Novel internal gear pump device with self-heat-dissipation function and optimization method of configuration of novel internal gear pump device

Abstract

The invention discloses a novel internal gear pump device with a self-cooling function and a configuration optimization method thereof, and belongs to the technical field of hydraulic driving. According to the novel internal gear pump device with the self-heat-dissipation function, the two ends of a crescent plate are provided with arc vertex angles located in a liquid suction area and a liquid pressing area respectively, and the connecting lines of the center axis of the crescent plate and the center axis of an internal gear are located in the same first axial plane; wherein the connecting line of one arc vertex angle and the center shaft of the inner gear is located on a second axial plane, the connecting line of the other arc vertex angle and the center shaft of the inner gear is located on a third axial plane, and an included angle is formed between the third axial plane and the reverse extension face of the second axial plane. According to the novel internal gear pump device with the self-heat-dissipation function, through the design of the included angle theta between the third axial plane and the second axial plane, the flexibility and adaptability of a pump are enhanced, diversified working condition requirements are met, the included angle theta is increased, fluid flowing can be optimized, power loss is reduced, meanwhile, the direct contact area is reduced, and frictional wear is reduced; the service life is prolonged.

Description

Technical Field

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

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

[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 the prediction of the performance of the internal gear pump. 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 provide a novel internal gear pump device with self-heat dissipation function and a method for optimizing its configuration in view of the problems existing in the prior art.

[0005] To achieve the above-mentioned purpose, the invention adopts the following technical scheme: a new type of internal meshing gear pump device with self-heating function, including a shell member, an external gear is provided on the inner side of the shell member, an electromagnetic member for rotating the external gear is provided between the outer periphery of the external gear and the inner periphery of the shell member, 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 divides the non-meshing area between the external gear and the internal gear into a liquid suction area and a liquid pressing area, arc vertex angles located in the liquid suction area and the liquid pressing area are respectively provided at both ends of the crescent plate, 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 arc vertex angles and the central axis of the internal gear is in the second axial plane, the line connecting the other arc vertex angle and the central axis of the internal gear is in the third axial plane, and an angle is provided between the third axial plane and the reverse extension surface of the second axial plane.

[0006] By adopting the above technical scheme, arc vertices located in the liquid suction area and the liquid pressure area are respectively provided at both ends of the crescent plate, and these arc vertices and the central axis of the internal gear are respectively located on different axial planes. 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 angle between the third axial plane and a 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 rotation of 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.

[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 connected to the heat dissipation shell; the heat dissipation shell includes a pair of relatively arranged connecting seats, a plurality of ribs are provided between the pair of connecting seats, the plurality of ribs are equidistantly distributed along the circumferential direction of the end faces of the pair of connecting seats, and the plurality of ribs are respectively provided with liquid flow channels at 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 fluid flow channel effectively improve the heat dissipation performance of the gear pump. The fluid flow channel connects the two connecting seats through the rib plate and runs through the entire heat dissipation housing, so that the 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 hole 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 the leakage of the liquid.

[0015] Optionally, a cavity structure is respectively provided on the first end cover and the second end cover, 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 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, a liquid inlet pipe is provided on the first end cover, one end of which is connected to the liquid inlet hole, and a liquid discharge pipe is provided on the second end cover, 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 rotatably connected to the first sealing cover and the second sealing cover respectively. 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 a number of adjacent rib plates, 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 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 the heat dissipation of the coil and the magnet.

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

[0024] Analyze the structural parameters of the gear pump device, which include 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 inlet and outlet pressure experiments of the multiple virtual models are compared with the existing gear pump to select the virtual model with the best performance;

[0027] Use ANSYS Workbench to perform multi-field coupling numerical simulation of the internal and external characteristics of the motor-structure-flow channel multi-structure on the virtual model with the best performance. After the multi-field coupling numerical simulation is completed, extract the simulation data from ANSYS Workbench;

[0028] By using the orthogonal experimental design principle, representative parameter combinations are selected from the initially 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] Through the MATLAB platform, the initial simulation data is iteratively optimized multiple times using the CG genetic algorithm 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, and the gear pump device is manufactured through the optimal configuration.

[0031] By adopting the above technical scheme, the structural parameters of the gear pump device are analyzed, and a virtual model is constructed using 3D modeling software for experimental comparison. The virtual model with the best performance is selected for multi-field coupling numerical simulation. It is then combined with the orthogonal experimental design principle and genetic algorithm for iterative optimization, and finally the optimal configuration that meets the design requirements is obtained. This optimization method not only improves the performance of the gear pump, but also reduces the design cost and shortens the R&D cycle.

