Air-cooled electric machine

Abstract

The application relates to a forced air cooling motor. The forced air cooling motor comprises a motor shell, a wind guide cover, an air flow driving assembly, a heat dissipation structure and a mounting carrier. The motor shell has opposite first and second ends in the axial direction. The wind guide cover is wrapped around the periphery of the motor shell, and an external air duct is formed between the motor shell and the wind guide cover. The wind guide cover is provided with an air inlet and an air outlet which are connected to the external air duct. The air flow driving assembly is arranged at the air inlet or the air outlet. The heat dissipation structure comprises heat dissipation fins arranged at the first and / or second ends, and the heat dissipation fins are in heat conduction contact with the motor shell and are accommodated in the external air duct. The mounting carrier is detachably mounted on the motor shell and is independent of and does not abut against the heat dissipation fins. The mounting carrier is assembled with the wind guide cover, and the surface of the mounting carrier away from the wind guide cover forms an outwardly exposed mounting surface for abutting against an external component.

Description

Technical Field

[0001] This invention relates to the field of disc motor technology, and more particularly to an air-cooled motor. Background Technology

[0002] Disc motors are characterized by short axial dimensions and high power density. The internal heating elements are compactly arranged, resulting in a large heat load per unit volume, thus placing high demands on air-cooling capabilities. To improve heat dissipation, forced air cooling structures are typically used, along with heat dissipation fins on the motor housing to increase the heat dissipation area. However, existing cooling methods have two drawbacks: firstly, this forced air cooling path causes significant differences in heat dissipation between the front and rear stators, leading to uneven temperature distribution across the entire motor and low heat exchange efficiency in localized areas; secondly, existing heat dissipation fins have poor heat dissipation performance and affect the overall installation of the motor. Summary of the Invention

[0003] The main objective of this invention is to propose an air-cooled motor that addresses the problems of uneven temperature distribution, low heat exchange efficiency in localized areas, poor heat dissipation of heat sinks, and poor overall motor installation associated with the air-cooled structure of existing disc motors.

[0004] To achieve the above objectives, the present invention proposes an air-cooled motor, comprising: The housing has a first end and a second end opposite each other in its axial direction; An air guide cover is provided to cover the outer periphery of the housing, and an external air duct is formed between the two and arranged around the outer periphery of the housing. The cooling airflow in the external air duct flows and exchanges heat around the outer periphery of the housing. An air inlet and an air outlet are provided on the air guide cover to connect the external air duct. An airflow drive component is located at the air inlet or the air outlet; A heat dissipation structure includes heat dissipation fins disposed at the first end and / or the second end, the heat dissipation fins being in thermal contact with the housing and housed within the external air duct; and, The mounting support is detachably installed on the housing and is independent of and does not abut against the heat dissipation fins. The mounting support is assembled with the air guide shroud, and its side surface facing away from the air guide shroud forms an exposed mounting surface for docking with the external components.

[0005] Optionally, the air inlet is provided at a position axially opposite to the first end of the air guide shroud, and the air outlet is provided at a position opposite to the outer peripheral sidewall of the housing and close to the second end. The external air duct includes two branch paths arranged in sections along the outer periphery of the housing. Both branch paths extend axially from the first end toward the second end, and their starting ends are connected to the air inlet, while their ending ends are connected to the air outlet on the same side.

[0006] Optionally, the air guide shroud has an air inlet at a position axially opposite to the first end and an air outlet at a position axially opposite to the second end; The external air duct is arranged to completely surround the outer periphery of the housing in the circumferential direction, and extends axially from the first end to the second end, so as to communicate with the air inlet and the air outlet respectively in the axial direction.

[0007] Optionally, the housing includes a front housing and a rear housing joined together along the axial direction; the air guide shroud has corresponding air inlets and outlets at positions corresponding to the periphery of the housing. The external air duct includes a front air duct formed on the periphery of the front shell and a rear air duct formed on the periphery of the rear shell. The starting ends of the front air duct and the rear air duct are connected to the air inlet, and the ending ends of the two air ducts are connected to the air outlet.

[0008] Optionally, the housing is used to house the powertrain, with the two ends of the rotor shaft of the powertrain passing through the first end and the second end, respectively. The heat dissipation structure also includes a back plate, which is detachably installed at the first end and / or the second end, and the back plate has a through hole for the end of the rotor shaft to pass through. The heat dissipation fins are disposed on the side surface of the back plate away from the housing, and the heat dissipation fins are broken at the positions corresponding to the through holes and their surrounding areas.

[0009] Optionally, the peripheral side of the housing has a mounting protrusion at a position corresponding to its bottom; The mounting support is configured as a plate-shaped mounting foot, which is located on the periphery of the housing and corresponds to the bottom of the housing. The mounting foot has a mounting groove for interlocking with the mounting protrusion during assembly. The mounting foot is used to install the housing onto an external support base.

