An internal gear pump device with self-heat dissipation function and an optimization method of configuration thereof

Abstract

The application discloses a novel self-heat-dissipation internal meshing gear pump device and a configuration optimization method thereof, and belongs to the technical field of hydraulic drive. The novel self-heat-dissipation internal meshing gear pump device is characterized in that: two ends of a crescent plate are respectively provided with a circular arc top corner located in a liquid suction area and a liquid compression area; a connecting line of a central shaft of the crescent plate and a central shaft of an internal gear is located in a same first axial plane; a connecting line of one of the circular arc top corners and the central shaft of the internal gear is located on a second axial plane; a connecting line of the other circular arc top corner and the central shaft of the internal gear is located on a third axial plane; and an included angle is arranged between the third axial plane and a reverse extension plane of the second axial plane. The novel self-heat-dissipation internal meshing gear pump device enhances flexibility and adaptability of the pump through design of the included angle theta between the third axial plane and the second axial plane, meets diversified working condition requirements, optimizes fluid flow by increasing the included angle theta, reduces power loss, simultaneously reduces direct contact area, reduces friction and abrasion, and prolongs service life.

Description

Technical Field

[0001] The present invention belongs to the technical field of hydraulic drive, and in particular relates to an internal meshing gear pump device with a self-heating function and a configuration optimization method thereof. Background Art

[0002] Gear pumps, with their compact structure, reliable operation, and ability to handle high-viscosity fluids, are widely used in hydraulic systems, lubrication systems, and the chemical industry. Typical applications include hydraulic pumps for hydraulic machinery, engine fluid pumps for automotive engines, lubrication systems for ships and aircraft, and the transportation of high-viscosity fluids in the chemical and food industries. However, despite the many advantages of internal gear pumps, their design optimization still presents numerous challenges.

[0003] At present, domestic internal gear pump manufacturers mostly rely on experimental experience or semi-empirical methods in the design process. Due to the complexity of the internal gear pump structure, this method often leads to low pump efficiency, especially the interactive effect of the shape of the crescent plate and the number of internal and external teeth, which is currently unclear. In addition, there is also a lack of a definite fluid-solid-electromagnetic multi-field coupling simulation model for predicting the performance of internal gear pumps. Therefore, there are great limitations when further optimizing the internal gear pump. Summary of the Invention

[0004] The purpose of the present invention is to address the problems existing in the prior art and to provide an internal gear pump device with a self-heating function and a method for optimizing its configuration.

[0005] To achieve the above-mentioned objectives, the invention adopts the following technical solution: an internal gear pump device with self-heating function, comprising a housing, an external gear is provided on the inner side of the housing, an electromagnetic component for rotating the external gear is provided between the outer periphery of the external gear and the inner periphery of the housing, an eccentrically arranged internal gear is provided on the inner periphery of the external gear, a crescent plate is provided between the outer periphery of the internal gear and the inner periphery of the external gear, the central axis of the crescent plate is coaxially arranged with the central axis of the external gear, the crescent plate separates the non-meshing area between the external gear and the internal gear into a liquid suction area and a liquid pressure area, circular arc vertex angles are provided at both ends of the crescent plate, respectively, located in the liquid suction area and the liquid pressure area, the line connecting the central axis of the crescent plate and the central axis of the internal gear is in the same first axial plane, the line connecting one of the circular arc vertex angles and the central axis of the internal gear is in a second axial plane, and the line connecting the other circular arc vertex angle and the central axis of the internal gear is in a third axial plane, and an angle is formed between the third axial plane and the reverse extension of the second axial plane.

[0006] By adopting the above technical solution, arc vertices are respectively provided at both ends of the crescent plate in the liquid suction area and the liquid pressure area. These arc vertices are respectively located on different axial planes with the central axis of the internal gear. This design not only optimizes the movement trajectory of the crescent plate, but also improves the sealing performance and volumetric efficiency of the pump. In particular, the line connecting one of the arc vertices and the central axis of the internal gear is on the second axial plane, and the other arc vertices is on the third axial plane that has an angle with the reverse extension plane of the second axial plane. This asymmetric design helps to reduce interference and wear of the crescent plate during movement, thereby improving the stability and reliability of the pump.

