Fluid conveying device and equipment

Abstract

The utility model relates to the technical field of fluid conveying, in particular to a fluid conveying device and equipment. The fluid conveying device comprises a pump shell, a rotor assembly, a first cavity and a second cavity. The pump shell is provided with a first through hole and a second through hole. The rotor assembly is arranged in the pump shell, and the rotor assembly is configured to drive fluid in the pump shell to flow from the first through hole to the second through hole when rotating forwards; during reverse rotation, fluid in the pump shell is driven to flow from the second through hole to the first through hole; the first cavity communicates with the first through hole and is provided with a first inlet and a first outlet, the first inlet is provided with a first one-way valve, and the first outlet is provided with a second one-way valve; the second cavity communicates with the second through hole and is provided with a second inlet and a second outlet, the second inlet is provided with a third one-way valve, and the second outlet is provided with a fourth one-way valve; the fluid conveying device is simple in structure, capable of rotating forwards and backwards and capable of keeping the fluid output direction constant.

Description

Technical Field

[0001] This utility model relates to the field of fluid transport technology, specifically to a fluid transport device and equipment. Background Technology

[0002] In the context of current oil pump technology, traditional mechanical oil pumps have significant drawbacks. Their unidirectional oil supply characteristic makes it impossible to maintain stable operation of the hydraulic system when the transmission output reverses (e.g., in reverse gear) or the motor reverses. Since they can only effectively supply oil in a single direction of rotation, once reverse occurs, it will cause backflow, which will not only damage the lubrication, cooling and clutch control functions, but also directly lead to the failure of the lubrication or cooling system.

[0003] For example, when an electric gearbox is in reverse or the motor is reversing, a traditional oil pump cannot adapt to the reverse drive demand, resulting in oil supply interruption or oil circuit disorder, which makes it difficult to meet the actual use requirements. Based on the problems of the prior art, this case proposes a fluid conveying device to effectively solve the above problems and make up for the deficiencies of the prior art. Utility Model Content

[0004] In view of the shortcomings of the prior art, the purpose of this utility model is to provide a fluid conveying device and equipment with a simple structure, capable of rotating in both directions and maintaining a constant fluid output direction.

[0005] To achieve the above and other related objectives, this utility model provides a fluid conveying device, comprising:

[0006] Pump housing, wherein the pump housing is provided with a first through hole and a second through hole;

[0007] A rotor assembly, disposed within the pump housing, is configured to switch between two operating states:

[0008] In state one, when the rotor assembly rotates forward, it drives the fluid in the pump casing to flow from the first through hole to the second through hole;

[0009] In state two, when the rotor assembly reverses, it drives the fluid in the pump casing to flow from the second through hole to the first through hole;

[0010] Also includes:

[0011] A first chamber is connected to the first through hole. The first chamber is provided with a first inlet and a first outlet. The first inlet is provided with a first one-way valve and the first outlet is provided with a second one-way valve.

[0012] The second chamber is connected to the second through hole. The second chamber has a second inlet and a second outlet. The second inlet is equipped with a third check valve, and the second outlet is equipped with a fourth check valve.

[0013] In one embodiment of the present invention, the first chamber and / or the second chamber are integrated within the pump housing.

[0014] In one embodiment of this utility model, the first check valve and / or the second check valve and / or the third check valve and / or the fourth check valve are disposed on the pump housing.

[0015] In one embodiment of this utility model, the pump casing further includes an inlet and an outlet;

[0016] The inlet is connected to the first inlet and the second inlet; the outlet is connected to the first outlet and the second outlet.

[0017] In one embodiment of the present invention, the pump housing is provided with an installation channel for installing the first check valve and / or the second check valve and / or the third check valve and / or the fourth check valve, and the installation channel is sealed by a removable plug.

[0018] In one embodiment of the present invention, the rotor assembly includes a drive shaft, a driving rotor, and a driven rotor that meshes and drives the driving rotor.

[0019] The active rotor and the driven rotor are sealed inside the pump casing by end covers, and the drive shaft passes through the end covers and is connected to the active rotor.

[0020] In one embodiment of this utility model, the active rotor is an inner rotor, the driven rotor is an outer rotor, the driven rotor changes its volume periodically as the rotation direction of the active rotor changes, and the difference in the number of teeth between the active rotor and the driven rotor is 1-3.

