A pump body, cooling equipment and vehicle

Abstract

This application relates to a pump body, cooling equipment, and vehicle. The pump body includes a power assembly, a transmission assembly, and a pump head assembly. The power assembly includes a stator structure and a rotor structure. The transmission assembly includes a shaft. The shaft of the transmission assembly is disposed within the rotor structure and does not enter the interior of the stator structure. This eliminates the need for the stator structure to provide space for the shaft and rotor structure, reducing the circumferential space required. Furthermore, the second end of the shaft is fixedly connected to the pump head assembly, reducing the space required for transmission components such as the reducer, further saving internal space and making the structure more compact. This application effectively solves the problem that existing pump bodies are not compact enough, have a large overall size, and occupy a large amount of space.

Description

Technical Field

[0001] This application relates to the technical field of electronic pumps, and more particularly to a pump body, cooling equipment, and vehicle. Background Technology

[0002] New energy vehicles represent the future of automobiles, and numerous manufacturers are gradually developing them. Currently, battery-powered motors are the mainstream approach for new energy vehicles. The biggest challenges in using batteries as an energy source are energy storage and charging. To achieve longer driving ranges, increasing battery capacity has become a primary focus. However, increasing battery capacity leads to issues such as larger battery size and the need for reliable temperature control. Therefore, a reliable temperature control system must be installed within the limited space of the vehicle to ensure safe operation.

[0003] In existing technologies, oil cooling is commonly used to control the temperature of vehicle energy storage batteries, and the key to oil cooling technology lies in the oil pump supply. To save space in the oil cooling system, the oil pump is installed inside the oil cylinder, thereby reducing the size of the cooling equipment. Existing oil pumps typically use a radial flux motor as the power source. A drive shaft and multiple bearings are required between the pump body and the motor. Due to the fit between the stator and rotor inside the motor, a relatively large assembly space is needed, resulting in a large overall size of the oil pump and a significant space requirement. Summary of the Invention

[0004] This application provides a pump body, cooling equipment, and vehicle to solve the problem that existing pump bodies are not compact enough, have a large overall size, and occupy a lot of space.

[0005] In a first aspect, this application provides a pump body, including: a power assembly, a transmission assembly, and a pump head assembly. The power assembly includes a stator structure and a rotor structure, the rotor structure and the stator structure having the same axis, and a gap is provided between the rotor structure and the stator structure along the axis direction. The transmission assembly includes a shaft, the first end of which is disposed inside the rotor structure and is fixedly connected to the rotor structure. The pump head assembly is fixedly connected to the second end of the shaft.

[0006] Furthermore, the stator structure includes multiple stator cores, and the rotor structure includes a rotor base and multiple magnets. The multiple stator cores are arranged around the axis, and the multiple magnets are fixedly connected to the rotor base.

[0007] Furthermore, the stator structure also includes a winding wire group, where the magnets are attached to the side of the rotor seat facing the stator core, the magnetic flux path direction of the magnets is parallel to the direction of the axis, the magnetic flux path directions of adjacent magnets are opposite, and the winding wire groups of adjacent stator cores are wound in opposite directions.

[0008] Furthermore, multiple magnets are arranged in a ring-shaped Heilbeck array, and the multiple magnets and rotor base are integrated into a single structure.

[0009] Furthermore, the power assembly also includes a mounting base and a control structure, and the stator structure also includes a winding wire assembly. The mounting base has multiple mounting positions on the side facing the stator structure, and the mounting positions are used for mounting the stator structure. A partition structure is provided between the mounting base and the control structure, and the winding wire assembly passes through the partition structure and is electrically connected to the control structure.

[0010] Furthermore, the transmission assembly also includes an axial contact bearing and a bearing mounting base, with the axial contact bearing installed within the bearing mounting base and the shaft passing through the axial contact bearing.

[0011] Furthermore, the axial contact bearing is a thrust ball bearing.

[0012] Furthermore, the thrust ball bearing includes a housing ring and a bearing ring, and the bearing mounting housing includes a first bearing chamber and a second bearing chamber. The diameter of the first bearing chamber is smaller than the diameter of the second bearing chamber. The outer ring of the housing ring is interference-fitted with the first bearing chamber, the inner ring of the housing ring is clearance-fitted with the shaft body, the outer ring of the bearing ring is clearance-fitted with the second bearing chamber, and the inner ring of the bearing ring is interference-fitted with the shaft body.