[0007] Optionally, an included angle between the third axial plane and the reverse extension plane of the second axial plane is θ, and 0°≤θ≤30°.

[0008] By adopting the above technical solution, the adjustability of the crescent plate angle θ provides more possibilities for optimizing the performance of the gear pump. By adjusting the angle θ, the spatial distribution of the suction area and the pressure area can be changed, thereby optimizing the flow and pressure characteristics of the gear pump to meet the needs of different application scenarios.

[0009] Optionally, a pair of bearings for rotating the external gear are installed on the outer periphery of the external gear, and the outer peripheries of the pair of bearings are respectively connected to the inner periphery of the housing.

[0010] By adopting the above technical solution, a pair of bearings installed on the outer periphery of the external gear provides stable support, making the external gear more stable during rotation, reducing friction and wear between the external gear and the housing, and extending the service life of the gear pump.

[0011] Optionally, the shell member includes a heat dissipation shell, a first sealing cover and a second sealing cover installed at both ends of the external gear, and a first end cover and a second end cover docked with the heat dissipation shell; the heat dissipation shell includes a pair of oppositely arranged connecting seats, a plurality of ribs are provided between the pair of connecting seats, and the plurality of ribs are equidistantly distributed along the circumferential direction of the end faces of the pair of connecting seats, and a plurality of the ribs are respectively provided with liquid flow channels with both ends passing through the pair of connecting seats.

[0012] By adopting the above technical solution, the design of the heat dissipation housing and the setting of the liquid flow channel effectively improve the heat dissipation performance of the gear pump. The liquid flow channel connects the two connecting seats through the rib plate and runs through the entire heat dissipation housing, so that heat can be quickly dissipated to the outside, ensuring the stable operation of the gear pump in a high temperature environment.

[0013] Optionally, the diameters of the first sealing cover and the second sealing cover are larger than the diameter of the inner ring of the outer gear, and the first sealing cover is provided with a liquid inlet hole and a liquid discharge hole connected to the liquid suction area and the liquid pressure area.

[0014] By adopting the above technical solution, the liquid inlet and the liquid discharge hole are connected to the liquid suction area and the liquid pressure area respectively, ensuring the smooth flow of the liquid. At the same time, the design of the sealing cover also effectively prevents liquid leakage.

[0015] Optionally, a cavity structure is provided on the first end cover and the second end cover respectively, both ends of the liquid flow channel are connected to the cavity structures on the first end cover and the second end cover respectively, and the drainage hole is connected to the cavity structure.

[0016] By adopting the above technical solution, the connection between the cavity structure on the first end cover and the second end cover and the liquid flow channel further improves the heat dissipation effect of the gear pump. The liquid in the liquid flow channel can cool the electromagnetic component and at the same time quickly dissipate the absorbed heat to the outside, thereby enhancing the heat dissipation capacity of the gear pump.

[0017] Optionally, the first end cover is provided with a liquid inlet pipe, one end of which is connected to the liquid inlet hole, and the second end cover is provided with a liquid discharge pipe, one end of which is connected to the cavity structure on the second end cover.

[0018] By adopting the above technical solution, the liquid inlet pipe is connected to the liquid inlet hole, which provides convenient liquid inlet and outlet for the gear pump. The design of the discharge pipe makes the liquid recyclable. This design not only facilitates the transportation of liquid, but also improves the convenience of using the gear pump.

[0019] Optionally, rotating shafts are respectively installed at both ends of the internal gear, and the other ends of the two rotating shafts are respectively rotatably connected to the first sealing cover and the second sealing cover, and connecting shafts are respectively provided at both ends of the crescent plate, and the two connecting shafts are respectively connected to the first sealing cover and the second sealing cover.

[0020] By adopting the above technical solution, this design ensures the stable rotation of the internal gear in the pump, improves the working reliability of the gear pump, and also ensures the stable connection of the crescent plate.

