Heat dissipation system and disc motor

Abstract

The application relates to a heat dissipation system and a disc motor. The heat dissipation system comprises a machine shell, a wind guide cover and an air flow driving assembly. The machine shell comprises a front shell and a rear shell which are butted along the axial direction. The wind guide cover is arranged at the periphery of the machine shell, and a front air duct is formed between the wind guide cover and the machine shell at a position corresponding to the periphery of the front shell, and a rear air duct is formed between the wind guide cover and the machine shell at a position corresponding to the periphery of the rear shell. The wind guide cover is provided with opposite air inlets and air outlets at positions corresponding to the circumferential side of the machine shell. The front air duct and the rear air duct are connected with the air inlets at the starting ends and connected with the air outlets at the ending ends. The air flow driving assembly is arranged at the air inlets or the air outlets to drive the air flow to flow into the front air duct and the rear air duct from the air inlets respectively and flow out from the air outlets. In this way, the air cooling heat dissipation mode of the heat dissipation system can not only reduce the temperature difference between the front stator and the rear stator, so that the temperature rise of the disc motor is more uniform, but also can make the assembly universality of the disc motor stronger.

Description

Technical Field

[0001] This invention relates to the field of disc motor technology, and more particularly to a heat dissipation system and a disc motor. Background Technology

[0002] Disc motors typically use permanent magnets as rotors and iron core windings as stators. To counteract the axial unilateral magnetic pull caused by a single stator, a dual-stator structure is usually used to ensure force balance.

[0003] Disc motors generate heat during operation, which is typically dissipated using air cooling. Under normal operating conditions, disc motors often employ forced air cooling with rear-end air intake and axial forward airflow. In this airflow mode, the cooling airflow first passes through the rear stator and then through the front stator, resulting in significantly worse heat dissipation in the front stator compared to the rear stator. This leads to a noticeable temperature difference between the front and rear stators, with a higher temperature rise in the front stator region.

[0004] Furthermore, in the assembly scenario where the motor is mounted on the front flange, the ventilation outlet of the air-cooled structure at the front of the motor is blocked, causing the airflow to change direction significantly at this point. The airflow velocity at the front root is low, further worsening the heat dissipation conditions of the front stator. Summary of the Invention

[0005] The main objective of this invention is to propose a heat dissipation system and a disc motor, which aims to solve the problem that the air supply mode of the existing air-cooled structure easily causes a large difference in heat dissipation conditions between the front and rear stators and a significant temperature difference between the front and rear stators.

[0006] To achieve the above objectives, the present invention proposes a heat dissipation system for use in a disc motor, comprising: The housing, including a front housing and a rear housing joined together along its axial direction; An air guide shroud is disposed on the periphery of the housing, forming a front air duct at a position corresponding to the periphery of the front housing and a rear air duct at a position corresponding to the periphery of the rear housing; the air guide shroud has opposing air inlets and outlets at positions corresponding to the periphery of the housing; the starting ends of the front air duct and the rear air duct are connected to the air inlets, and the ending ends of the front air duct and the rear air duct are connected to the air outlets; and, An airflow driving component is located at the air inlet or the air outlet to drive airflow from the air inlet into the front air duct and the rear air duct respectively, and out of the air outlet.

[0007] Optionally, the front air duct and the rear air duct are spatially interconnected; and / or, The flow boundaries of the front air duct and / or the rear air duct are jointly defined by the inner wall of the air guide shroud and the outer wall of the housing.

[0008] Optionally, the projection of the air inlet onto the housing has an area equal to the area of ​​its projection onto the front housing and the area of ​​its projection onto the rear housing; and / or, The projection of the air outlet onto the housing has an area that falls into the front housing and an area that falls into the rear housing that are equal; and / or, The air inlet area is smaller than the air outlet area.

[0009] Optionally, the central axis of the air inlet and the central axis of the air outlet are collinear, and their common axis passes through the geometric center of the housing and intersects with the central axis of the housing.

[0010] Optionally, the common axis is orthogonal to the central axis of the housing, and the plane formed by the two is horizontal.

[0011] Optionally, the housing has a horizontal first diameter direction; the air guide shroud is square in shape and has opposing first and second side plates in the first diameter direction; wherein: The air inlet is located on the first side plate and penetrates the first side plate axially in the housing; and / or, the air outlet is located on the second side plate and penetrates the second side plate axially in the housing.

[0012] Optionally, the opening area of ​​the air outlet completely covers the surface area of ​​the second side panel.

[0013] Optionally, the front housing and the rear housing enclose an inner cavity for housing the powertrain, and the two ends of the rotor shaft of the powertrain pass through the front housing and the rear housing respectively along the axial direction of the housing; The heat dissipation system also includes a flexible transmission component, which is bent and drives the rotor shaft and the airflow drive assembly.

[0014] Optionally, the flexible transmission component is located in the front air duct or the rear air duct. One end of the flexible transmission component is connected to the rotor shaft, and the other end extends radially along the housing, extends out of the air guide shroud from the air inlet or the air outlet, and is connected to the airflow drive assembly.

[0015] Optionally, at least a portion of the airflow drive assembly is located outside the air guide shroud.

[0016] Optionally, the airflow driving component is configured as an air supply component, which is located at the air inlet and generates positive pressure at the air inlet to supply air into the front and rear air ducts; or, The airflow driving component is configured as a suction component, which is located at the air outlet and generates negative pressure at the air outlet to draw airflow from the front air duct and the rear air duct and discharge it outward.