[0021] In one embodiment of this utility model, the rotor assembly is a single-stage internal meshing cycloidal rotor assembly or a single-stage external meshing rotor assembly.

[0022] To achieve the above-mentioned objectives and other related objectives, this utility model provides a device including the fluid conveying device described above.

[0023] In one embodiment of the present invention, the device further includes a drive motor, a gearbox, and a clutch connecting the drive motor and the gearbox;

[0024] The drive shaft of the fluid conveying device is connected to the drive motor via a transmission or to the output shaft of the gearbox via a power clutch. A speed sensor is provided between the output shaft of the gearbox and the output shaft of the drive motor, and the speed sensor is electrically connected to the controller. The controller is configured to: when the speed sensor detects that the speed of the gearbox output shaft is greater than zero, control the power clutch to engage the drive shaft and the output shaft of the drive motor; when the speed of the gearbox output shaft is detected to be zero, control the power clutch to disconnect the drive shaft and the output shaft of the drive motor.

[0025] In summary, this utility model's fluid delivery device, through the synergistic action of a one-way valve assembly and a pump casing with a rotor assembly, achieves stable oil supply under both forward and reverse rotation conditions of the rotor assembly. Its core lies in the one-way valve assembly's ability to automatically switch the suction and discharge paths according to the rotor assembly's rotation direction, ensuring a continuous and sufficient supply of pressurized medium to the lubrication / cooling system during forward operation (e.g., conventional drive) or reverse operation (e.g., electric transmission reverse gear, motor reverse), effectively preventing equipment failures caused by oil supply interruptions or oil circuit disturbances, and significantly improving system reliability and stability. This invention simplifies the system structure; the fluid delivery device can be directly driven by the vehicle's transmission output, achieving an energy-saving mode of synchronous operation during driving. Compared to electric oil pumps, this fluid delivery device offers advantages in both energy consumption and cost, ensuring oil supply needs under critical operating conditions without requiring an additional power supply system, making it suitable for the needs of new energy vehicle transmission systems. Attached Figure Description

[0026] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0027] Figure 1 This is a schematic diagram of the fluid conveying device in one embodiment of the present invention.

[0028] Figure 2 This is a fluid flow diagram of the rotor assembly rotating forward in one embodiment of the present invention;

[0029] Figure 3 This is a fluid flow diagram of the rotor assembly in reverse rotation in one embodiment of the present invention;

[0030] Figure 4 This is an exploded view of the fluid conveying device structure in one embodiment of the present invention;

[0031] Figure 5This is a front view of the fluid conveying device in one embodiment of the present invention;

[0032] Figure 6 This is a schematic diagram of the fluid conveying device A1 in one embodiment of the present invention;

[0033] Figure 7 This is a schematic diagram of the structure of the fluid conveying device B1 in one embodiment of the present invention;

[0034] Figure 8 This is a schematic diagram of the fluid conveying device C1 in one embodiment of the present invention;

[0035] Figure 9 for Figure 2 Sectional view of the structure at point AA;

[0036] Figure 10 for Figure 2 Sectional view of the structure at point BB;

[0037] Figure 11 for Figure 4 Sectional view of the structure at point C;

[0038] Figure 12 for Figure 4 Sectional view of the structure at point DD;

[0039] Figure 13 for Figure 4 Structural state diagram of the active rotor at point DD during forward rotation;

[0040] Figure 14 for Figure 4 Structural state diagram of the active rotor reversing at point DD;

[0041] Component labeling description: Pump housing 1, First through hole 101, Second through hole 102, First chamber 11, First inlet 111, First outlet 112, Second chamber 12, Second inlet 121, Second outlet 122, Suction port 13, Discharge port 14, End cover 15, Drive shaft 16, Mounting channel 17, Plug 18, Screw 19, First check valve 21, Second check valve 22, Third check valve 23, Fourth check valve 24, Rotor assembly 3, Driving rotor 31, Driven rotor 32. Detailed Implementation

[0042] The following specific examples illustrate the implementation of this utility model. Those skilled in the art can easily understand other advantages and effects of this utility model from the content disclosed in this specification. This utility model can also be implemented or applied through other different specific embodiments, and various details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of this utility model. It should be noted that, in the absence of conflict, the following embodiments and features in the embodiments can be combined with each other. It should also be understood that the terminology used in the embodiments of this utility model is for describing specific implementation schemes and not for limiting the scope of protection of this utility model. Test methods in the following embodiments that do not specify specific conditions are generally performed under conventional conditions or according to the conditions recommended by the respective manufacturers.