[0021] Optionally, the electromagnetic component includes a magnet installed between several adjacent ribs, and a coil installed on the outer periphery of the outer gear and positioned to dock with the magnet. The number of the magnets is n, n≥12, and n is an integer multiple of 4. The number of the magnets is the same as the number of the coils, and there is a gap between the magnet and the coil.

[0022] By adopting the above technical solution, the design of the magnet and the coil provides a stable driving force for the gear pump. The gap between the magnet and the coil ensures the effective transmission of the electromagnetic force, improves the driving efficiency of the gear pump, and at the same time, facilitates heat dissipation of the coil and the magnet.

[0023] Optionally, a method for optimizing an internal gear pump device with a self-heating function comprises the following steps:

[0024] Analyzing the structural parameters of the gear pump device, including the number of teeth and radius of the external gear and the internal gear, the speed and torque of the gear pump, and the crescent angle, wherein the crescent angle refers to the angle θ between the third axial plane and the reverse extension of the second axial plane;

[0025] Based on the structural parameter range of the existing gear pump, confirm the structural parameter range of the gear pump device;

[0026] Using three-dimensional modeling software, based on the preliminarily determined structural parameter range of the gear pump device and the value range of the angle θ, multiple virtual models of the gear pump device are constructed, and the multiple virtual models are compared with the inlet and outlet pressure tests of existing gear pumps to select the virtual model with the best performance;

[0027] Use ANSYS Workbench to perform multi-field coupled numerical simulation of the internal and external characteristics of the motor, structure, and flow channel of the optimal performance virtual model. After the multi-field coupled numerical simulation is completed, the simulation data is extracted from ANSYS Workbench.

[0028] By using the orthogonal experimental design principle, representative parameter combinations are selected from the preliminarily determined structural parameter range of the gear pump device to form a structural parameter matrix;

[0029] By combining the structural parameter matrix with the simulation data, the simulation data with the closest performance is selected as the initial simulation data;

[0030] The initial simulation data is iteratively optimized multiple times using a CG genetic algorithm through a MATLAB platform until a predetermined number of iterations is reached or the optimal simulation data and the corresponding optimal configuration that meet the design requirements are found. The gear pump device is manufactured using the optimal configuration.

[0031] By adopting the above technical solution, the structural parameters of the gear pump device were analyzed, and a virtual model was constructed using 3D modeling software for experimental comparison. The virtual model with the best performance was selected for multi-field coupling numerical simulation. Then, iterative optimization was carried out by combining the orthogonal experimental design principle and genetic algorithm, and finally the optimal configuration that met the design requirements was obtained. This optimization method not only improved the performance of the gear pump, but also reduced the design cost and shortened the R&D cycle.

[0032] Compared with the prior art, the present invention has the following beneficial effects:

[0033] 1. The internal meshing gear pump device with self-heating function of the present invention innovatively realizes the variable crescent plate arc vertex angle through the design of the angle θ between the third and second axial planes, thereby enhancing the flexibility and adaptability of the pump and meeting the needs of diverse working conditions. At low speeds, reducing the angle θ to 0° can increase the contact area between the crescent plate and the gear. This design change helps to reduce fluid leakage inside the pump body because a larger contact area means a tighter seal. The reduction in leakage directly improves the working efficiency of the pump, minimizes energy loss, and thus improves the overall performance. At high speeds, increasing the angle θ can optimize fluid flow, reduce power loss, and at the same time reduce the direct contact area, reduce friction and wear, and extend the service life.

[0034] 2. The adjustability of the angle θ allows the structure of the crescent plate to be adjusted according to different working conditions. In applications requiring high pressure output, the sealing effect of the crescent plate can be improved by optimizing the angle θ, thereby ensuring stable operation of the pump. In situations where low-viscosity liquids are processed or a fast response is required, the fluid flow path can be optimized by adjusting the angle θ, thereby improving the response speed and efficiency of the pump.