[0017] Optionally, both the end plate of the front housing and the end plate of the rear housing are provided with shaft holes for the rotor shaft of the powertrain to pass through. The heat dissipation system further includes two sets of heat dissipation fins respectively disposed on the front shell and the rear shell. Each set of heat dissipation fins includes multiple thin plates. The multiple thin plates are disposed on the outer end face of the corresponding end plate and are arranged in parallel radial direction. Both ends of each thin plate extend beyond the peripheral outer edge of the end plate and are bent and extended axially. Part of the thin plate is broken at the position corresponding to the shaft hole and its surrounding area. The thin plates of the two sets of heat dissipation fins correspond one-to-one.

[0018] Optionally, the air inlet and the air outlet are arranged opposite each other along the first diameter direction of the housing; the plurality of thin plates are arranged opposite each other along the second diameter direction of the housing; wherein the first diameter direction and the second diameter direction are arranged intersectingly.

[0019] This invention proposes a disc motor, comprising: The aforementioned heat dissipation system; and, The powertrain is housed within the housing of the cooling system, and the powertrain and the airflow drive assembly of the cooling system are connected via a flexible transmission component of the cooling system.

[0020] The technical solution provided by this invention has at least the following advantages: The heat dissipation system provided by this invention employs parallel-connected front and rear air ducts. The cold airflow entering from the air inlet flows in two directions: one enters the front air duct, enveloping the front housing and directly exchanging heat with the front stator area; the other enters the rear air duct, enveloping the rear housing and directly exchanging heat with the rear stator area. This allows for simultaneous air-cooled heat exchange in both the front and rear stator areas, eliminating the sequential heat absorption and superposition process. The front stator no longer uses airflow heated by the rear stator, thus reducing or even eliminating the temperature difference between the front and rear stators. This results in more uniform temperature rise across the windings and housing, preventing localized overheating and extending the lifespan of the disc motor. Furthermore, the air inlet and outlet are located around the perimeter of the housing, with the front and rear air ducts surrounding the outer edge of the housing. This ensures that the ventilation path is completely independent of the front end face opening of the disc motor. Moreover, the front flange assembly does not obstruct or block the air inlet or outlet, ensuring stable airflow velocity within the front air duct and enhancing the assembly versatility of the disc motor. Attached Figure Description

[0021] 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, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0022] Figure 1 This is a schematic diagram of a structure of an embodiment of a disc motor provided by the present invention; Figure 2 for Figure 1 A schematic diagram of the structure of the disc motor (from another perspective); Figure 3 for Figure 1 Side view of the disc motor; Figure 4 for Figure 1 The exploded view of the disc motor.

[0023] Explanation of icon numbers: 1000 Disc motor; 100 Cooling system; 1 Housing; 11 Front housing; 12 Rear housing; 13 Shaft hole; 2 Air guide shroud; 21 Front air duct; 22 Rear air duct; 23 Air inlet; 24 Air outlet; 25 First side plate; 26 Second side plate; 3 Airflow drive assembly; 4 Flexible transmission component; 5 Heat dissipation fins; 51 Thin plate; 200 Powertrain; 201 Rotor shaft.

[0024] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0025] To further illustrate the technical means and effects of the present invention in achieving its intended purpose, the following detailed description of the specific implementation methods, structures, features, and effects of the present invention, in conjunction with the accompanying drawings and preferred embodiments, is provided below.

[0026] Disc motors typically use permanent magnets as rotors and iron-core windings as stators. To counteract the axial magnetic pull from a single stator, a dual-stator structure is commonly used to ensure force balance. Disc motors generate heat during operation, which is usually dissipated using air cooling.

[0027] To reduce the difference in heat dissipation between the front and rear stators and ensure a uniform temperature distribution throughout the machine, this invention improves the structure of the heat dissipation system 100 of the disc motor 1000. The heat dissipation system 100 of the disc motor 1000 will be described in detail below with reference to the accompanying drawings.

[0028] Please see Figure 1 and Figure 2The disc motor 1000 includes a cooling system 100 and a powertrain 200. The cooling system 100 can be applied to operating scenarios that require simultaneous air cooling of the front and rear areas. The cooling system 100 forms a front air duct 21 and a rear air duct 22 on the outer periphery of the housing 1, allowing the cooling airflow to reach the front and rear outer peripheries of the housing 1 respectively, rather than simply flowing sequentially through the two areas along the axial direction of the housing 1.

[0029] The housing 1 includes a front housing 11 and a rear housing 12 that are axially joined together. The front housing 11 and the rear housing 12 can be combined by interlocking connecting edges to form an internal cavity for housing the powertrain. The axial direction of the housing 1 is the direction in which the front housing 11 and the rear housing 12 extend to join together, and the radial direction of the housing 1 is a direction perpendicular to the axial direction and extending from the center of the housing 1 outwards. When the powertrain 200 is located within the internal cavity of the housing 1, the housing 1 can provide external protection for the powertrain 200 and dissipate the heat generated by the powertrain 200 during operation.

[0030] The air guide shroud 2 is disposed around the periphery of the housing 1, forming a space between the air guide shroud 2 and the housing 1 for airflow. It should be noted that the air guide shroud 2 is not limited to a single integral component; it can also be formed by splicing multiple shroud walls to create an external airflow guiding component, as long as it can form an airflow space together with the housing 1. The airflow space corresponding to the periphery of the front housing 11 constitutes the front air duct 21, and the airflow space corresponding to the periphery of the rear housing 12 constitutes the rear air duct 22. Both the front air duct 21 and the rear air duct 22 have a starting end near the air inlet 23 and an ending end near the air outlet 24. The air inlet 23 and the air outlet 24 are located on the periphery of the air guide shroud 2 corresponding to the housing 1 and are arranged opposite each other.