[0013] Furthermore, the transmission assembly also includes a washer, which is disposed between the axial contact bearing and the pump head assembly.

[0014] Furthermore, the pump head assembly includes an external gear, an internal gear, and a first housing. Both the external gear and the internal gear are disposed within the first housing. The external gear is fixedly connected to the shaft. The distance between the axis of the internal gear and the axis of the external gear is greater than or equal to the difference between the tip circle diameter and the root circle diameter of the internal gear. The external gear and the internal gear have a meshing position.

[0015] Furthermore, the pump head assembly also includes a pump head cover, which is fixedly connected to the first housing. The pump head cover includes a first partition and a second partition. The first partition is located at the meshing position and is connected to the external gear and the internal gear respectively. The second partition is located at the maximum clearance position between the external gear and the internal gear and is connected to the external gear and the internal gear on both sides of the clearance position respectively.

[0016] Furthermore, the pump head cover also includes a fluid inlet and a fluid outlet. The fluid inlet is located on the side wall of the pump head cover, and the fluid inlet, the first partition and the second partition form a liquid inlet chamber. The fluid outlet is located at the end of the pump head cover away from the first housing, and the fluid outlet, the first partition and the second partition form a liquid outlet chamber.

[0017] Furthermore, the first baffle is inclined from the liquid outlet chamber to the liquid inlet chamber along the axial direction of the pump head cover away from the first housing.

[0018] Furthermore, the power assembly also includes a second housing, in which both the stator and rotor structures are housed. The bearing mounting base is integrally formed with the first housing, and the second housing is connected to the end of the first housing where the bearing mounting base is located via fasteners.

[0019] Secondly, this application provides a cooling device, which includes a pump body and a cooling pipeline, wherein the pump body is used for circulation in the cooling pipeline.

[0020] Thirdly, this application provides a vehicle that includes the aforementioned cooling equipment.

[0021] The technical solutions provided in this application have the following advantages compared with the prior art:

[0022] This application provides a pump body, cooling equipment, and vehicle. The pump body includes a power assembly, a transmission assembly, and a pump head assembly. The power assembly includes a stator structure and a rotor structure, which share the same axis and have a gap along the axis. The transmission assembly includes a shaft, with its first end located within the rotor structure and fixedly connected to it. The pump head assembly is fixedly connected to the second end of the shaft. This arrangement minimizes the space occupied by the rotor and stator structures along the axis. Furthermore, the shaft's location within the rotor structure, avoiding entry into the stator structure, eliminates the need for space in the stator to accommodate the shaft and rotor structure, reducing circumferential space requirements. The fixed connection of the second end of the shaft to the pump head assembly further reduces the space required for transmission components such as the reducer, resulting in a more compact structure. This application effectively solves the problems of existing pump bodies being insufficiently compact, having a large overall size, and occupying significant space. Attached Figure Description

[0023] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with the invention and, together with the description, serve to explain the principles of the invention.

[0024] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, for those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0025] Figure 1 This shows a front view schematic diagram of a pump body provided in Embodiment 1 of this application;

[0026] Figure 2 It shows Figure 1 A cross-sectional view of the pump body along the AA direction;

[0027] Figure 3 It shows Figure 2 A partially enlarged schematic diagram of the pump body;

[0028] Figure 4 It shows Figure 1 A three-dimensional structural diagram of the pump body;

[0029] Figure 5 It shows Figure 1 Right view of the pump body;

[0030] Figure 6 It shows Figure 1 Front view of the pump head cover of the pump body;

[0031] Figure 7 It shows Figure 6 Rear view of the pump head cover;

[0032] Figure 8 It shows Figure 6 A cross-sectional view of the pump head cover along the CC direction;

[0033] Figure 9 A cross-sectional schematic diagram of a pump body provided in Embodiment 2 of this application is shown.