[0035] 3. The heat dissipation shell, liquid flow channel, liquid inlet pipe, liquid inlet hole, liquid discharge hole and the cavity structure on the end cover together constitute an integrated heat dissipation system. This design not only simplifies the heat dissipation structure, but also improves the heat dissipation efficiency. The cooling liquid enters the liquid-oil area from the liquid inlet pipe. With the rotation of the internal gear and the sealing effect of the crescent plate, the liquid is compressed and pushed into the liquid pressure area, and finally enters the liquid flow channel through the discharge hole and the cavity structure for circulation and heat dissipation. In this process, the heat exchange between the cooling liquid and the internal components of the gear pump is more sufficient, and the heat dissipation effect is more significant.

[0036] 4. By using advanced tools such as 3D modeling software, ANSYS Workbench and MATLAB for numerical simulation and optimization design, the performance of the gear pump device was accurately predicted and optimized. This approach not only improved the accuracy and efficiency of the design, but also reduced the design cost and shortened the R&D cycle.

[0037] 5. By applying the principles of parametric design and orthogonal experimental design, combined with simulation data and genetic algorithms for optimization, the optimal configuration that meets the design requirements was found. This design optimization method not only improves the performance of the gear pump, but also enhances its adaptability and flexibility, making customized design possible for different application scenarios. BRIEF DESCRIPTION OF THE DRAWINGS

[0038] Figure 1 This is a schematic cross-sectional view of the internal gear pump device with self-heating function according to the present invention;

[0039] Figure 2This is a schematic diagram of the overall main structure of the internal gear pump device with self-heating function of the present invention;

[0040] Figure 3 This is a schematic diagram of the exploded structure of the electromagnetic component, internal gear, external gear and crescent plate of the present invention;

[0041] Figure 4 This is a schematic diagram of the three-dimensional structure of the heat dissipation housing of the present invention;

[0042] Figure 5 This is a schematic diagram of the three-dimensional structure of the first end cover of the present invention;

[0043] Figure 6 This is a schematic diagram of the three-dimensional structure of the second end cover of the present invention;

[0044] Figure 7 The magnetic flux distribution vector diagram of the present invention;

[0045] Figure 8 This is a parameter range diagram for the present invention;

[0046] Figure 9 It is the structural parameter matrix diagram of the present invention;

[0047] Figure 10 The flow rate change and fluctuation diagram under different chamfers of the present invention;

[0048] Figure 11 This is the pressure distribution diagram under different chamfers of the present invention;

[0049] Figure 12 This is a time-frequency response characteristic diagram of the torque of the present invention;

[0050] Figure 13 This is the magnetic flux density distribution diagram of the present invention.

[0051] In the figure: 1. Shell member; 11. Heat dissipation shell; 1101. Connecting seat; 1102. Rib plate; 1103. Liquid flow channel; 12. First sealing cover; 1201. Liquid inlet hole; 1202. Liquid discharge hole; 13. Second sealing cover; 14. First end cover; 1401. Liquid inlet pipe; 15. Second end cover; 1501. Liquid discharge pipe; 16. Cavity structure; 2. External gear; 201. Bearing; 3. Electromagnetic component; 301. Magnet; 302. Coil; 4. Internal gear; 401. Rotating shaft; 5. Crescent plate; 501. Connecting shaft; 6. Liquid suction area; 7. Liquid pressure area; 8. Arc top angle. DETAILED DESCRIPTION

[0052] The following will clearly and completely describe the technical solution of the present invention in conjunction with the accompanying drawings. Obviously, the embodiments described are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0053] In the description of the present invention, it should be noted that the terms "middle", "upper", "lower", "left", "right", "inside", "outside", etc., indicating directions or positional relationships, are based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the present invention.