[0043] Please see Figures 1 to 14 It should be understood that the structures, proportions, sizes, etc., depicted in the accompanying drawings are merely for illustrative purposes to aid those skilled in the art and are not intended to limit the scope of this invention. Therefore, they have no substantial technical significance. Any modifications to the structure, changes in proportions, or adjustments to size, without affecting the effectiveness or purpose of this invention, should still fall within the scope of the technical content disclosed in this invention. Furthermore, the terms such as "upper," "lower," "left," "right," "middle," and "one" used in this specification are merely for clarity and are not intended to limit the scope of this invention. Changes or adjustments to their relative relationships, without substantially altering the technical content, should also be considered within the scope of this invention.

[0044] When numerical ranges are given in the embodiments, it should be understood that, unless otherwise stated in this invention, both endpoints of each numerical range and any value between the two endpoints may be selected. Unless otherwise defined, all technical and scientific terms used in this invention, as well as the prior art known to those skilled in the art and the description of this invention, may be implemented using any prior art methods, devices, and materials similar to or equivalent to those described, used, or made of materials in the embodiments of this invention.

[0045] Please see Figures 1 to 3 This utility model provides a fluid conveying device, including a pump casing 1 and a rotor assembly 3;

[0046] The pump housing 1 is provided with a first through hole 101 and a second through hole 102; the rotor assembly 3 is disposed inside the pump housing 1, and the rotor assembly 3 is configured to switch between the following two operating states:

[0047] In state one, when the rotor assembly 3 rotates forward, it drives the fluid in the pump housing 1 to flow from the first through hole 101 to the second through hole 102; in state two, when the rotor assembly 3 rotates in reverse, it drives the fluid in the pump housing 1 to flow from the second through hole 102 to the first through hole 101.

[0048] The fluid conveying device further includes a first chamber 11 and a second chamber 12; the first chamber 11 is connected to the first through hole 101, and the first chamber 11 is provided with a first inlet 111 and a first outlet 112, the first inlet 111 is provided with a first one-way valve 21, and the first outlet 112 is provided with a second one-way valve 22; the second chamber 12 is connected to the second through hole 102, and the second chamber 12 is provided with a second inlet 121 and a second outlet 122, the second inlet 121 is provided with a third one-way valve 23, and the second outlet 122 is provided with a fourth one-way valve 24.

[0049] It should be noted that in this case, the pump housing 1 is the pump housing 1 of the fluid pump. The pump housing 1 is provided with a fluid drive cavity, which is a cavity for fitting and installing the rotor assembly 3. The first through hole 101 and the second through hole 102 are both connected to the fluid drive cavity. The first through hole 101 and the second through hole 102 are both holes for fluid to enter and exit the fluid drive cavity. The rotor assembly 3 is matched and installed with the pump housing 1. The rotor assembly 3 can rotate in the pump housing 1 to drive the fluid flow. When the rotation direction of the rotor assembly 3 of the fluid conveying device is switched, the fluid flow direction of the first through hole 101 and the second through hole 102 is switched accordingly. This case does not impose excessive restrictions on the type of fluid pump mentioned above, as long as the rotor assembly 3 is configured to switch between state one and state two. That is, the rotor assembly 3 in this case can be a claw rotor assembly (claw pump), a twin-screw rotor assembly (twin-screw pump), etc. Among them, the two non-contact claw-shaped rotors of the claw pump mesh with synchronous gears to form a periodic volume change to transport fluid. The claw rotors are symmetrically designed, and the fluid flow direction naturally switches when rotating in both directions. The twin-screw rotor assembly (twin-screw pump) uses two parallel screws that mesh with each other and push the fluid through the helical grooves. When the screw helix angle of the twin-screw pump is symmetrical, reversing the direction of rotation can achieve the switching of the flow direction. In addition, rotor assemblies 3 such as externally meshing gear rotors and internally meshing eccentrically set gear rotors can also achieve the switching of the fluid flow direction when rotating in both directions. Whether the first chamber 11, the second chamber 12, the first check valve 21, the second check valve 22, the third check valve 23, and the fourth check valve 24 are located inside the pump housing 1 can be determined according to actual needs. For example, the pump housing 1 can be an independent fluid pump housing 1, with the first through hole 101 of the fluid pump connected to the external first chamber 11 via a first pipeline, and the second through hole 102 of the fluid pump connected to the external second chamber 12 via a second pipeline, thus achieving the above solution.