[0034] The above figures include the following reference numerals:

[0035] 10. Power assembly; 11. Stator structure; 111. Stator core; 112. Winding wire assembly; 12. Rotor structure; 121. Rotor seat; 122. Magnet; 13. Clearance; 14. Mounting seat; 15. Control structure; 16. Partition structure; 17. Second housing; 20. Transmission assembly; 21. Shaft; 211. Fluid passage; 22. Contact bearing; 221. Seat ring; 222. Bearing ring; 23. Bearing mounting seat; 231. First bearing chamber; 232. Second bearing chamber; 24. Washer ring; 30. Pump head assembly; 31. External gear; 32. Internal gear; 33. First housing; 34. Pump head cover; 341. First partition; 342. Second partition; 343. Fluid inlet; 344. Fluid outlet; 345. Motor inlet. Detailed Implementation

[0036] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0037] like Figures 1 to 5 As shown, in the first aspect, the technical solution of Embodiment 1 of this application provides a pump body, including: a power assembly 10, a transmission assembly 20, and a pump head assembly 30. The power assembly 10 includes a stator structure 11 and a rotor structure 12. The rotor structure 12 and the stator structure 11 have the same axis, and a gap 13 is provided between the rotor structure 12 and the stator structure 11 along the axis direction. The transmission assembly 20 includes a shaft 21. The first end of the shaft 21 is disposed in the rotor structure 12, and the shaft 21 is fixedly connected to the rotor structure 12. The pump head assembly 30 is fixedly connected to the second end of the shaft 21. This configuration minimizes the space occupied by the rotor structure 12 and stator structure 11 along the axial direction. Simultaneously, the shaft 21 is positioned within the rotor structure 12, not entering the stator structure 11, eliminating the need for space in the stator structure 11 to accommodate the shaft 21 and rotor structure 12. This reduces the circumferential space required in the stator structure 11. Furthermore, the second end of the shaft 21 is fixedly connected to the pump head assembly 30, reducing the space required for transmission components such as the reducer, further saving internal space and resulting in a more compact structure. This application effectively solves the problem of existing pump bodies having insufficient compactness, large overall size, and occupying significant space. It should be noted that the gap 13 is designed to allow space for the rotor structure 12 to move along the axial direction, preventing direct contact between the rotor structure 12 and stator structure 11. Simultaneously, the fixed connection of the shaft 21 to the pump head assembly 30, along with these other features, ensures that the rotor structure 12 will not directly contact the stator structure 11 even under large axial forces, guaranteeing that the positional relationship between the stator structure 11 and rotor structure 12 remains in a working state.

[0038] In the technical solution of Embodiment 1 (not shown in the figure), the stator structure 11 includes multiple stator cores 111, and the rotor structure 12 includes a rotor base 121 and multiple magnets 122. The multiple stator cores 111 are arranged around an axis, and the multiple magnets 122 are fixedly connected to the rotor base 121. The arrangement of multiple stator cores 111 facilitates the setting of different winding wire groups 112. Different winding directions generate different magnetic fields, thereby driving the rotor base 121 to rotate. The arrangement of multiple magnets 122 corresponds to the multiple stator cores 111. The magnets 122 are permanent magnets that can generate a fixed magnetic field, which cooperates with the changing magnetic field generated by the stator cores 111 to drive the rotor base 121 to rotate.

[0039] like Figure 2 and Figure 3As shown, in the technical solution of Embodiment 1, multiple magnets 122 are arranged in a ring-shaped Hellbeck array, and the multiple magnets 122 and the rotor seat 121 are integrally formed. The magnet structure arranged in a ring-shaped Hellbeck array can generate a strong magnetic field. The superposition of the parallel magnetic field and the radial magnetic field after the multiple magnets 122 are decomposed greatly increases the magnetic field strength on the other side. The structure is simple, reliable, and the process is simplified. At the same time, since the pump body needs to be immersed in liquid, specifically cooling oil, the shaft 21 is provided with a fluid passage 211 along the axis. The oil enters the second housing 17 through the fluid passage 211, which can cool the stator structure 11 and the rotor structure 12 to a certain extent. In this application, since the magnets 122 and the rotor seat 121 are integrally formed, specifically in a disc shape, there is no side gap. When the rotor structure 12 rotates, the friction between the rotor structure 12 and the oil is small, thereby reducing fluid loss. It should be noted that the rotor base 121 and the magnet 122 are integrally molded and combined by injection molding. The rotor base 121 can be made of metal and bonded to the magnet 122 by magnetic force. This arrangement can ensure a tight bond between the rotor base 121 and the magnet 122 due to magnetic force. Alternatively, the rotor base 121 can be made of non-metallic material and directly integrally molded with the magnet 122 by injection molding, which can reduce production steps and lower production costs.