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

[0033] 1. The novel 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 diversified working conditions. At low speeds, when the angle θ is reduced to 0°, the contact area between the crescent plate and the gear can be increased. This design change helps to reduce fluid leakage inside the pump body, because a larger contact area means a tighter seal, and 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 service life.

[0034] 2. The adjustability of the angle θ enables 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 the stable operation of the pump. When processing low-viscosity liquids or requiring rapid response, the angle θ can be adjusted to optimize the fluid flow path and improve 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 liquid 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, accurate prediction and optimization of the performance of the gear pump device are achieved. This method not only improves the accuracy and efficiency of the design, but also reduces the design cost and shortens the R&D cycle.

[0037] 5. Through the principles of parametric design and orthogonal experimental design, combined with simulation data and genetic algorithm 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, providing the possibility for customized design in different application scenarios. BRIEF DESCRIPTION OF THE DRAWINGS

[0038] Figure 1 It is a schematic cross-sectional structure diagram of a novel internal gear pump device with self-heat dissipation function of the present invention;

[0039] Figure 2It is a schematic diagram of the overall front view of the novel internal gear pump device with self-heat dissipation function of the present invention;

[0040] Figure 3 It is a schematic diagram of the explosion structure of the electromagnetic part, the inner gear, the outer gear and the 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 It 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 It is a parameter range diagram of the present invention;

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

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

[0048] Fig.11 The pressure distribution diagram of different chamfers of the present invention;

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

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

[0051] In the figure: 1, housing member; 11, heat dissipation housing; 1101, connection 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;

[0052] 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 pressing area; 8. Arc top angle. DETAILED DESCRIPTION

[0053] The technical solution of the present invention will be described clearly and completely below in conjunction with the accompanying drawings of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0054] In the description of the present invention, it should be noted that the directions or positional relationships indicated by terms such as "middle", "upper", "lower", "left", "right", "inside" and "outside" are based on the directions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific direction, be constructed and operated in a specific direction, and therefore cannot be understood as a limitation on the present invention.

[0055] like Figure 1 —6, the specific scheme of the embodiment is as follows: a new type of internal meshing gear pump device with self-heating function, including a shell member 1, an outer gear 2 is provided on the inner side of the shell member 1, and the outer gear 2 is one of the key components of the gear pump. It meshes with the inner gear 4 through electromagnetic drive to achieve liquid suction and discharge. 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 the rotation of the outer gear 2 are 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 member 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 member 1. The outer periphery of the outer gear 2 An electromagnetic member 3 for rotating the outer gear 2 is provided between the outer periphery of the housing member 1 and the inner periphery of the housing member 1. The electromagnetic member 3 includes a magnet 301 installed on the outer periphery of the housing member, and a coil 302 installed on the outer periphery of the outer gear 2 and positioned to dock with the magnet 301. The number of the magnets 301 is n, n≥12, and n is an integer multiple of 4. The number of the magnets 301 is n (n≥12, and n is an integer multiple of 4). Such a 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 the magnets 301 is the same as that of the coils 302, and there is a gap between the magnets 301 and the coils 302.

[0056] After the three-phase alternating current is introduced, a rotating magnetic field is formed around the magnet 301. Due to the different directions of the current introduced, the NS-level fluctuations of the magnetic field change, resulting in the effect of like-charge repulsion and opposite-charge attraction. This effect causes the outer gear 2 to be driven and start to rotate. Under the action of the rotating magnetic field, the outer gear 2 meshes with the inner gear 4 to achieve the suction and discharge of the liquid. The rotation speed and direction of the outer gear 2 are determined by the intensity and direction of the rotating magnetic field. Therefore, the output flow and pressure of the gear pump can be controlled by adjusting the magnitude and frequency of the current. During the change of the current of the coil 302, the direction of the magnetic field formed by the coil 302 alternates inward and outward near the magnet 301, and is densely distributed in the air gap of the coil 302, as shown in Figure 7, which can effectively provide torque.

[0057] An eccentrically arranged internal gear 4 is arranged on the inner periphery of the external gear 2, and rotating shafts 401 are respectively installed at both ends of the internal gear 4, and the other ends of the two rotating shafts 401 are respectively rotatably connected to the first sealing cover 12 and the second sealing cover 13, and a crescent plate 5 is arranged between the outer periphery of the internal gear 4 and the inner periphery of the external gear 2, and connecting shafts 501 are respectively arranged at both ends of the crescent plate 5, and the two connecting shafts 501 are respectively connected to the first sealing cover 12 and the second sealing cover 13, and 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, which 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, and realizing continuous suction and discharge of the liquid through the periodic increase and decrease of the volume;