[0050] The principle of this invention is as follows: The rotor assembly 3 of this invention can achieve bidirectional rotation. When switching between forward and reverse rotation, the first chamber 11 and the second chamber 12 alternately form an oil suction chamber and an oil pressure chamber. Specifically, in the forward rotation mode: the first one-way valve 21 (oil suction) of the first chamber 11 and the fourth one-way valve 24 (oil discharge) of the second chamber 12 are opened, and the second one-way valve 22 of the first chamber 11 and the third one-way valve 23 of the second chamber 12 are closed. The fluid flows from the first through hole 101 to the second through hole 102. Reverse operation: The third check valve 23 (oil suction) of the second chamber 12 and the second check valve 22 (oil discharge) of the first chamber 11 are opened, and the first check valve 21 of the first chamber 11 and the fourth check valve 24 of the second chamber 12 are closed. The fluid flows in reverse from the second through hole 102 to the first through hole 101, thereby enabling the fluid conveying device to adaptively switch the flow path. The opening and closing of the check valve responds to the rotor rotation direction, without the need for external control signals, realizing fully mechanized flow path reversal, and thus maintaining a constant fluid output direction.

[0051] In this case, the driving rotor 31 (such as the inner rotor) and the driven rotor 32 (such as the outer rotor) adopt an asymmetric design with a difference in the number of teeth (e.g., 6:7). Their meshing interface changes with the direction of rotation to form alternating suction chambers and pressure chambers: when rotating forward, the volume of the first chamber 11 increases to form a negative pressure and draw in fluid; the volume of the second chamber 12 decreases to form a high pressure and discharge fluid; when rotating in reverse, the first chamber 11 becomes a high pressure zone and the second chamber 12 becomes a negative pressure zone.

[0052] This invention utilizes the coordinated operation of pump casing 1, rotor assembly 3, first chamber 11, second chamber 12, first check valve 21, second check valve 22, third check valve 23, and fourth check valve 24 to ensure stable unidirectional fluid output regardless of whether rotor assembly 3 rotates forward or backward, thus completely eliminating the risk of backflow. Whether under normal forward operation or in special reverse-drive conditions, such as when the electric gearbox is in reverse gear or the motor is reversing, it ensures a sufficient supply of pressurized medium to the lubrication or cooling system, preventing equipment failure due to oil supply interruption or oil circuit confusion, and significantly improving the operational reliability and stability of the equipment. The fluid conveying device in this invention can be... The transmission output is directly driven and operates only when the vehicle is in motion. When the vehicle is stationary, the fluid delivery device stops rotating along with the transmission, significantly reducing ineffective energy consumption. Since the electric pump requires complex control circuitry to achieve bidirectional oil supply, which is costly and unreliable, this design uses a mechanical one-way valve to replace the complex control module of the electric pump. This significantly reduces manufacturing costs while ensuring functionality, and the structure is simple and the response speed is fast. The fluid delivery device in this design is compatible with electric transmissions, dual-motor composite drive systems, and traditional fuel vehicle transmissions. It is especially suitable for electric vehicle scenarios that require the motor to rotate in both directions. Through redundant one-way valve design, backflow of fluid (oil) is prevented, ensuring continuous lubrication and cooling of key components such as gears and bearings.

[0053] The fluid delivery device in this case effectively solves the problem of traditional oil pumps during reverse rotation, ensuring that the entire lubrication or cooling system maintains good operating conditions under different operating circumstances. This stable oil supply performance helps improve the heat dissipation and lubrication of the equipment, reduces wear and tear, and extends the service life of the equipment. At the same time, because the system complexity does not significantly increase due to oil circuit switching, the entire system is easier to design, install, and debug, further improving its adaptability and versatility, and making it widely applicable to various mechanical equipment requiring bidirectional oil supply.