[0010] Optionally, the interior of the housing is used to house the powertrain; The mounting support is configured as a mounting plate, which is located on the side of the heat dissipation fins away from the housing. The mounting plate has a clearance space to accommodate the heat dissipation fins when it is assembled to the housing. The mounting plate has a clearance hole along the axial direction to allow the end of the rotor shaft of the powertrain to pass through. The end face of the mounting plate away from the heat dissipation fins has a protruding stop portion, which is arranged around the outer edge of the clearance hole and is inserted and positioned with the mating part on the external equipment when the mounting plate is assembled with the external equipment.

[0011] Optionally, the housing is used to house the powertrain, and both the first and second ends have shaft holes for the rotor shaft to pass through. The heat dissipation structure includes two sets of heat dissipation fins, which are respectively disposed at the first end and the second end. Each set of heat dissipation fins forms a clearance area at the position corresponding to the shaft hole and its surrounding area. The end of the heat dissipation fin extends beyond the peripheral outer edge of the housing and is bent and extended axially along its peripheral outer wall.

[0012] Optionally, each set of heat dissipation fins includes at least four sets of fins arranged around the periphery of the shaft hole, and the four sets of fins are arranged in a cross-shaped orthogonal symmetrical distribution with the center of the end of the housing as the array center; The fin assembly extends in a fan shape from the center of the end of the housing to its periphery, including multiple layers of thin plates arranged radially. A heat dissipation channel is formed between two adjacent layers of thin plates along the axial direction. Each thin plate extends radially outward from the central region of the end of the housing and is partially bent. The extended end of the thin plate extends beyond the outer edge of the housing and is bent and extended axially along the outer peripheral sidewall of the housing, so that the heat dissipation channel on the end of the housing extends to the outer periphery of the enclosure.

[0013] Optionally, each set of heat dissipation fins includes two fin groups, which are symmetrically distributed along the first diameter direction of the housing. Each fin group includes multiple thin plates arranged parallel to each other along the second diameter direction of the housing. Both ends of the thin plates extend beyond the outer edge of the housing and are bent and extended axially along the outer peripheral sidewall of the housing. A portion of the thin plates located in the central region of the housing end is broken at the position corresponding to the shaft hole and its surrounding area to form the clearance area. At the break point, a portion of the thin plates is connected to an arc-shaped guide section along the circumference of the shaft hole.

[0014] The technical solution provided by this invention has at least the following advantages: In the air-cooled motor provided by this invention, an annular external air duct is provided around the outer periphery of the casing. The cooling airflow surrounds the entire outer periphery of the casing for convective heat exchange, and the entire outer wall of the casing can participate in heat dissipation, with heat being evenly carried away along the outer periphery of the casing. Meanwhile, heat dissipation fins are arranged at both ends of the axial direction. These fins are also placed within the external air duct and cooled by forced airflow, giving both ends of the disc motor efficient heat dissipation capabilities. This achieves combined circumferential full-area casing heat exchange and heat dissipation from the heat dissipation fins at both ends, thereby improving the uneven heat dissipation problem of the disc motor's axial front-to-back direction and enhancing the overall heat exchange utilization rate of the casing. Simultaneously, the heat dissipation fins are housed within the external air duct, and the forced cooling airflow continuously washes the fin surface, thereby enhancing the convective heat transfer capacity of the heat dissipation fins and improving their heat dissipation effect. Furthermore, the entire installation load is borne by the mounting support, which is independent of and does not abut against the heat dissipation fins, preventing load transfer to the fins. The heat dissipation fins do not need to consider mechanical load-bearing capacity, allowing for a more reasonable height-to-thickness ratio, thus increasing the heat dissipation area and improving the air-cooling capacity. Disc motors are easier to install because they are mounted on mounting brackets that connect with external components. These mounting brackets can be placed on the periphery of the housing for foot mounting or on the axial end of the housing for flange mounting, thus meeting different installation requirements for disc motors. Attached Figure Description

[0015] 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.

[0016] Figure 1 This is a schematic diagram of the structure of a first 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 (with a hidden partial air guide cover); Figure 3 for Figure 2 A schematic diagram of the structure of the disc motor (from another perspective); Figure 4 for Figure 1 A schematic diagram of the air-cooled flow path arrangement of the disc motor; Figure 5 This is a schematic diagram of a second embodiment of a disc motor provided by the present invention; Figure 6 for Figure 5 A schematic diagram of the structure of the disc motor (from another perspective); Figure 7 for Figure 5 A schematic diagram of the air-cooled flow path arrangement of the disc motor; Figure 8 A schematic diagram of the structure of a third embodiment of a disc motor provided by the present invention; Figure 9 for Figure 8 A schematic diagram of the structure of the disc motor (from another perspective); Figure 10 for Figure 8 A schematic diagram of the air-cooled flow path arrangement of the disc motor; Figure 11 A schematic diagram of the structure of a fourth embodiment of a disc motor provided by the present invention; Figure 12 for Figure 11 A schematic diagram of the structure of the disc motor (from another perspective); Figure 13 for Figure 15 Side view of the disc motor; Figure 14 An exploded view of the structure of a fifth embodiment of a disc motor provided by the present invention; Figure 15 for Figure 14 A schematic diagram of the structure of the disc motor (with added air guide cover); Figure 16 A schematic diagram of the sixth embodiment of a disc motor provided by the present invention; Figure 17 for Figure 16 A schematic diagram of the structure of the disc motor (with added air guide cover); Figure 18 A schematic diagram of the first structure of a heat dissipation fin for a disc motor provided by the present invention; Figure 19 This is a schematic diagram of a second structure of the heat dissipation fins for a disc motor provided by the present invention.