[0040] It should be noted that, due to the self-shielding effect of the magnets 122 arranged in a ring-shaped Hellbeck array, the unilateral magnetic field distribution no longer requires the rotor to use magnetic materials to provide a path. This not only provides a larger selection space for rotor materials but also allows the system to have lower rotational inertia and better rapid response performance. Compared with the traditional permanent magnet motor architecture, the superposition of the parallel magnetic field and radial magnetic field after the decomposition of the magnets 122 arranged in a ring-shaped Hellbeck array significantly increases the magnetic field strength on the other side. This effectively reduces the volume of the power assembly 10 and increases its power density.

[0041] The magnets 122, arranged in a ring-shaped Hellbeck array, have no magnetic field passing through the side facing the stator structure 11, while the side facing away from the stator structure 11 does. Therefore, a magnetically conductive rotor base 121 is not required on the bottom surface. This reduces the number of parts, making the structure more compact and lighter, and also reduces the process of attaching the magnets 122, thus improving product reliability. Furthermore, the regular cylindrical shape significantly reduces flow resistance losses between the rotor and the oil during operation. Specifically, in traditional rotor base 121 and magnet-attached 122 designs, the irregular shape of the magnets 122 causes them to agitate the oil during rotor structure 12 operation, resulting in flow resistance losses. As the rotational speed increases, the oil temperature decreases, and the viscosity increases, this flow resistance rises sharply, significantly reducing oil pump efficiency. This design improves overall product efficiency.

[0042] like Figure 2 and Figure 3 As shown, in the technical solution of Embodiment 1, the power assembly 10 further includes a mounting base 14 and a control structure 15, and the stator structure 11 further includes a winding wire assembly 112. The mounting base 14 has multiple mounting positions on the side facing the stator structure 11, which are used for mounting the stator structure 11. A partition structure 16 is provided between the mounting base 14 and the control structure 15. The winding wire assembly 112 passes through the partition structure 16 and is electrically connected to the control structure 15. The partition structure 16 is used to isolate the control structure 15 from the oil. The control structure 15 is fixedly connected to the partition structure 16. The periphery of the partition structure 16 transitions with the inner wall of the second housing 17 to prevent the passage of oil. Specifically, a waterproof gasket can also be provided on the periphery of the partition structure 16 to increase the sealing performance of the partition structure 16 during installation and prevent damage to the control structure 15.

[0043] like Figure 2 and Figure 3 As shown, in the technical solution of Embodiment 1, the transmission assembly 20 further includes an axial contact bearing 22 and a bearing mounting base 23. The axial contact bearing 22 is installed in the bearing mounting base 23, and the shaft 21 passes through the axial contact bearing 22. Since there is a large axial tensile force between the rotor structure 12 and the stator structure 11, this means that the rotor structure 12 needs to overcome a large resistance when rotating. This reduces the pump's output efficiency and generates frictional heat, causing a large amount of heat to be generated inside the pump, severely affecting the pump's operation. The axial contact bearing 22 is designed to withstand the axial tensile force, preventing the rotor structure 12 from pulling the pump head assembly 30 towards the stator structure 11 when rotating. Simultaneously, the axial contact bearing 22 can rotate together with the shaft 21 under load. The rotation direction component then becomes the resistance to the rotation of the axial contact bearing 22 itself, which is relatively smaller than the resistance directly overcome by the rotor structure 12, and also avoids generating a large amount of frictional heat.