[0054] like Figure 1 —6, the specific scheme of the embodiment is as follows: an internal meshing gear pump device with self-heating function, including a shell part 1, an outer gear 2 is provided on the inner side of the shell part 1, and the outer gear 2 is one of the key components of the gear pump. It is meshed with the inner gear 4 through electromagnetic drive to realize the suction and discharge of liquid. The tooth shape of the outer gear 2 matches the tooth shape of the inner gear 4 to ensure the efficient operation of the gear pump. A pair of bearings 201 for rotating the outer gear 2 is installed on the outer periphery of the outer gear 2. The outer peripheries of the pair of bearings 201 are respectively connected to the inner periphery of the shell part 1. The pair of bearings 201 play a supporting and guiding role to ensure that the outer gear 2 rotates smoothly and frictionlessly in the shell part 1. The outer periphery of the outer gear 2 An electromagnetic component 3 for rotating the external gear 2 is provided between the housing 1 and the inner periphery thereof. The electromagnetic component 3 includes magnets 301 mounted on the outer periphery of the housing 1 and coils 302 mounted on the outer periphery of the external gear 2 and positioned to engage with the magnets 301. The number of magnets 301 is n, where n ≥ 12 and n is an integer multiple of 4. The number of magnets 301 is n (n ≥ 12 and n is an integer multiple of 4). This design ensures the stability and uniformity of the rotating magnetic field. The distribution and arrangement of the magnetic poles of the magnets 301 are crucial to the generation and effect of the rotating magnetic field. The number of magnets 301 is the same as that of the coils 302, and a gap exists between the magnets 301 and the coils 302.

[0055] When three-phase alternating current is applied, a rotating magnetic field forms around magnet 301. Due to the varying directions of the applied current, the magnetic field's NS-order fluctuations shift, creating the effect of like charges repelling and opposite charges attracting. This effect drives outer gear 2, causing it to begin rotating. Under the influence of the rotating magnetic field, outer gear 2 meshes with inner gear 4, achieving the suction and discharge of liquid. The rotational speed and direction of outer gear 2 are determined by the strength and direction of the rotating magnetic field. Therefore, the output flow rate and pressure of the gear pump can be controlled by adjusting the magnitude and frequency of the current. As the current in coil 302 changes, the magnetic field formed by coil 302 alternates inward and outward motion near magnet 301, becoming densely distributed within the air gap of coil 302, as shown in Figure 7, effectively providing torque.

[0056] An eccentrically arranged internal gear 4 is provided on the inner periphery of the external gear 2, and rotating shafts 401 are respectively installed at both ends of the internal gear 4. The other ends of the two rotating shafts 401 are rotatably connected to the first sealing cover 12 and the second sealing cover 13 respectively. A crescent plate 5 is provided between the outer periphery of the internal gear 4 and the inner periphery of the external gear 2, and connecting shafts 501 are respectively provided at both ends of the crescent plate 5. The two connecting shafts 501 are respectively connected to the first sealing cover 12 and the second sealing cover 13. The central axis of the crescent plate 5 is coaxially arranged with the central axis of the external gear 2. The eccentric arrangement of the internal gear 4 and the external gear 2 is the key to realizing the function of the positive displacement pump. It rotates with the rotation of the external gear 2, but the centers of the two do not coincide, thereby forming a changing volume during the meshing process. The continuous suction and discharge of the liquid are realized through the periodic increase and decrease of the volume.

[0057] The crescent plate 5 separates the non-meshing area between the external gear 2 and the internal gear 4 into a liquid suction area 6 and a liquid pressure area 7. The crescent plate 5 can achieve continuous suction, compression and discharge of the fluid by changing the fluid path, and is one of the decisive factors for the efficiency and working characteristics of the pump. The two ends of the crescent plate 5 are respectively provided with arc vertex angles 8 located in the liquid suction area 6 and the liquid pressure area 7. The arc vertex angles 8 can optimize the fluid flow path, reduce the turbulence and energy loss of the fluid in the conversion area, improve the efficiency of the pump, reduce noise and vibration, and help maintain the stability and reliability of the system. The central axis of the crescent plate 5 and the line connecting the central axis of the internal gear 4 are in the same first axial plane, the line connecting one of the arc vertex angles 8 and the central axis of the internal gear 4 is in the second axial plane, and the line connecting the other arc vertex angle 8 and the central axis of the internal gear 4 is in the third axial plane. An angle is set between the third axial plane and the reverse extension plane of the second axial plane. The angle between the third axial plane and the reverse extension plane of the second axial plane is θ, and 0°≤ θ≤ 30°. By adjusting the angle θ, the relative position of the crescent plate 5 in the liquid suction area 6 and the liquid pressure area 7 can be changed, thereby affecting the flow rate, pressure and efficiency of the pump.