[0054] Please see Figures 4 to 11 As one of the optional embodiments of this case, the first chamber 11 and / or the second chamber 12 are integrated into the pump housing 1.

[0055] It should be noted that if the first chamber 11 and / or the second chamber 12 are separate from the pump casing 1, there may be structural redundancy and leakage risks, requiring additional seals, increasing assembly complexity and leakage hazards. Furthermore, separate chambers occupy more space, which is not conducive to the miniaturization design of fluid conveying devices. At the same time, separate chambers need to be processed and assembled independently, increasing manufacturing costs and overall weight. Therefore, in this case, the pump casing 1 can be integrally formed with the first chamber 11 and the second chamber 12 through a casting process, with the chamber walls directly extending from the inner wall of the pump casing 1, without additional assembly. The integrated first chamber 11 and the second chamber 12 are directly connected to the flow channels in the pump casing 1, ensuring that the fluid flow paths between the first chamber 11 and the first through hole 101, and between the second chamber 12 and the second through hole 102 are minimized, reducing pressure loss. This invention integrates the first chamber 11 and / or the second chamber 12 into the pump housing 1, eliminating the connection interface between the separate chambers and the pump housing 1, reducing the number of parts and assembly steps, and lowering production costs. The integrated chamber avoids the sealing surfaces between the separate structures, significantly reducing the risk of oil leakage. Furthermore, the integrated chamber makes full use of the internal space of the pump housing 1, reducing the overall volume of the fluid delivery device and adapting to narrow installation environments (such as inside a gearbox). At the same time, the integral molding of the pump housing 1 and the chamber (such as casting or machining) can improve structural rigidity, resist high-pressure oil impact, and extend service life.

[0056] Please see Figures 4 to 11 As one of the optional embodiments of this case, the first one-way valve 21 and / or the second one-way valve 22 and / or the third one-way valve 23 and / or the fourth one-way valve 24 are disposed on the pump housing 1.

[0057] It should be noted that the one-way valve in this case can be directly installed and integrated into the first inlet 111 and the first outlet 112 of the first chamber 11, and / or installed and integrated into the second inlet 121 and the second outlet 122 of the second chamber 12. It can be fixed by threads or interference fit, or by other components, which simplifies the installation process and reduces the size of the fluid delivery device.

[0058] Please see Figures 11 to 14 As one of the optional embodiments of this case, the pump housing 1 further includes an inlet 13 and an outlet 14;

[0059] The inlet 13 is connected to the first inlet 111 and the second inlet 121; the outlet 14 is connected to the first outlet 112 and the second outlet 122.

[0060] It should be noted that if the suction port 13 and discharge port 14 are not integrated into the pump housing 1, the following problems will exist: for example, it will result in a long fluid flow path, large pressure loss, and easy leakage due to pipeline vibration; the assembly complexity will be high, as the separate suction port 13 and discharge port 14 require additional sealing interfaces, increasing assembly steps and failure risks; in addition, the suction and discharge directions of traditional oil pumps are reversed when they reverse, resulting in frequent switching of external oil circuits, increasing leakage risks and maintenance difficulties, and significantly increasing system complexity. In this case, by directly integrating the suction port 13 and discharge port 14 into the body of the pump housing 1, the fluid flow path is shortened, pressure loss is reduced, and oil supply efficiency is improved; at the same time, the sealing surface of the separate interface is eliminated, reducing the risk of leakage due to aging or loosening of the seals, and the integrated structure reduces external pipeline connections, reducing the risk of structural fatigue caused by vehicle vibration or impact. Specifically, in this case, the suction port 13 and the discharge port 14 can be directly formed inside the pump casing 1 by casting or machining, and the internal flow channels are seamlessly connected to the inlet / outlet of the first chamber 11 and the second chamber 12.

[0061] In this case, since each check valve can automatically switch between the inlet and outlet of the corresponding first chamber 11 and second chamber 12 according to the rotation direction of the rotor assembly 3, frequent switching of the external oil circuit is unnecessary. This not only reduces the risk of leakage due to poor sealing during oil circuit switching, but also simplifies the system's oil circuit structure and reduces the workload and difficulty for maintenance personnel. Maintenance personnel do not need to frequently inspect and replace the seals and connecting parts of the external oil circuit, reducing equipment downtime and maintenance time and costs, and improving equipment utilization efficiency.