[0044] like Figure 2 and Figure 3As shown, in the technical solution of Embodiment 1, the axial contact bearing 22 is a thrust ball bearing. Compared to thrust bearings using rollers, thrust ball bearings can withstand larger loads and are more suitable for the technical solution of Embodiment 1. Specifically, the thrust ball bearing is a one-way thrust ball bearing, arranged within the bearing mounting seat 23. Simultaneously, the power assembly 10 and pump head assembly 30 are integrated. After assembly, the relative positions of the internal gear 32, shaft 21, and rotor structure 12 are fixed; that is, the shaft 21 is press-fitted with the internal gear 32, and with the rotor structure 12, using a press-fit process. Due to the axial tension, a very small axial space needs to be reserved between the rotor structure 12 and the second housing 17 to ensure they do not contact each other during operation. This makes the entire pump body very compact in the axial space. Furthermore, this arrangement makes the weight on both sides of the thrust ball bearing relatively balanced, which improves the stability of the pump body operation to a certain extent. Since a one-way thrust ball bearing itself requires axial pressure to operate, this is equivalent to using the axial tension of the power assembly 10, which solves both the problem of applying axial preload to the one-way thrust ball bearing and the problem of friction between the internal gear and the housing caused by the axial tension.

[0045] like Figure 2 and Figure 3 As shown, in the technical solution of Embodiment 1, the thrust ball bearing includes a housing ring 221 and a bearing ring 222. The bearing mounting base 23 includes a first bearing chamber 231 and a second bearing chamber 232. The diameter of the first bearing chamber 231 is smaller than the diameter of the second bearing chamber 232. The outer ring of the housing ring 221 is interference-fitted with the first bearing chamber 231, and the inner ring of the housing ring 221 is clearance-fitted with the shaft body 21. The outer ring of the bearing ring 222 is clearance-fitted with the second bearing chamber 232, and the inner ring of the bearing ring 222 is interference-fitted with the shaft body 21. This arrangement allows the bearing ring 222 to be fixedly connected to the bearing mounting base 23, and the housing ring 221 to be fixedly connected to the shaft body 21. The housing ring 221 is rotatably connected to the bearing ring 222 via balls. With the bearing ring 222 fixed, the shaft body 21 is not radially restricted. At the same time, the axial tensile force is applied to the balls and the bearing ring 222 through the housing ring to transfer the axial tensile force and reduce the resistance experienced by the shaft body 21. The diameter of the first bearing chamber 231 is smaller than the diameter of the second bearing chamber 232, and the diameter of the bearing ring 222 is smaller than the diameter of the seat ring 221. The diameter of the first bearing chamber 231 is smaller, and there is a transition fit between the first bearing chamber 231 and the bearing ring 222. This arrangement can prevent the seat ring 221 from sliding into the first bearing chamber 231. A step is formed between the first bearing chamber 231 and the second bearing chamber 232, and the seat ring 221 cannot cross the step to enter the first bearing chamber 231. This can protect the thrust ball bearing from being crushed and also prevent damage to the bearing mounting seat 23.

[0046] like Figure 2 and Figure 3 As shown, in the technical solution of Embodiment 1, the transmission assembly 20 further includes a washer 24, which is disposed between the axial contact bearing 22 and the pump head assembly 30. The washer 24 prevents the pump head assembly 30 from directly contacting the axial contact bearing 22, thus preventing displacement of either the pump head assembly 30 or the axial contact bearing 22, which could lead to failure of the axial contact bearing 22. Specifically, the washer 24 can be made of an elastic material and contacts the inner wall of the second bearing chamber 232. The elastic material provides a pressure-resistant function, preventing the pump head assembly 30 from directly contacting the bearing mounting seat 23 under axial tension, which could damage the pump head assembly 30. Simultaneously, the elastic material has a certain sealing capability, preventing particles in the oil from directly entering the gap between the axial contact bearing 22 and the bearing mounting seat 23, thereby preventing failure of the axial contact bearing 22.

[0047] like Figure 1 , Figure 2 as well as Figures 4 to 8 As shown, in the technical solution of Embodiment 1, the pump head assembly 30 includes an external gear 31, an internal gear 32, and a first housing 33. Both the external gear 31 and the internal gear 32 are disposed within the first housing 33. The external gear 31 is fixedly connected to the shaft 21. The distance between the axis of the internal gear 32 and the axis of the external gear 31 is greater than or equal to the difference between the tip circle diameter and the root circle diameter of the internal gear 32. The external gear 31 and the internal gear 32 have a meshing position. This arrangement allows the external gear 31 and the internal gear 32 to form a cyclic process where the gap gradually increases and then decreases. At the meshing position, the gap between the external gear 31 and the internal gear 32 is minimal, thus achieving the pump's function of suction and discharge. Specifically, the external gear 31 is fixed to the shaft 21, and the first housing 33 has a mounting cavity that is clearance-fitted with the internal gear 32. The process from the meshing position to the maximum clearance between the external gear 31 and the internal gear 32 is the suction process, where liquid is drawn in by gradually increasing clearance. The process from the maximum clearance between the external gear 31 and the internal gear 32 back to the meshing position is the discharge process, where oil is squeezed out by gradually decreasing clearance. The precise fit between the external gear 31 and the internal gear 32 ensures stable output efficiency. It should be noted that the tooth thicknesses of the external gear 31 and the internal gear 32 are equal. This arrangement facilitates pump body sealing and the arrangement of other mating components, while also reducing the larger axial dimension of the first housing 33 caused by the thickness difference between the two gears, further reducing the overall size of the pump body.