[0058] In the second embodiment, the shell member 1 includes a heat dissipation shell 11, a first sealing cover 12 and a second sealing cover 13 installed at both ends of the external gear 2, and a first end cover 14 and a second end cover 15 docked with the heat dissipation shell 11; the heat dissipation shell 11 includes a pair of relatively arranged connecting seats 1101, which not only connect and support the ribs 1102, but also provide installation space for the electromagnetic member 3 and the external gear 2. A plurality of ribs 1102 are provided between the pair of connecting seats 1101, which not only enhance the structural strength of the heat dissipation shell 11, but also realize the circulation path of the cooling liquid through the liquid flow channel 1103 opened inside. The design of the ribs 1102 optimizes the heat conduction performance of the heat dissipation shell 11 and improves the heat dissipation performance. Thermal efficiency: The magnet 301 is installed between the ribs 1102, so that the magnet 301 can directly dissipate heat. Several of the ribs 1102 are equidistantly distributed along the end faces of a pair of connecting seats 1101. Several of the ribs 1102 are respectively provided with liquid channels 1103 with both ends passing through the pair of connecting seats 1101. The liquid channels 1103 provided in the ribs 1102 are the core part of the gear pump heat dissipation system. The cooling liquid enters the liquid channel 1103 through the liquid inlet pipe 1401, circulates inside the gear pump, absorbs and takes away the heat generated by the gear assembly, and then is discharged through the drain pipe 1501 to complete the heat dissipation cycle. The design of the liquid channel 1103 ensures the smooth flow of the cooling liquid and efficient heat dissipation.

[0059] The diameters of the first sealing cover 12 and the second sealing cover 13 are larger than the diameter of the inner ring of the outer gear 2. The first sealing cover 12 and the second sealing cover 13 are respectively installed at both ends of the outer gear 2 to play a sealing role to prevent the gear pump from leaking during operation. At the same time, they also serve as an isolation layer between the gear pump and the external environment to protect the internal gear components from external pollution and damage. The first sealing cover 12 is provided with a liquid inlet hole 1201 and a liquid discharge hole 1202 connected to the liquid suction area 6 and the liquid pressure area 7. The liquid inlet hole 1201 is the entrance for the cooling liquid to enter the liquid suction area 6 of the gear pump. The cooling liquid is introduced into the interior of the gear pump through the connection between the liquid inlet pipe 1401 and the liquid inlet hole 1201. The liquid discharge hole 1202 is a connecting channel between the liquid pressure area 7 of the gear pump and the cavity structure 16. During the operation of the gear pump, the compressed cooling liquid enters the cavity structure 16 through the liquid discharge hole 1202;

[0060] The first end cover 14 and the second end cover 15 are respectively provided with cavity structures 16, which are key parts of the cooling liquid circulation, and are not only connected with the liquid flow channel 1103 to form a complete cooling circuit, but also provide necessary space for the storage and flow of the cooling liquid.

[0061] An optimization method of an internal meshing gear pump device with self-heat dissipation function, the optimization method comprising the following steps:

[0062] Analyzing the structural parameters of the gear pump device, the structural parameters of the gear pump device including the number of teeth and the radius of the outer gear 2 and the inner gear 4, the rotational speed and torque of the gear pump, and the angle of the crescent plate 5, wherein the angle of the crescent plate 5 refers to the included angle θ between the third axial plane and the reverse extension plane of the second axial plane, and the number of teeth of the outer gear 2 is N1, the number of teeth of the inner gear 4 is N2, the radius of the outer gear 2 is R, the chamfer angle of the crescent plate 5 is θ, and the thickness of the crescent plate 5 is H;