[0031] Please see Figure 1 The airflow drive assembly 3 is installed at the air inlet 23 or the air outlet 24. When the airflow drive assembly 3 is working, the external cooling airflow can enter the flow space between the air guide shroud 2 and the housing 1 through the air inlet 23. The airflow entering the air guide shroud 2 is split near the air inlet 23. Part of the airflow enters the front air duct 21 along the periphery of the front housing 11, and the other part of the airflow enters the rear air duct 22 along the periphery of the rear housing 12.

[0032] The cold airflow in the front air duct 21 exchanges heat with the front shell 11, and the cold airflow in the rear air duct 22 exchanges heat with the rear shell 12. The two airflows converge near the air outlet 24 or flow separately to the air outlet 24, and are finally discharged from the air guide shroud 2 through the air outlet 24.

[0033] The airflow drive component 3 can be installed at the air inlet 23 or the air outlet 24, as long as it can make the airflow flow in a directional manner along the air inlet 23, the front air duct 21 and the rear air duct 22 and the air outlet 24.

[0034] In the technical solution of this invention, a front air duct 21 and a rear air duct 22 are arranged in parallel. The cold airflow entering from the air inlet 23 enters the front air duct 21 to wrap around the front shell 11 and directly exchange heat with the front stator area; the other enters the rear air duct 22 to wrap around the rear shell 12 and directly exchange heat with the rear stator area. In this way, air-cooled heat exchange can be achieved simultaneously for the front and rear stator areas. There is no sequential heat absorption and superposition process of the airflow. The front stator no longer uses the airflow heated by the rear stator, thereby reducing or even eliminating the temperature difference between the front and rear stators. This makes the temperature rise of the windings and the housing 1 more uniform, avoids local overheating, and thus extends the service life of the disc motor 1000.

[0035] Meanwhile, both the air inlet 23 and the air outlet 24 are located on the periphery of the housing 1, and the front air duct 21 and the rear air duct 22 are arranged around the periphery of the housing 1, so that the ventilation path does not depend on the air outlet at the front end face of the disc motor 1000. Furthermore, the air inlet 23 or the air outlet 24 will not be obstructed or blocked during the assembly of the front flange. This not only stabilizes the airflow velocity within the front air duct 21 and optimizes the heat dissipation conditions in the front stator area, but also enhances the assembly versatility of the disc motor 1000.

[0036] Based on the above structure, in a specific assembly process of the heat dissipation system 100, the front shell 11 and the rear shell 12 can be joined together along the axial direction of the housing 1 to form the housing 1. Then, the air guide shroud 2 is installed on the periphery of the housing 1, so that a predetermined gap is formed between the inner wall of the air guide shroud 2 and the outer wall of the housing 1. The air inlet 23 and the air outlet 24 on the air guide shroud 2 are respectively connected to the two ends of the gap.

[0037] After the airflow drive assembly 3 is assembled, the airflow direction can be confirmed by rotating the direction; when the airflow direction is detected to be opposite to the predetermined direction, the installation orientation of the airflow drive assembly 3 can be changed or its drive direction can be changed so that the airflow enters from the air inlet 23 and is discharged from the air outlet 24.

[0038] This invention does not impose specific limitations on the relationship between the front air duct 21 and the rear air duct 22. The front air duct 21 and the rear air duct 22 can be independent of each other, or they can be at least partially connected.

[0039] In one embodiment, the front air duct 21 and the rear air duct 22 are spatially interconnected.

[0040] That is, the front air duct 21 and the rear air duct 22 can be connected near the air inlet 23 or near the air outlet 24, and a continuous or partial connection area can also be set between them. When the front air duct 21 and the rear air duct 22 are connected near the air inlet 23, the airflow entering the air guide shroud 2 can be automatically distributed according to the flow resistance around the front shell 11 and the rear shell 12; when the front air duct 21 and the rear air duct 22 are connected near the air outlet 24, the airflow in the front air duct 21 and the rear air duct 22 can converge before being discharged; when there are multiple connection points between the air ducts, the airflow can be redistributed at multiple locations around the outer periphery of the casing 1. In one embodiment, the flow boundary of the front air duct 21 and / or the rear air duct 22 is jointly defined by the inner wall of the air guide shroud 2 and the outer wall of the housing 1. That is, the cooling airflow does not flow in a separately added closed duct, but forms a restricted interlayer channel between the inner wall of the air guide shroud 2 and the outer wall of the housing 1, and flows along this channel close to the outer surface of the housing 1. Since the flow boundary is jointly defined by the inner wall of the air guide shroud 2 and the outer wall of the housing 1, the airflow can be restricted and forward along the outer wall of the housing 1, thereby allowing the cold airflow to participate more fully in the heat exchange of the outer wall of the housing 1.

[0041] It should be noted that either of the above two technical features can be set, or both can be set simultaneously. Specifically, both of the above technical features can be set simultaneously.

[0042] To further reduce the difference in heat dissipation between the front and rear stators and ensure a uniform temperature field distribution throughout the machine.

[0043] In one embodiment, the projection of the air inlet 23 onto the housing 1 has the same area falling into the front housing 11 and the same area falling into the rear housing 12. That is, the air inlet 23 is arranged across the mating surfaces of the front housing 11 and the rear housing 12, and its projected area is evenly divided in half. After the cold air enters the air guide shroud 2 from the air inlet 23, the airflow is naturally divided into two streams and flows into the front air duct 21 and the rear air duct 22 in equal amounts, ensuring that the basic air intake volume of the two parallel air ducts is consistent.