[0048] like Figure 1 , Figure 2 as well as Figures 4 to 8As shown, in the technical solution of Embodiment 1, the pump head assembly 30 further includes a pump head cover 34, which is fixedly connected to the first housing 33. The pump head cover 34 includes a first partition 341 and a second partition 342. The first partition 341 is located at the meshing position and is connected to the external gear 31 and the internal gear 32 respectively. The second partition 342 is located at the maximum gap position between the external gear 31 and the internal gear 32 and is connected to the external gear 31 and the internal gear 32 on both sides of the gap position respectively. The arrangement of the first partition 341 and the second partition 342 separates the liquid suction process and the liquid discharge process of the pump body. When the second partition 342 is at the maximum gap position between the external gear 31 and the internal gear 32, it surrounds the oil between the external gear 31, the internal gear 32 and the first housing 33, preventing the liquid inlet process from communicating with the liquid discharge process at the maximum gap position, thus ensuring the smooth operation of the liquid suction process and the liquid discharge process.

[0049] like Figure 1 , Figure 2 as well as Figures 4 to 8 As shown, in the technical solution of Embodiment 1, the pump head cover 34 further includes a fluid inlet 343 and a fluid outlet 344. The fluid inlet 343 is disposed on the side wall of the pump head cover 34, and the fluid inlet 343, the first partition 341, and the second partition 342 form an inlet chamber. The fluid outlet 344 is disposed at the end of the pump head cover 34 away from the first housing 33, and the fluid outlet 344, the first partition 341, and the second partition 342 form an outlet chamber. The formation of the inlet chamber can increase the amount of oil prepared. When the pump body needs to discharge liquid outward with high efficiency, it can reduce the oil flow rate at the inlet position to a certain extent, thereby reducing the fluid pressure received by the pump head cover 34 and extending the service life of the pump body. The arrangement of the outlet chamber is similar to that of the inlet chamber. The structure of the chamber can accommodate more oil, avoiding excessive oil and causing too much oil at the outlet end of the pump body. On the one hand, it can protect the pump head assembly 30, and on the other hand, it can reduce the overall pressure at the outlet end so as not to be too high, avoiding damage to the power assembly 10 and the transmission assembly 20. It should be noted that the pump head cover 34 is also provided with a motor liquid inlet 345, which is connected to the fluid passage 211 to connect the stator structure 11 and the rotor structure 12, thereby realizing the cooling of the stator structure 11 and the rotor structure 12.

[0050] like Figure 6 and Figure 8As shown, in the technical solution of Embodiment 1, the first partition 341 is inclined along the axis of the pump head cover 34 away from the first housing 33, and is arranged from the liquid outlet chamber to the liquid inlet chamber. The inclined first partition 341 can reduce the liquid inlet chamber and expand the liquid outlet chamber. This arrangement can reduce the volume of oil in the liquid inlet chamber at the location where the first partition 341 is located, and avoid excessive oil squeezing the external gear 31, which would cause a gap in the meshing between the external gear 31 and the internal gear 32, leading to pump failure. At the same time, expanding the liquid outlet chamber can further reduce the fluid pressure in the liquid outlet chamber.