[0063] Confirming the range of the structural parameters of the gear pump device based on the range of the structural parameters of the existing gear pump, and the range of the structural parameters is as shown in Figure 8

[0064] Using three-dimensional modeling software such as SolidWorks, CATIA, etc., according to the range of the structural parameters of the gear pump device and the range of the included angle θ preliminarily determined, a plurality of virtual models of the gear pump device are constructed, the inlet and outlet pressure tests of the plurality of virtual models are carried out, the test data are compared with the inlet and outlet pressure test data of the existing gear pump, the performance of each virtual model is evaluated by measuring the performance indexes such as inlet and outlet pressure and flow rate, and the virtual model with the best performance is selected as the basis for subsequent numerical simulation.

[0065] ​When using 3D modeling software to model different gear pump flow channels, the model design of no chamfer, small chamfer, medium chamfer and large chamfer is carried out according to the principle of bionics, and the flow change, fluctuation diagram and pressure distribution diagram are analyzed, such as Figure 10 and Figure 11 , the chamfer angle θ=20° corresponding to the maximum flow rate is determined. The flow velocity gradually increases under different chamfer angles, which also leads to an increase in flow rate. When the chamfer angle is too large, the sealing performance of the inner and outer sides of the crescent plate 5 is reduced, which also leads to a decrease in fluid transport capacity. Similarly, as the left crescent plate 5 gradually becomes smoother, the internal flow field fluctuation gradually decreases. As the chamfer angle continues to increase, the backflow effect causes the flow fluctuation to intensify. The mean pressure difference gradually decreases under different chamfer angles, indicating that under the same outlet pressure, it is less likely to generate negative pressure at the inlet, and the torque of the motor is also smaller.

[0066] ANSYS Workbench was used to perform multi-field coupled numerical simulations of the internal and external characteristics of the motor, structure, and flow channel structures of the optimal virtual model. The following parameter settings were required during the multi-field coupled numerical simulations:

[0067] The inlet pressure is atmospheric pressure, i.e. 101.325 kPa;

[0068] The outlet pressure is 10MPa;

[0069] The rotation speed of the external gear 2 is 4800 r / min;

[0070] The internal gear 4 rotates at a speed of 8000 r / min;

[0071] The density of the fluid is 844 kg / m3;

[0072] Fluid viscosity: 0.0254 kg / (m·s);

[0073] After completing the multi-field coupling numerical simulation, the internal flow pressure, velocity vector, motor magnetic flux, motor torque, and pressure time-frequency response characteristic diagrams were obtained. The simulation data, including key performance indicators such as flow rate, pressure distribution, and torque, were extracted from ANSYS Workbench.

[0074] By using the principle of orthogonal experimental design, representative parameter combinations are selected from the initially determined structural parameter range of the gear pump device to form a structural parameter matrix. The structural parameter matrix is ​​as follows: Figure 9 As shown;

[0075] Through the structural parameter matrix and combined with the simulation data, the simulation data with the closest performance are selected as the initial simulation data, which will serve as the starting point for the subsequent optimization algorithm;

[0076] Through the MATLAB platform, the CG genetic algorithm is used to perform multiple iterations of optimization on the initial simulation data. During the optimization process, the structural parameter combination is continuously adjusted to find the optimal simulation data and the corresponding optimal configuration that meet the design requirements. The optimization process should continue until the predetermined number of iterations is reached or the optimal solution that meets the design requirements is found, such as Figure 12 As shown in Figure 2, when the torque fluctuation is relatively regular and maintained in a relatively low range, the torque fluctuation value is about 5% of the mean value, indicating that the motor can run smoothly under this structure. Figure 13 As shown in the figure, the magnetic field intensity distribution is relatively uniform and the rotor can run smoothly, so the optimized configuration is the optimal configuration.

[0077] Although the embodiments of the present invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and variations may be made to these embodiments without departing from the principles and concepts of the present invention, and that the scope of the present invention is defined by the appended claims and their equivalents.