[0044] In one embodiment, the projection of the air outlet 24 onto the housing 1 has the same area falling into the front housing 11 and the same area falling into the rear housing 12. That is, the air outlet 24 is arranged across the mating surfaces of the front housing 11 and the rear housing 12, and its projected area is evenly divided in half, so that the front air duct 21 and the rear air duct 22 have the same exhaust flow area, the air inlet and outlet flow rates of the two air ducts correspond one-to-one, the air pressure is consistent, and there will be no airflow obstruction or airflow cross-flow in a single air duct, ensuring that the flow rate of the two cooling airflows is stable throughout the entire process.

[0045] In one embodiment, the air inlet 23 has a smaller air inlet area than the air outlet 24. By making the air inlet area smaller than the air outlet area, the cross-sectional change is used to accelerate the airflow in the duct, expand the capacity, reduce pressure, and facilitate exhaust, thereby reducing exhaust resistance, fan power consumption, and noise, and extending the heat exchange time between the airflow and the casing 1 to improve heat dissipation efficiency. At the same time, the smaller air inlet 23 reduces the intake of impurities, while the larger air outlet 24 facilitates the discharge of dirt and is less prone to duct blockage.

[0046] It should be noted that one, two, or all of the above three technical features can be set. Specifically, all three technical features can be set simultaneously.

[0047] The air inlet area can be determined by the opening profile, number of openings, or effective ventilation area of ​​the air inlet 23; the air outlet area can be determined by the opening profile, number of openings, or effective exhaust area of ​​the air outlet 24.

[0048] The specific area relationship between the air inlet 23 and the air outlet 24 can be determined by taking into account the available installation space outside the air guide shroud 2, the installation position of the airflow drive component 3, and the flow resistance of the air duct.

[0049] In actual operation, after the airflow drive component 3 is started, the airflow direction can be confirmed by observing the airflow status near the air inlet 23 and the exhaust status near the air outlet 24. When exhaust is found to be restricted at the air outlet 24, check whether there are any assembly obstructions affecting airflow near the second side plate 26, and adjust the position of the external mating structure to maintain sufficient space for airflow to exit between the air outlet 24 and the external environment. This check does not change the basic airflow path of the front air duct 21 and the rear air duct 22, but is used to avoid adverse effects of external installation conditions on exhaust.

[0050] Specifically, the central axis of the air inlet 23 and the central axis of the air outlet 24 can be collinear, forming a common axis. This common axis passes through the geometric center of the housing 1, allowing the air inlet 23 and the air outlet 24 to form corresponding air intake and exhaust positions relative to the housing 1. Here, the geometric center of the housing 1 can be understood as the center position of the housing 1's shape in the corresponding geometric direction. When the common axis passes through this position, the air inlet 23 and the air outlet 24 can form a relatively balanced arrangement relative to the periphery of the housing.

[0051] The common axis intersects with the central axis of the housing 1. The central axis of the housing 1 can be aligned with the extension direction of the rotor shaft 201. The common axis defines the main air intake and exhaust directions between the air inlet 23 and the air outlet 24. When the two axes intersect, the cooling airflow can enter from one direction around the housing 1 and exit from the opposite direction, creating a lateral flow trend around the periphery of the front housing 11 and the rear housing 12. This lateral flow trend intersects with the axial extension direction of the housing 1.

[0052] The air inlet 23 and air outlet 24 are arranged coaxially and oppositely, with their common axis passing through the center of the casing 1 and intersecting the main axis of the disc motor 1000. This ensures that the path length, turning angle, flow cross-section, and local resistance of the two airflow loops, the front air duct 21 and the rear air duct 22, are consistent. As a result, the flow rates and heat exchange times of the two cooling airflows are essentially the same, further eliminating the temperature difference between the front and rear stators. This results in a more uniform temperature rise across the windings and casing 1, preventing localized overheating and extending the service life of the disc motor 1000.

[0053] This invention does not impose specific limitations on the arrangement of the common axis and the central axis of the housing 1. In one embodiment, the common axis and the central axis of the housing 1 are orthogonal. The orthogonal arrangement defines the angular relationship between the two axes, ensuring that the air inlet and outlet directions of the air inlet 23 and air outlet 24 are perpendicular to the axial direction of the housing 1. The plane formed by the common axis and the central axis of the housing 1 can be horizontal. This horizontal arrangement describes the planar orientation determined by the two axes, enabling the relative positions of the air inlet 23 and air outlet 24 to be adapted to the installation direction of the disc motor 1000.

[0054] In this embodiment, the central axis of the housing 1 is the axial main axis of the disc motor 1000, and the common axis is orthogonal to it. This allows the air inlet 23 and the air outlet 24 to be arranged directly opposite each other along the radial direction of the disc motor 1000, resulting in straight airflow. Compared to oblique cross-flow, the orthogonal layout minimizes airflow turns, reduces local wind resistance, lowers fan pressure loss, and increases ventilation efficiency. Simultaneously, it ensures that the air inlet 23 and the air outlet 24 are precisely divided in half by the mating surfaces of the front and rear housings, further improving airflow accuracy and ensuring consistent air-cooling conditions for the front and rear stators.