[0051] like Figure 1 , Figure 2 , Figure 4 and Figure 5 As shown, in the technical solution of Embodiment 1, the power assembly 10 also includes a second housing 17. The stator structure 11 and the rotor structure 12 are both disposed within the second housing 17. The bearing mounting seat 23 and the first housing 33 are integrally formed. The second housing 17 is connected to one end of the first housing 33 where the bearing mounting seat 23 is disposed by fasteners. The integral formation of the bearing mounting seat 23 and the first housing 33 further reduces the size of the pump body in the axial direction. The separate design of the first housing 33 and the second housing 17 means that there is a great deal of freedom in selecting the outer diameter of the stator structure 11 and the rotor structure 12, which allows for easy increase or decrease in the volume of the power assembly 10, thereby changing the power of the power assembly 10. On the other hand, since the control structure 15 is made of a PCB board, and the power of the PCB is closely related to its area, if the outer diameter of the stator structure 11 can be freely selected, it means that the power of the PCB can also be made larger. This is much more flexible than the usual integrated design of the pump housing and the machine housing. In addition, when setting up a gearbox or reducer, the axial space reserved for the electronic oil pump is usually sufficient, but the radial space is insufficient. The first housing 33 and the second housing 17 are designed separately. The axial dimension of the first housing 33 can be made as small as possible, while the axial dimension of the second housing 17 can be made as large as possible. Therefore, the pump body has stronger adaptability in installation.

[0052] like Figure 9As shown in Embodiment 2 of this application, the magnet 122 is attached to the side of the rotor base 121 facing the stator core 111. The magnetic flux path direction of the magnet 122 is parallel to the direction of the axis, the magnetic flux path directions of adjacent magnets 122 are opposite, and the winding directions of adjacent stator cores 111 are opposite. Embodiment 2 attaches the magnet 122 to the rotor base 121 according to a certain pattern. This arrangement facilitates assembly, and the magnetic field can be adjusted and changed by changing the thickness of the magnet 122. Furthermore, assembly is more convenient, and disassembly and maintenance are also easier. It should be noted that the rotor base 121 can be made of metal material to generate magnetic force with the magnet 122, and then be attached by other fixing methods, such as fasteners or adhesives. This arrangement ensures that the rotor base 121 and the magnet 122 achieve an initial bond due to magnetic force, and then further tighten the bond with fasteners or adhesives, ensuring that the magnet 122 is firmly attached to the rotor base 121. Alternatively, the rotor base 121 can be made of non-metallic material, and the magnet 122 can be wrapped by injection molding, directly forming a single piece. This reduces production steps and lowers production costs. The power components 10 in this application are all powered by DC power, which is in line with the use in the vehicle industry, especially the new energy vehicle industry.

[0053] Secondly, this application provides a cooling device, which includes a pump body and cooling pipes. The pump body, as described above, is used for circulation in the cooling pipes. By using the pump body as the power source for the cooling device's pipes, the size of the cooling device is minimized while ensuring its power output.

[0054] Thirdly, this application provides a vehicle that includes the aforementioned cooling device. The aforementioned cooling device can be used for temperature control of vehicle components, and its smaller size makes it more suitable for the complex environment inside the vehicle body. Furthermore, the reduced size allows for the installation of other components, making it more suitable for the development of the vehicle industry.

[0055] It should be noted that, in this document, relational terms such as "first" and "second" are used merely to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

[0056] The above description is merely a specific embodiment of the present invention, enabling those skilled in the art to understand or implement the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the invention. Therefore, the present invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features claimed herein.

Claims

1. A pump body, characterized in that, include: The power assembly (10) includes a stator structure (11) and a rotor structure (12), the rotor structure (12) and the stator structure (11) having the same axis, and a gap (13) is provided between the rotor structure (12) and the stator structure (11) along the direction of the axis; The transmission assembly (20) includes a shaft (21), the first end of which is disposed in the rotor structure (12), and the shaft (21) is fixedly connected to the rotor structure (12). Pump head assembly (30), the pump head assembly (30) being fixedly connected to the second end of the shaft (21); The stator structure (11) includes multiple stator cores (111), and the rotor structure (12) includes a rotor base (121) and multiple magnets (122). The multiple stator cores (111) are arranged around the axis, and the multiple magnets (122) are fixedly connected to the rotor base (121). The multiple magnets (122) are arranged around the axis. The plurality of magnets (122) are arranged in a ring-shaped Heilbeck array, and the plurality of magnets (122) and the rotor base (121) are integrally formed. The shaft (21) is provided with a fluid passage (211) along its axis; The transmission assembly (20) further includes an axial contact bearing (22) and a bearing mounting base (23), wherein the axial contact bearing (22) is installed in the bearing mounting base (23), and the shaft (21) passes through the axial contact bearing (22); The axial contact bearing (22) is a thrust ball bearing.