[0062] Please see Figure 4 , Figure 10-11 As one of the optional embodiments of this case, the pump housing 1 is provided with an installation channel 17 for installing the first one-way valve 21 and / or the second one-way valve 22 and / or the third one-way valve 23 and / or the fourth one-way valve 24, and the installation channel 17 is sealed by a removable plug 18.

[0063] It should be noted that installation channels 17 for installing each check valve are provided at specific locations on the pump casing 1 to facilitate subsequent installation and maintenance of each check valve. Each installation channel 17 is equipped with a matching removable plug 18, which can be easily removed when installing or replacing check valves, and can also securely seal the installation channel 17 during daily operation, ensuring that the sealing and integrity of the pump casing 1 are not affected. This improves the efficiency of replacing, repairing, or inspecting the check valves of the fluid conveying device, significantly saving time and labor costs and improving the maintainability of the equipment. Secondly, the presence of the plug 18 effectively ensures the sealing of the pump casing 1, preventing fluid leakage and the entry of external impurities, maintaining the normal operating environment of the fluid conveying device, and ensuring the performance and reliability of the pump.

[0064] Please see Figure 4 As one of the optional embodiments of this case, the rotor assembly 3 includes a drive shaft 16, a drive rotor 31, and a driven rotor 32 that meshes with the drive rotor 31.

[0065] The active rotor 31 and the driven rotor 32 are sealed inside the pump housing 1 by the end cover 15, and the drive shaft 16 passes through the end cover 15 and is connected to the active rotor 31.

[0066] It should be noted that the end cover 15 is an important component of the pump casing 1, located on the side or end of the pump casing 1, serving a sealing and supporting function. The end cover 15 is generally made of high-strength metal material, possessing good sealing performance and mechanical strength, capable of withstanding the pressure and temperature generated during pump operation. The end cover 15 fits tightly with the inner wall of the pump casing 1, forming a sealed space to prevent fluid leakage. Simultaneously, the end cover 15 is also provided with sealing grooves and sealing rings to further enhance the sealing effect. At the connection between the end cover 15 and the pump casing 1, bolts or other reliable connection methods are typically used to ensure that the end cover 15 will not loosen or fall off during pump operation. The drive shaft 16 is a key component connecting the external power source and the drive rotor 31. The drive shaft 16 passes through the end cover 15 and connects to the drive rotor 31, enabling power to be effectively transmitted to the drive rotor 31. One end of the drive shaft 16 is generally connected to the external power source (such as a motor) via a coupling, while the other end is connected to the drive rotor 31 via a special coupling or spline to achieve torque transmission.

[0067] Please see Figure 4 , Figure 11-13 As one of the optional embodiments of this case, the active rotor 31 is an inner rotor, the driven rotor 32 is an outer rotor, the driven rotor 32 forms a periodic volume change as the rotation direction of the active rotor 31 changes, and the difference in the number of teeth between the active rotor 31 and the driven rotor 32 is 1-3.

[0068] It should be noted that in the single-stage internal meshing cycloidal pump, the driving rotor 31 and the driven rotor 32 are eccentrically arranged. During the operation of the single-stage internal meshing cycloidal pump, the meshing interface between the driving rotor 31 and the driven rotor 32 is constantly changing. When the drive shaft 16 rotates clockwise, at certain rotation angles, the gap between the driving rotor 31 and the driven rotor 32 gradually increases, forming an ever-expanding space, which is the suction chamber. At this time, the fluid is drawn into the suction chamber under the combined action of external pressure and negative pressure inside the pump. As the rotor continues to rotate, at other angles, the meshing interface gradually shrinks, and the fluid originally in the suction chamber is enclosed within it and continuously compressed, thus forming the pressure chamber. When the drive shaft 16 rotates counterclockwise, the entire process is reversed. The space that was originally the suction chamber gradually transforms into the pressure chamber, and the space that was originally the pressure chamber transforms into the suction chamber. In the single-stage internal meshing cycloidal pump, the tooth difference between the driving rotor 31 and the driven rotor 32 is set to a range of 1-3. When the tooth difference between the driving rotor 31 and the driven rotor 32 is within this range, the two rotors can form a suitable contact angle and contact area during meshing. If the tooth difference is too small, for example, less than 1, the meshing between the rotors may be too tight, thereby increasing frictional resistance and wear. This will not only affect the service life of the rotors but may also consume more energy to drive the rotors to rotate, reducing the overall efficiency of the pump. Conversely, if the tooth difference is too large, for example, greater than 3, the fit between the rotors may not be tight enough, resulting in an increased leakage channel and an increased amount of fluid leakage within the pump, which will also reduce the pump's working efficiency and performance.