[0058] The crescent plate 5 separates the non-meshing area between the outer gear 2 and the inner gear 4 into a liquid suction area 6 and a liquid pressure area 7. The crescent plate 5 can realize continuous suction, compression and discharge of the fluid by changing the fluid path, and is one of the decisive factors for the pump efficiency and working characteristics. 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 angle 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 central axis of the inner gear 4 are connected in the same first axial plane, one of the arc vertex angles 8 and the central axis of the inner gear 4 are connected in the second axial plane, and the other arc vertex angle 8 and the central axis of the inner gear 4 are connected in the third axial plane. An angle is set between the third axial plane and the reverse extension plane of the second axial plane, and the angle between the third axial plane and the reverse extension plane of the second axial plane is θ, and 0°≤ θ ≤ By adjusting the angle θ, the relative position of the crescent plate 5 in the liquid suction area 6 and the liquid pressing area 7 can be changed, thereby affecting the flow rate, pressure and efficiency of the pump.

[0059] 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 outer gear 2, and a first end cover 14 and a second end cover 15 connected to the heat dissipation shell 11; the heat dissipation shell 11 includes a pair of relatively arranged connecting seats 1101, the connecting seats 1101 not only play the role of connecting and supporting the ribs 1102, but also provide installation space for the electromagnetic member 3 and the outer gear 2, and a plurality of ribs 1102 are arranged between the pair of connecting seats 1101, the ribs 1102 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, and the design of the ribs 1102 optimizes the thermal conductivity of the heat dissipation shell 11 and improves the heat dissipation. Thermal efficiency, the magnet 301 is installed between the ribs 1102, so that the magnet 301 can directly perform heat dissipation treatment, a number of the ribs 1102 are equidistantly distributed along the end faces of a pair of the connecting seats 1101, and a number of the ribs 1102 are respectively provided with liquid channels 1103 with both ends penetrating the pair of the 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 the cooling liquid is discharged through the liquid discharge 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;

[0060] 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 the two 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 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;

[0061] The first end cover 14 and the second end cover 15 are respectively provided with a cavity structure 16, which is a key part of the cooling liquid circulation. They are not only connected to 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. The first end cover 14 and the second end cover 15 are docked and installed with the heat dissipation housing 11 to jointly form a closed space for the gear pump. The cavity structure 16 is a key part of the cooling liquid circulation. They are connected to the liquid flow channel 1103 to form a complete cooling circuit. The two ends of the liquid flow channel 1103 are respectively connected to the first end The cover 14 is connected to the cavity structure 16 on the second end cover 15, and the drainage hole 1202 is connected to the cavity structure 16. The first end cover 14 is provided with a liquid inlet pipe 1401, and one end of the liquid inlet pipe 1401 is connected to the liquid inlet hole 1201. The second end cover 15 is provided with a drainage pipe 1501, and one end of the drainage pipe 1501 is connected to the cavity structure 16 on the second end cover 15. The other end of the drainage pipe 1501 is connected to an external heat dissipation system or a cooling liquid recovery device, which is responsible for discharging the cooling liquid that completes the heat dissipation cycle out of the gear pump to realize the recycling of the cooling liquid.

[0062] An optimization method for a novel internal gear pump device with a self-heat dissipation function, the optimization method comprising the following steps:

[0063] The structural parameters of the gear pump device are analyzed, and the structural parameters of the gear pump device include the number of teeth and radius of the external gear 2 and the internal gear 4, the 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 angle θ between the third axial plane and the reverse extension plane of the second axial plane, assuming that the number of teeth of the external gear 2 is N1, the number of teeth of the internal gear 4 is N2, the radius of the external gear 2 is R, the chamfer of the crescent plate 5 is θ, and the thickness of the crescent plate 5 is H;

[0064] Based on the structural parameter range of the existing gear pump, the structural parameter range of the gear pump device is confirmed. The structural parameter range is as follows: Figure 8 As shown;

[0065] Using 3D modeling software, such as SolidWorks, CATIA, etc., according to 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, the inlet and outlet pressure tests are performed on the multiple virtual models, and the test data are compared with the inlet and outlet pressure test data of the existing gear pump, and the performance of each virtual model is evaluated by measuring the inlet and outlet pressure, flow rate and other performance indicators, and the virtual model with the best performance is selected as the basis for subsequent numerical simulation;

[0066] 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 Fig.10 and Fig.11 , it is determined that the chamfer angle θ=20° corresponding to the maximum flow rate, the flow velocity gradually increases under different chamfers, which also leads to an increase in flow rate, and when the chamfer 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 the fluid transport capacity. Similarly, since the left crescent plate 5 gradually becomes smooth, the internal flow field fluctuation gradually decreases, and as the chamfer continues to increase, the backflow effect causes the flow fluctuation to intensify, and the mean pressure difference gradually decreases under different chamfers, indicating that under the same outlet pressure, the inlet is less likely to generate negative pressure, and the torque of the motor is also smaller;