[0055] Please see Figure 3The air guide shroud 2 can be square in shape. The square air guide shroud 2 has a first side plate 25 and a second side plate 26 arranged opposite each other along the horizontal first diameter direction of the housing 1. The first side plate 25 faces the side along the first diameter direction, and the second side plate 26 faces the opposite side along the first diameter direction. The relative position between the first side plate 25 and the second side plate 26 is used to determine the basis for the arrangement of the air inlet and outlet sides, while the axial direction of the housing 1 is used to define the extension direction of the air outlet on the corresponding side plate. Therefore, the first diameter direction is not equivalent to the housing axial direction, and the lateral relative position of the air outlet should not be confused with the axial penetration relationship of the air outlet on the side plate.

[0056] The air inlet 23 can be disposed on the first side plate 25 and pass through the first side plate 25 along the axial direction of the housing 1. When the air inlet 23 passes through the first side plate 25, an air intake passage is formed on the first side plate 25 from the outside of the air guide shroud 2 to the inside of the air guide shroud 2.

[0057] The air outlet 24 can be disposed on the second side plate 26 and penetrate through the second side plate 26 along the axial direction of the housing 1. When the air outlet 24 penetrates through the second side plate 26, an exhaust passage is formed on the second side plate 26 from the inside of the air guide shroud 2 to the external environment.

[0058] After the first side plate 25 and the second side plate 26 are arranged opposite each other, the airflow can enter the air guide hood 2 from the first side plate 25, and after flowing through the front air duct 21 and the rear air duct 22 inside the air guide hood 2, it can leave from the second side plate 26.

[0059] Combination Figures 1 to 4 From the perspective of the front-back direction, it usually refers to the axial direction of the housing 1; the left-right direction usually refers to the first diameter direction of the housing 1; and the up-down direction usually refers to the second diameter direction of the housing 1.

[0060] This invention does not specifically limit the opening area of ​​the air outlet 24. In one embodiment, the opening area of ​​the air outlet 24 completely covers the surface area of ​​the second side plate 26. The second side plate 26 can form an entirely open exhaust side, allowing the airflow in the front air duct 21 and the rear air duct 22 to leave the air guide shroud 2 through a larger exhaust area. In this way, the maximum exhaust area can be fully released, exhaust throttling resistance and airflow dead zones can be eliminated, and the hot air exhaust efficiency and the uniformity of heat dissipation of the whole machine can be further improved.

[0061] Please see Figures 1 to 4 The front housing 11 and the rear housing 12 enclose the inner cavity of the housing 1, and the powertrain 200 is located in this inner cavity. The rotor shaft 201 of the powertrain 200 extends axially along the housing 1, and its two ends pass through the front housing 11 and the rear housing 12, respectively. The rotor shaft 201 is capable of outputting rotational power when the powertrain 200 is running. The flexible transmission member 4 is bent, with one end connected to the rotor shaft 201 and the other end connected to the airflow drive assembly 3.

[0062] In this embodiment, during the operation of the powertrain 200, the rotational power output by the rotor shaft 201 is transmitted to the airflow drive assembly 3 via the flexible transmission component 4, enabling the airflow drive assembly 3 to synchronously generate cooling airflow. This transmission method utilizes the rotation of the rotor shaft 201 to achieve airflow drive, eliminating the need for a separate independent power source for the airflow drive assembly 3 and simplifying the overall electrical structure of the machine.

[0063] Meanwhile, the flexible transmission component 4 can be bent and rotated arbitrarily, without being limited by the angle or distance between the extended end of the rotor shaft 201 and the installation position of the airflow drive component 3. In the above embodiment, the air inlet 23 and the air outlet 24 are arranged on the periphery of the housing 1. The rotor shaft 201 extends along the axial direction of the disc motor 1000, and the airflow drive component 3 is arranged in the radial side air duct. The two are axially and radially misaligned, and power transmission can be completed by relying on the bent flexible transmission component 4, without modifying the main air duct structure of the housing 1 and the air guide shroud 2.

[0064] The flexible transmission component 4 can be a transmission component capable of transmitting rotational power and allowing the formation of a bending path. When transmitting power, the flexible transmission component 4 should maintain effective transmission cooperation with the rotor shaft 201 and the airflow drive assembly 3 at both ends respectively; when the path of the flexible transmission component 4 needs to bypass the outer peripheral structure of the housing 1, its bending path can be adjusted according to the relative position of the air guide shroud 2, the air duct and the air outlet.

[0065] Specifically, the flexible transmission component 4 can be located in the front air duct 21 or the rear air duct 22. One end of the flexible transmission component 4 is connected to the rotor shaft 201, and the other end is bent and extended radially along the housing 1, and extends out from the air inlet 23 or the air outlet 24 to the outside of the air guide shroud 2 and then connects to the airflow drive assembly 3.

[0066] When the flexible transmission component 4 is arranged in the front air duct 21, it can extend along the air duct space around the front shell 11; when the flexible transmission component 4 is arranged in the rear air duct 22, it can extend along the air duct space around the rear shell 12. The specific bending direction of the flexible transmission component 4 can be selected in combination with the different positions of the airflow drive component 3 at the air inlet 23 or the air outlet 24.

[0067] In this embodiment, the flexible transmission component 4 is directly arranged in the front air duct 21 or the rear air duct 22, rather than being exposed on the outside of the air guide shroud 2; only the end of the flexible transmission component 4 passes through the air inlet 23 or the air outlet 24 and connects with the airflow drive component 3, thereby making the overall outer contour of the disc motor 1000 neat and simple.