[0069] Please see Figure 4 , Figure 11-13 As an optional embodiment of this case, the active rotor 31 is an inner rotor, the driven rotor 32 is an outer rotor, and the outer rotor can form a periodic volume change with the rotation direction of the inner rotor.

[0070] It should be noted that the coordinated operation of the inner and outer rotors results in a periodic and regular change in the volume of the working chamber. During the suction phase, as the volume of the working chamber gradually increases, sufficient negative pressure is created within the pump, facilitating the smooth entry of fluid into the pump cavity. Conversely, during the discharge phase, the volume of the working chamber gradually decreases, effectively compressing the fluid and imparting higher pressure energy, thus allowing it to be smoothly discharged from the pump cavity. This regular volume change helps reduce turbulence and eddies within the pump, minimizing energy loss and improving fluid transport efficiency.

[0071] Please see Figure 4 , Figure 11-13As one of the optional embodiments of this case, the rotor assembly 3 is a single-stage internal meshing cycloidal rotor assembly or a single-stage external meshing rotor assembly; the single-stage internal meshing cycloidal rotor assembly includes an inner rotor (cycloidal tooth shape) and an outer rotor (circular arc tooth shape), the inner and outer rotors are eccentrically mounted, and the fluid is transported by forming a periodically changing sealed cavity through meshing; the single-stage external meshing rotor assembly consists of two spur or helical gears of the same specification meshing, and when the gears rotate, they disengage to draw in liquid and enter meshing to discharge liquid.

[0072] This utility model provides a device, including the aforementioned fluid conveying device.

[0073] It should be noted that, for example, if the device is an electric drive transmission for a new energy vehicle, the fluid delivery device is integrated into the lubrication system inside the transmission housing. For example, if the device is a wind turbine pitch system, the fluid delivery device is integrated into the pitch hydraulic power station. The fluid delivery device in this case can be applied to scenarios where the drive shaft 16 needs to rotate in both directions, and where the fluid output direction of the fluid delivery device needs to be kept constant. Devices with such scenarios can use the fluid delivery device in this case.

[0074] As one optional embodiment of this case, the device further includes a drive motor, a gearbox, and a clutch that drives the drive motor and the gearbox;

[0075] The drive shaft 16 of the fluid delivery device is connected to the output shaft of the transmission or to the output shaft of the drive motor via a power clutch; a speed sensor is provided between the output shaft of the transmission and the output shaft of the drive motor, and the speed sensor is electrically connected to the controller; the controller is configured to: when the speed sensor detects that the speed of the transmission output shaft is greater than zero, control the power clutch to engage the drive shaft 16 and the output shaft of the drive motor; when the speed of the transmission output shaft is detected to be zero, control the power clutch to disconnect the drive shaft 16 and the output shaft of the drive motor.

[0076] It should be noted that when the speed sensor detects that the speed at the output of the gearbox is zero, the speed sensor will transmit a signal to the controller, which will then control the power clutch to operate. It should be understood that the controller can be the original controller on the vehicle for easy sharing; or the controller can be a PLC controller, such as a Siemens SIMATIC S7-1500 series PLC or a Mitsubishi Electric MELSEC iQ-R series PLC; the speed sensor is, for example, an MP-936 non-contact speed sensor or a Hal-12 Hall speed sensor; the power clutch is, for example, an HBS type separable pneumatic toothed clutch.

[0077] Traditional oil pumps continue to operate under the continuous drive of the engine or transmission when the vehicle is stationary (such as in neutral) or the engine is idling, resulting in ineffective power consumption and fuel waste. Especially in hybrid vehicles, when the electric motor and transmission power are decoupled, the oil pump or fluid delivery device runs idle, causing additional energy loss.