2. The pump body according to claim 1, characterized in that, The stator structure (11) further includes a winding wire group (112). The magnet (122) is attached to the side of the rotor seat (121) facing the stator core (111). The magnetic flux path direction of the magnet (122) is parallel to the direction of the axis. The magnetic flux path directions of adjacent magnets (122) are opposite. The winding directions of the winding wire groups (112) of adjacent stator cores (111) are opposite.

3. The pump body according to claim 1, characterized in that, The power assembly (10) also includes a mounting base (14) and a control structure (15). The stator structure (11) also includes a winding wire group (112). The mounting base (14) has multiple mounting positions on the side facing the stator structure (11). The mounting positions are used for mounting the stator structure (11). A partition structure (16) is provided between the mounting base (14) and the control structure (15). The winding wire group (112) passes through the partition structure (16) and is electrically connected to the control structure (15).

4. The pump body according to claim 1, characterized in that, The thrust ball bearing includes a seat ring (221) and a bearing ring (222). The bearing mounting base (23) includes a first bearing chamber (231) and a second bearing chamber (232). The diameter of the first bearing chamber (231) is smaller than the diameter of the second bearing chamber (232). The outer ring of the seat ring (221) is interference-fitted with the first bearing chamber (231). The inner ring of the seat ring (221) is clearance-fitted with the shaft body (21). The outer ring of the bearing ring (222) is clearance-fitted with the second bearing chamber (232). The inner ring of the bearing ring (222) is interference-fitted with the shaft body (21).

5. The pump body according to claim 1, characterized in that, The transmission assembly (20) further includes a washer (24) disposed between the axial contact bearing (22) and the pump head assembly (30).

6. The pump body according to claim 1, characterized in that, The pump head assembly (30) includes an external gear (31), an internal gear (32), and a first housing (33). The external gear (31) and the internal gear (32) are both disposed in the first housing (33). The external gear (31) is fixedly connected to the shaft (21). The distance between the axis of the internal gear (32) and the axis of the external gear (31) is greater than or equal to the difference between the tip circle diameter and the root circle diameter of the internal gear (32). The external gear (31) and the internal gear (32) have a meshing position.

7. The pump body according to claim 6, characterized in that, The pump head assembly (30) further includes a pump head cover (34), which is fixedly connected to the first housing (33). The pump head cover (34) includes a first partition (341) and a second partition (342). The first partition (341) is disposed at the meshing position and is connected to the external gear (31) and the internal gear (32) respectively. The second partition (342) is disposed at the maximum clearance position between the external gear (31) and the internal gear (32) and is connected to the external gear (31) and the internal gear (32) on both sides of the maximum clearance position respectively.

8. The pump body according to claim 7, characterized in that, The pump head cover (34) further includes a fluid inlet (343) and a fluid outlet (344). The fluid inlet (343) is disposed on the side wall of the pump head cover (34). The fluid inlet (343), the first partition (341) and the second partition (342) form a liquid inlet chamber. The fluid outlet (344) is disposed at one end of the pump head cover (34) away from the first housing (33). The fluid outlet (344), the first partition (341) and the second partition (342) form a liquid outlet chamber.

9. The pump body according to claim 8, characterized in that, The first partition (341) is arranged at an angle from the outlet chamber toward the inlet chamber along the axial direction of the pump head cover (34) away from the first housing (33).

10. The pump body according to claim 6, characterized in that, The power assembly (10) also includes a second housing (17), in which the stator structure (11) and the rotor structure (12) are both disposed. The bearing mounting seat (23) and the first housing (33) are integrally formed. The second housing (17) is connected to one end of the first housing (33) where the bearing mounting seat (23) is disposed by fasteners.

11. A cooling device, characterized in that, The cooling device includes a pump body and cooling pipes, wherein the pump body is the pump body according to any one of claims 1 to 10, and the pump body is used for circulation in the cooling pipes.

12. A vehicle, characterized in that, The vehicle includes the cooling device as described in claim 11.

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