[0068] Furthermore, the flexible transmission component 4 is composed of alternating layers of steel wire wound around the inner and outer parts, with a protective layer (such as rubber or plastic) covering the metal parts. The flexible transmission component 4 can achieve large-angle bending transmission. During motor operation, the metal parts and protective layer of the flexible transmission component 4 are prone to heat generation and aging due to long-term deformation, stress, and friction. The flexible transmission component 4 is designed to pass through the front air duct 21 or the rear air duct 22 throughout its operation, with the cooling airflow continuously circulating and washing around the flexible transmission component 4, carrying away the heat generated by transmission friction, preventing the flexible transmission component 4 from softening, loosening, or breaking at high temperatures, thereby reducing the wear rate of the flexible transmission component 4.

[0069] To avoid adverse effects on the main airflow path, the flexible transmission component 4 can be arranged close to the duct boundary and maintain a suitable transmission distance from the inner wall of the air guide shroud 2 or the outer wall of the housing 1. When interference occurs between the flexible transmission component 4 and the air guide shroud 2, it can be avoided by adjusting the position of the bent section of the flexible transmission component 4, the peripheral installation position of the airflow drive assembly 3, or the assembly position around the air outlet, as long as power can still be transmitted between the rotor shaft 201 and the airflow drive assembly 3.

[0070] In one embodiment, please refer to Figure 1 At least a portion of the airflow drive assembly 3 is located outside the air guide shroud 2. The main body of the airflow drive assembly 3 can be located outside the air guide shroud 2, while a portion of the structure that mates with the air outlet can be near the air inlet 23 or the air outlet 24. Positioning at least a portion of the airflow drive assembly 3 outside the air guide shroud 2 helps to reserve flow space for the front air duct 21 and the rear air duct 22, and facilitates the transmission connection between the airflow drive assembly 3 and the flexible transmission component 4. The airflow drive assembly 3 can be installed or positioned in conjunction with the air guide shroud 2 through the peripheral structure 23, while the central connecting component 4 establishes a transmission relationship with the flexible transmission component 4. The peripheral mounting structure of the airflow drive assembly 3 can be adapted to the contour of the air inlet 23 or the air outlet 24, as long as it does not affect the airflow communication between the air outlet and the air duct.

[0071] The present invention does not impose specific limitations on the form of the airflow driving component 3. The airflow driving component 3 can be configured as an air supply component, which is disposed at the air inlet 23. The airflow driving component 3 can also be configured as a suction component, which is disposed at the air outlet 24.

[0072] In one embodiment, the airflow drive component 3 can be configured as an air supply component located at the air inlet 23 and generating positive pressure at the air inlet 23 to supply air into the front air duct 21 and the rear air duct 22. The air supply component may include a fan, which, when rotating, draws outside air into the air inlet 23. The air supply component may employ an axial flow fan, a centrifugal fan, a blower, or other structure capable of creating an air supply effect at the air inlet 23. In one embodiment, the airflow drive component 3 can also be configured as a suction component. The suction component is disposed at the air outlet 24 and generates negative pressure at the air outlet 24 to draw airflow in the front air duct 21 and the rear air duct 22 and discharge it outward.

[0073] The air guide shroud 2 and the casing 1 together enclose a through and directional front air duct 21 and a rear air duct 22, confining the airflow within the fixed channels for orderly unidirectional flow, avoiding disorderly diffusion and impact losses. Simultaneously, the suction component at the air outlet 24 drives the airflow through negative pressure, resulting in orderly and stable airflow within the front air duct 21 and rear air duct 22, with minimal turbulence and pressure loss, thereby reducing airflow resistance and minimizing ineffective energy loss.

[0074] In both supply and exhaust modes, the rotational status of the airflow drive assembly 3 can be checked. If the airflow drive assembly 3 fails to rotate with the rotor shaft 201 due to an abnormal connection of the flexible transmission component 4, the transmission coordination between the airflow drive assembly 3 and the flexible transmission component 4 can be rechecked. If the airflow drive assembly 3 rotates but the airflow within the duct is unstable, the gaps between the air inlet 23, the air outlet 24, and the air guide shroud 2 and the casing 1 can be checked. These checks ensure that the airflow drive assembly 3, the air outlet, and the duct maintain communication without altering the basic airflow drive principle of the supply and exhaust modes.

[0075] Please see Figure 2 and Figure 3 In one embodiment, both the end plates of the front housing 11 and the rear housing 12 are provided with shaft holes 13, through which the rotor shaft 201 passes and extends axially along the housing 1. The front housing 11 and the rear housing 12 are each provided with a set of heat dissipation fins 5, each set of fins 5 including multiple thin plates 51. The heat dissipation fins 5 on the front housing 11 are in contact with the airflow in the front air duct 21, and the heat dissipation fins 5 on the rear housing 12 are in contact with the airflow in the rear air duct 22.

[0076] Multiple thin plates 51 are disposed on the outer end faces of corresponding end plates and arranged radially parallel to each other along the housing 1. When the thin plates 51 extend radially, they can extend from near the shaft hole 13 toward the periphery of the end plate. Both ends of each thin plate 51 extend beyond the outer periphery of the corresponding end plate and bend axially along the housing 1, so that the thin plates 51 are not only located on the outer end faces of the end plates, but also extend to the periphery of the end plates. The axially bent extension of the thin plates 51 can form a corresponding heat exchange space with the outer periphery of the housing 1 and come into contact with the airflow flowing in the front air duct 21 or the rear air duct 22.

[0077] Part of the thin plate 51 is broken at the location corresponding to the shaft hole 13 and its surrounding area. After the thin plate 51 is broken, the shaft hole 13 and its surrounding area retain space for the rotor shaft 201 to pass through and for the arrangement of adjacent structures. The break position can be determined in combination with the actual position of the shaft hole 13, so that the thin plate 51 will not obstruct the rotor shaft 201 from passing through the front shell 11 and the rear shell 12 along the housing axis.