[0067] ANSYS Workbench is used to perform multi-field coupling numerical simulation of the internal and external characteristics of the motor-structure-flow channel multi-structure for the optimal performance virtual model. When performing multi-field coupling numerical simulation, the following parameter settings are required:

[0068] The inlet pressure is atmospheric pressure, i.e. 101.325 kPa;

[0069] The outlet pressure is 10MPa;

[0070] The rotation speed of the external gear 2 is 4800r / min;

[0071] The internal gear 4 rotates at a speed of 8000 r / min;

[0072] The density of the fluid is 844kg / m3;

[0073] Viscosity of the fluid: 0.0254 kg / (m·s);

[0074] 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 are obtained, and simulation data are extracted from ANSYS Workbench, including key performance indicators such as flow rate, pressure distribution, and torque;

[0075] By using the orthogonal experimental design principle, 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: Fig. 9 As shown;

[0076] Through the structural parameter matrix, combined with the simulation data, the simulation data with the closest performance is selected as the initial simulation data, which will serve as the starting point for the subsequent optimization algorithm;

[0077] 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 combination of structural parameters 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 Fig.12 As shown in the figure, 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. Fig.13 As shown, the magnetic field intensity distribution is relatively uniform and the rotor can run smoothly, so the optimized configuration is the optimal configuration.

[0078] Although embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and ideas of the present invention, and that the scope of the present invention is defined by the appended claims and their equivalents.

Claims

1. A new type of internal gear pump device with self-heating function, characterized in that: The invention comprises a shell member, an outer gear is arranged on the inner side of the shell member, an electromagnetic member for rotating the outer gear is arranged between the outer periphery of the outer gear and the inner periphery of the shell member, an eccentrically arranged inner gear is arranged on the inner periphery of the outer gear, a crescent plate is arranged between the outer periphery of the inner gear and the inner periphery of the outer gear, a central axis of the crescent plate is coaxially arranged with the central axis of the outer gear, the crescent plate separates the non-meshing area between the outer gear and the inner gear into a liquid suction area and a liquid pressing area, arc vertex angles located in the liquid suction area and the liquid pressing area are respectively arranged at two ends of the crescent plate, a line connecting the central axis of the crescent plate and the central axis of the inner gear is in the same first axial plane, a line connecting one of the arc vertex angles and the central axis of the inner gear is in the second axial plane, a line connecting the other arc vertex angle and the central axis of the inner gear is in the third axial plane, and an angle is arranged between the third axial plane and the reverse extension surface of the second axial plane.

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

3. A novel 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. A novel internal gear pump device with self-heat dissipation function according to claim 1, characterized in that: 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 connected to the heat dissipation shell; the heat dissipation shell includes a pair of relatively arranged connecting seats, a plurality of ribs are arranged between the pair of connecting seats, the plurality of ribs are equidistantly distributed along the circumferential direction of the end faces of the pair of connecting seats, and the plurality of ribs are respectively provided with liquid flow channels with both ends penetrating the pair of connecting seats.

5. A novel internal gear pump device with self-heat dissipation function according to claim 4, characterized in that: 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. 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.

6. A novel internal gear pump device with self-heat dissipation function according to claim 5, characterized in that: 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 drainage hole is connected to the cavity structure.

7. A novel internal gear pump device with self-heat dissipation function according to claim 4, 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.

8. A novel internal gear pump device with self-heat dissipation function according to claim 4, characterized in that: Rotating shafts are respectively 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. 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.

9. A novel internal gear pump device with self-heat dissipation function according to claim 4, characterized in that: The electromagnetic component includes a magnet installed between a number of adjacent rib plates, 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 magnet and the coil.

10. The method for optimizing the configuration of a novel internal gear pump device with self-heat dissipation function according to claim 1, characterized in that: The optimization method comprises the following steps: Analyze the structural parameters of the gear pump device, which include 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 inlet and outlet pressure experiments of the multiple virtual models are compared with the existing gear pump to select the virtual model with the best performance; Use ANSYS Workbench to perform multi-field coupling numerical simulation of the internal and external characteristics of the motor-structure-flow channel multi-structure on the virtual model with the best performance. After the multi-field coupling numerical simulation is completed, extract the simulation data from ANSYS Workbench; By using the orthogonal experimental design principle, representative parameter combinations are selected from the initially 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; Through the MATLAB platform, the CG genetic algorithm is used to perform multiple iterations of optimization on the initial simulation data 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.

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