of the gear teeth by elastic deformation.

12. The gear pump device according to any one of claims 1 to 11, characterized in that, The pump housing (100) is divided into a drive chamber and a pumping chamber (111). The drive assembly (200) includes a drive motor (210), a drive gear (220), and a driven gear (230). The drive gear (220) and the driven gear (230) are placed in the drive chamber and are meshed. The drive motor (210) is driven by the drive gear (220). The pumping wheel assembly (300) is placed in the pumping chamber (111) and includes two pumping gears (310). The two pumping gears (310) are coaxially connected to the drive gear (220) and the driven gear (230) respectively, and the two pumping gears (310) are meshed.

13. The gear pump device according to claim 12, characterized in that, The pump housing (100) includes an intermediate pump housing (110), a first end cap (120), and a second end cap (130). The intermediate pump housing (110) has an open drive chamber and a pumping chamber (111) on opposite sides. The first end cap (120) and the second end cap (130) respectively cover the drive chamber and the pumping chamber (111) and are both sealed and detachably connected to the intermediate pump housing (110). The intermediate pump housing (110) is also provided with an oil inlet pipe (112) and an oil outlet pipe (113) that are both connected to the pumping chamber (111). The oil inlet pipe (112) and the oil outlet pipe (113) are respectively provided with the oil suction side and the oil pressure side in the pumping chamber (111).

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