[0078] The multiple thin plates 51 on the front shell 11 correspond one-to-one with the multiple thin plates 51 on the rear shell 12, that is, each thin plate 51 on the front shell side can be found in a corresponding position on the rear shell side. This correspondence helps to form a corresponding heat exchange structure on the outer sides of the front shell 11 and the rear shell 12.

[0079] In this embodiment, the end plate is directly attached to the stator end winding, serving as a concentrated heat conduction surface. The multiple thin plates 51 increase the heat exchange area on the outer surface of the end plate. Before forced air cooling is activated and when the airflow of the low-speed fan is insufficient, natural convection can enhance the basic heat dissipation capacity and reduce the temperature rise of the winding base. Furthermore, the multiple thin plates 51 are arranged in parallel radially, with a neat and unobstructed arrangement. The airflow experiences low resistance as it flows radially, making it less likely to form airflow stagnation dead zones, thus ensuring stable heat exchange efficiency.

[0080] Meanwhile, the thin plate 51 extends radially outward beyond the outer edge of the end plate circumference and then bends along the motor axis. The forced cooling airflow in the sandwich duct can directly wash over and wrap around the bent section of the thin plate 51, thereby increasing the heat exchange contact area and the degree of airflow contact, maximizing the heat dissipation utilization rate of forced air cooling.

[0081] The rotor shaft 201 needs to pass through the shaft hole 13 to install the oil seal and bearing end cover. The thin plate 51 is cut off at this point to directly avoid the shaft assembly space and prevent the thin plate 51 from interfering with the disassembly and installation of the shaft, seals, and bearing cover. There is no structural conflict in the assembly process. The cut-off design does not completely remove the single thin plate 51, but only partially cuts it. The remaining part of the single thin plate 51 can still conduct heat and dissipate heat normally, resulting in a small loss of overall heat dissipation area, which balances structural avoidance and heat dissipation performance.

[0082] Furthermore, the number, position, and size of the multiple thin plates 51 on the front shell 11 are matched with the number of thin plates 51 on the rear shell 12. The internal heat exchange structures of the front air duct 21 and the rear air duct 22 are completely symmetrical, and the airflow heat exchange load in the two air ducts is consistent, thereby further reducing the temperature difference between the front stator and the rear stator and further improving the uniformity of the temperature rise of the whole machine.

[0083] It should be noted that the thin plate 51 can be a metal sheet, a sheet-shaped heat sink, or other components with a sheet-shaped heat exchange surface; its quantity, spacing, thickness, and included angle can also be adjusted according to the size of the casing and heat dissipation requirements; the disconnected area can be an arc notch, a U-shaped clearance opening, or other clearance shape that fits the outer periphery of the shaft hole.

[0084] The thin plates 51 can be arranged according to the shape of the end plate, the surrounding space of the shaft hole 13, and the flow range of the front air duct 21 and the rear air duct 22. The number, spacing, and disconnection position of the thin plates 51 can be adjusted, as long as multiple thin plates 51 are arranged radially parallel to the casing 1, connected to the corresponding end plates, and both ends extend beyond the outer edge of the end plate and bend axially. When the thin plates 51 come into contact with the airflow in the front air duct 21 and the rear air duct 22, they can increase the heat exchange contact area between the outer side of the end plate and the airflow.

[0085] In one embodiment, the air inlet 23 and the air outlet 24 are arranged opposite each other along the first diameter direction of the housing 1, and the multiple thin plates 51 are arranged opposite each other along the second diameter direction of the housing 1, with the first diameter direction and the second diameter direction intersecting. When the main air inlet and outlet directions of the air outlets intersect with the arrangement direction of the thin plates 51, the airflow can pass through the area between or near adjacent thin plates 51 during its flow around the housing, thereby allowing the cooling airflow to make sufficient contact with the thin plates 51.

[0086] The first diameter direction is used to determine the relative positions of the first side plate 25 and the second side plate 26, and the second diameter direction is used to determine the arrangement direction of the plurality of thin plates 51. The first diameter direction and the second diameter direction are arranged intersectingly, and are not required to be the same as the axial direction of the housing. The first diameter direction of the housing 1 usually refers to the left-right direction; the second diameter direction of the housing 1 usually refers to the up-down direction.

[0087] The present invention also provides a disc motor 1000. The disc motor 1000 includes a heat dissipation system 100 and a power assembly 200. The power assembly 200 is housed within the housing 1 of the heat dissipation system 100 and includes a stator and a rotor arranged in a front-rear direction. The two ends of the rotor shaft 201 of the rotor pass axially through the housing 1. An airflow drive assembly 3 of the heat dissipation system 100 is disposed corresponding to the periphery of the housing 1. The airflow drive assembly 3 is drively connected to the rotor shaft 201 via a flexible transmission member 4 of the heat dissipation system 100.

[0088] The heat dissipation system 100 is configured as described above. That is, the heat dissipation system 100 has all the embodiments of the heat dissipation system 100 described above. Therefore, the disc motor 1000 also includes all the technical features of the heat dissipation system 100 described above, and thus possesses the technical effects brought about by all the aforementioned technical features.

[0089] Thus, when the disc motor 1000 is working, the rotor in the power assembly 200 rotates, driving the rotor shaft 201 to rotate. The rotor shaft 201 then drives the rotating turbulence component to rotate synchronously through the flexible transmission component 4, so as to drive the airflow to flow from the air inlet 23 into the front air duct 21 and the rear air duct 22 respectively, and out from the air outlet 24.