[0078] This design uses a speed sensor to monitor the output speed of the transmission in real time. When the detected speed is zero (the vehicle is stationary and not driven), it is determined to be an invalid oil supply condition. Regarding the rapid response of the power clutch, an electromagnetic wet power clutch can be used. After receiving the sensor signal, the controller controls the power clutch to quickly disconnect the mechanical connection between the drive shaft 16 and the drive motor, causing the fluid delivery device to stop working. It should be understood that the disengagement force of the power clutch is matched with the drive torque of the fluid delivery device to ensure reliable disengagement, thereby reducing the invalid operating time of the fluid delivery device, reducing oil consumption and wear on the fluid delivery device itself, and extending the service life of the fluid delivery device.

[0079] In summary, this utility model effectively overcomes some practical problems in the prior art, thus having high utilization value and significance.

[0080] The above embodiments are merely illustrative of the principles and effects of this utility model and are not intended to limit the scope of this utility model. Any person skilled in the art can modify or alter the above embodiments without departing from the spirit and scope of this utility model. Therefore, all equivalent modifications or alterations made by those skilled in the art without departing from the spirit and technical concept disclosed in this utility model should still be covered by the claims of this utility model.

Claims

1. A fluid delivery device, characterized by, include: Pump housing, wherein the pump housing is provided with a first through hole and a second through hole; A rotor assembly, disposed within the pump housing, is configured to switch between two operating states: In state one, when the rotor assembly rotates forward, it drives the fluid in the pump casing to flow from the first through hole to the second through hole; In state two, when the rotor assembly reverses, it drives the fluid in the pump casing to flow from the second through hole to the first through hole; Also includes: A first chamber is connected to the first through hole. The first chamber is provided with a first inlet and a first outlet. The first inlet is provided with a first one-way valve and the first outlet is provided with a second one-way valve. The second chamber is connected to the second through hole. The second chamber has a second inlet and a second outlet. The second inlet is equipped with a third check valve, and the second outlet is equipped with a fourth check valve.

2. The fluid delivery device of claim 1, wherein, The first chamber and / or the second chamber are integrated within the pump housing.

3. The fluid delivery device of claim 2, wherein, The first check valve and / or the second check valve and / or the third check valve and / or the fourth check valve are disposed in the pump housing.

4. The fluid delivery device of claim 3, wherein, The pump casing also includes an inlet and an outlet; The inlet is connected to the first inlet and the second inlet; the outlet is connected to the first outlet and the second outlet.

5. The fluid delivery device of claim 3, wherein, The pump casing is provided with an installation channel for installing the first check valve and / or the second check valve and / or the third check valve and / or the fourth check valve, and the installation channel is sealed by a removable plug.

6. The fluid delivery device of claim 1, wherein, The rotor assembly includes a drive shaft, a driving rotor, and a driven rotor that meshes with the driving rotor. The active rotor and the driven rotor are sealed inside the pump casing by end covers, and the drive shaft passes through the end covers and is connected to the active rotor.

7. The fluid delivery device of claim 6, wherein, The active rotor is an inner rotor, and the driven rotor is an outer rotor. The driven rotor changes its volume periodically as the rotation direction of the active rotor changes, and the difference in the number of teeth between the active rotor and the driven rotor is 1-3.

8. The fluid delivery device of claim 1, wherein, The rotor assembly is a single-stage internal meshing cycloidal rotor assembly or a single-stage external meshing rotor assembly.

9. An apparatus, comprising: Includes the fluid transport device according to any one of claims 1-8.

10. The apparatus of claim 9, wherein, The device also includes a drive motor, a gearbox, and a clutch connecting the drive motor and the gearbox; The drive shaft of the fluid conveying device is connected to the drive motor via a transmission or to the output shaft of the gearbox via a power clutch. A speed sensor is provided between the output shaft of the gearbox and the output shaft of the drive motor, and the speed sensor is electrically connected to the controller. The controller is configured to: when the speed sensor detects that the speed of the gearbox output shaft is greater than zero, control the power clutch to engage the drive shaft and the output shaft of the drive motor; when the speed of the gearbox output shaft is detected to be zero, control the power clutch to disconnect the drive shaft and the output shaft of the drive motor.

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