Claims

1. An internal gear pump device with self-heating function, characterized in that: The cam is secured to the inner surface of the gear train and is designed to engage the gears of the driver and the control gear of the driver, the cam being secured to the inner surface of the gear train and being adapted to engage the gears of the driver and the control gear of the driver. The shell member includes a heat dissipation shell, a first sealing cover and a second sealing cover installed at both ends of the external gear, and a first end cover and a second end cover docked with the heat dissipation shell; the heat dissipation shell includes a pair of oppositely arranged connecting seats, a plurality of ribs are provided between the pair of connecting seats, and the plurality of ribs are equidistantly distributed along the circumference of the end faces of the pair of connecting seats, and a plurality of ribs are respectively provided with flow channels with both ends passing through the pair of connecting seats, the diameters of the first sealing cover and the second sealing cover are larger than the diameter of the inner ring of the external gear, the first sealing cover is provided with a liquid inlet hole and a liquid discharge hole connected to the liquid suction area and the liquid pressure area, the first end cover and the second end cover are respectively provided with a cavity structure, the two ends of the liquid flow channel are respectively connected to the cavity structures on the first end cover and the second end cover, and the liquid discharge hole is connected to the cavity structure.

2. The internal gear pump device with self-heating function according to claim 1, characterized in that: An included angle between the third axial plane and the reverse extension plane of the second axial plane is θ, and 0°≤θ≤30°.

3. The internal gear pump device with self-heating function according to claim 1, characterized in that: A pair of bearings for rotating the external gear is installed on the outer periphery of the external gear, and the outer peripheries of the pair of bearings are respectively connected to the inner periphery of the housing.

4. The internal gear pump device with self-heating function according to claim 1, characterized in that: The first end cover is provided with a liquid inlet pipe, one end of which is connected to the liquid inlet hole; the second end cover is provided with a liquid discharge pipe, one end of which is connected to the cavity structure on the second end cover.

5. The internal gear pump device with self-heating function according to claim 1, characterized in that: A rotating shaft is installed at both ends of the internal gear, and the other ends of the two rotating shafts are rotatably connected to the first sealing cover and the second sealing cover respectively. A connecting shaft is provided at both ends of the crescent plate, and the two connecting shafts are connected to the first sealing cover and the second sealing cover respectively.

6. The internal gear pump device with self-heating function according to claim 1, characterized in that: The electromagnetic component includes a magnet installed between several adjacent ribs, and a coil installed on the outer periphery of the external gear and positioned to interface with the magnet. The number of the magnets is n, n≥12, and n is an integer multiple of 4. The number of the magnets is the same as the number of the coils, and there is a gap between the magnets and the coils.

7. The method for optimizing the configuration of an internal gear pump device with self-heating function according to claim 1, characterized in that: The optimization method includes the following steps: Analyzing the structural parameters of the gear pump device, including the number of teeth and radius of the external gear and the internal gear, the speed and torque of the gear pump, and the crescent angle, wherein the crescent angle refers to the angle θ between the third axial plane and the reverse extension of the second axial plane; Based on the structural parameter range of the existing gear pump, confirm the structural parameter range of the gear pump device; Using three-dimensional modeling software, based on the preliminarily determined structural parameter range of the gear pump device and the value range of the angle θ, multiple virtual models of the gear pump device are constructed, and the multiple virtual models are compared with the inlet and outlet pressure tests of existing gear pumps to select the virtual model with the best performance; Use ANSYS Workbench to perform multi-field coupled numerical simulation of the internal and external characteristics of the motor, structure, and flow channel of the optimal performance virtual model. After the multi-field coupled numerical simulation is completed, the simulation data is extracted from ANSYS Workbench. By using the orthogonal experimental design principle, representative parameter combinations are selected from the preliminarily determined structural parameter range of the gear pump device to form a structural parameter matrix; By combining the structural parameter matrix with the simulation data, the simulation data with the closest performance is selected as the initial simulation data; The initial simulation data is iteratively optimized multiple times using a CG genetic algorithm through a MATLAB platform until a predetermined number of iterations is reached or optimal simulation data and a corresponding optimal configuration that meet the design requirements are found.

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