[0090] In other words, the heat generated by the powertrain 200 is transferred outward through the housing 1 and the heat dissipation fins 5, and then carried away by the flowing air in the front air duct 21 and the rear air duct 22, thereby applying the air guide shroud 2, the airflow drive component 3 and the heat dissipation fins 5 around the heat dissipation system 100 to the overall operation of the disc motor 1000.

[0091] The powertrain 200 can also adopt a stator and rotor combination adapted to the structure of the disc motor 1000, as long as it can be housed in the housing 1 and cooperate with the air-cooling system 100.

[0092] The above embodiments illustrate the air-cooling system 100 of the disc motor 1000 and its application. The features in each embodiment can be combined as needed.

[0093] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention in any way. Although the present invention has been disclosed above with reference to preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art can make some modifications or alterations to the above-disclosed technical content to create equivalent embodiments without departing from the scope of the present invention. Any simple modifications, equivalent changes and alterations made to the above embodiments based on the technical essence of the present invention without departing from the scope of the present invention shall still fall within the scope of the present invention.

Claims

1. A heat dissipation system applied to a disc motor, characterized in that, include: The housing, including a front housing and a rear housing joined together along its axial direction; An air guide shroud is disposed on the periphery of the housing, and the two form a front air duct at the position corresponding to the periphery of the front housing and a rear air duct at the position corresponding to the periphery of the rear housing. The air guide shroud has opposing air inlets and outlets at positions corresponding to the periphery of the housing; the front air duct and the rear air duct have their starting ends connected to the air inlets and their ending ends connected to the air outlets; and, An airflow driving component is located at the air inlet or the air outlet to drive airflow from the air inlet into the front air duct and the rear air duct respectively, and out of the air outlet.

2. The heat dissipation system according to claim 1, characterized in that, The front air duct and the rear air duct are spatially interconnected; and / or, The flow boundaries of the front air duct and / or the rear air duct are jointly defined by the inner wall of the air guide shroud and the outer wall of the housing.

3. The heat dissipation system according to claim 1, characterized in that, The projection of the air inlet onto the housing has an area that falls into the front housing and an area that falls into the rear housing that are equal; and / or, The projection of the air outlet onto the housing has an area that falls into the front housing and an area that falls into the rear housing that are equal; and / or, The air inlet area is smaller than the air outlet area.

4. The heat dissipation system according to claim 3, characterized in that, The central axis of the air inlet and the central axis of the air outlet are collinear, and their common axis passes through the geometric center of the housing and intersects with the central axis of the housing.

5. The heat dissipation system according to claim 4, characterized in that, The common axis is orthogonal to the central axis of the housing, and the plane formed by the two is horizontal.

6. The heat dissipation system according to claim 1, characterized in that, The housing has a horizontal first diameter direction; the air guide shroud is square in shape and has opposing first and second side plates in the first diameter direction; wherein: The air inlet is located on the first side plate and penetrates the first side plate axially in the housing; and / or, the air outlet is located on the second side plate and penetrates the second side plate axially in the housing.

7. The heat dissipation system according to claim 6, characterized in that, The opening area of ​​the air outlet completely covers the surface area of ​​the second side panel.

8. The heat dissipation system according to claim 1, characterized in that, The front housing and the rear housing together form an inner cavity for housing the powertrain, and the two ends of the rotor shaft of the powertrain pass through the front housing and the rear housing respectively along the axial direction of the housing; The heat dissipation system also includes a flexible transmission component, which is bent and drives the rotor shaft and the airflow drive assembly.

9. The heat dissipation system according to claim 8, characterized in that, The flexible transmission component is located in the front air duct or the rear air duct. One end of the flexible transmission component is connected to the rotor shaft, and the other end extends radially along the housing, extends out of the air guide shroud from the air inlet or the air outlet, and is connected to the airflow drive assembly.

10. The heat dissipation system according to claim 1, characterized in that, The airflow drive component has at least a partial structure located outside the air guide shroud.

11. The heat dissipation system according to claims 8 to 10, characterized in that, The airflow drive component is configured as an air supply component, which is located at the air inlet and generates positive pressure at the air inlet to supply air into the front air duct and the rear air duct. or, The airflow driving component is configured as a suction component, which is located at the air outlet and generates negative pressure at the air outlet to draw airflow from the front air duct and the rear air duct and discharge it outward.

12. The heat dissipation system according to claim 1, characterized in that, Both the end plate of the front housing and the end plate of the rear housing have shaft holes for the rotor shaft of the powertrain to pass through. The heat dissipation system further includes two sets of heat dissipation fins respectively disposed on the front shell and the rear shell. Each set of heat dissipation fins includes multiple thin plates. The multiple thin plates are disposed on the outer end face of the corresponding end plate and are arranged in parallel radial direction. Both ends of each thin plate extend beyond the peripheral outer edge of the end plate and are bent and extended axially. Part of the thin plate is broken at the position corresponding to the shaft hole and its surrounding area. The thin plates of the two sets of heat dissipation fins correspond one-to-one.

13. The heat dissipation system according to claim 12, characterized in that, The air inlet and the air outlet are arranged opposite each other along the first diameter direction of the housing; the plurality of thin plates are arranged opposite each other along the second diameter direction of the housing; wherein the first diameter direction and the second diameter direction are arranged intersectingly.

14. A disc motor, characterized in that, include: The heat dissipation system as described in any one of claims 1 to 13; as well as, The powertrain is housed within the housing of the cooling system, and the powertrain and the airflow drive assembly of the cooling system are connected via a flexible transmission component of the cooling system.

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