[0017] Explanation of icon numbers: 100 Air-cooled motor; 1 Housing; 11 First end; 12 Second end; 13 Guide plate; 14 Shaft hole; 15 Front shell; 16 Rear shell; 2 Air guide shroud; 21 Air inlet; 22 Air outlet; 221 Air outlet; 23 External air duct; 231 First flow path; 232 Second flow path; 233 Front air duct; 234 Rear air duct; 241 Air outlet side plate; 3 Airflow drive assembly; 4 Heat dissipation structure; 41 Heat dissipation fins; 411 Fin assembly; 4111 Thin plate; 4112 Arc-shaped guide section; 412 Heat dissipation channel; 42 Back plate; 5 Mounting support; 51 Mounting feet; 52 Mounting groove; 53 Mounting plate; 54 Clearance space; 55 Stop; 6 Flexible transmission component; 7 Mounting protrusion; 8 Powertrain; 81 Rotor shaft.

[0018] 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

[0019] 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.

[0020] Disc motors are characterized by short axial dimensions and high power density. The internal heating elements are compactly arranged, resulting in a large heat load per unit volume, which places high demands on air-cooling capabilities. To improve heat dissipation, a forced air-cooling structure is typically incorporated, and heat dissipation fins are installed on the motor housing to increase the heat dissipation area.

[0021] To ensure uniform temperature distribution across the entire machine, improve heat transfer efficiency in localized areas of the motor, enhance the heat dissipation effect of the heat sink fins, and facilitate overall motor assembly, this invention improves the structure of the air-cooled motor 100. The structure of the air-cooled motor 100 is described in detail below with reference to the accompanying drawings.

[0022] Please see Figure 1 , Figure 5 , Figure 8 , Figure 11 , Figure 14 as well as Figure 16The air-cooled motor 100 includes a housing 1, an air guide shroud 2, an airflow drive assembly 3, a heat dissipation structure 4, and a mounting support 5. The housing 1 has a first end 11 and a second end 12 arranged opposite each other along the axial direction. The interior of the housing 1 forms a space for accommodating a power assembly 8. The power assembly 8 may include rotating components, a stator component, and a support component that cooperates with the rotating components. The specific internal composition of the power assembly 8 does not affect the separate configuration of the fin assembly 411 and the mounting support 5 in this embodiment. The peripheral portion of the housing 1 surrounds the power assembly 8. The peripheral portion can be a continuous outer wall or composed of multiple circumferentially connected housing segments.

[0023] The air guide shroud 2 covers the periphery of the housing 1, forming an external air duct 23 around the outer periphery of the housing 1. The cooling airflow within the external air duct 23 flows and exchanges heat around the outer periphery of the housing. The air guide shroud 2 defines the flow boundary of the cooling airflow and allows the cooling airflow to pass through the heat exchange area around the outer periphery of the housing 1 during its movement from the air inlet 21 to the air outlet 221.

[0024] Both the air inlet 21 and the air outlet 221 are connected to the external air duct 23. The airflow drive assembly 3 can be arranged at the air inlet 21 or at the air outlet 221. When the airflow drive assembly 3 is working, it generates a driving force at the air inlet 21 to drive the airflow into the external air duct 23, or generates a driving force at the air outlet 221 to draw the airflow out of the external air duct 23.

[0025] After the cooling airflow enters the external air duct 23, it flows along the outer peripheral surface of the housing 1 and absorbs the heat transmitted from the housing 1, and then is discharged through the air outlet 221. Thus, the heat generated by the powertrain 8 can be transferred to the cooling airflow through the housing 1 and discharged with the cooling airflow from the peripheral area of ​​the air-cooled motor 100.

[0026] In the technical solution of the present invention, the cooling airflow does not enter the inner cavity of the air-cooled motor 100, but forms a surrounding external air duct 23 on the outer periphery of the housing 1 of the air-cooled motor 100. The heat generated by the front and rear stators is conducted outward through the outer wall of the housing 1, and the heat is carried away synchronously and uniformly by the airflow in the same annular air duct, so that the heat dissipation conditions of the front and rear stators are basically the same, thereby improving the uniformity of the temperature field of the whole machine.

[0027] The external air duct 23 is formed between the air guide shroud 2 and the housing 1. The external air duct 23 is regular and continuous, and the airflow flows smoothly along the external air duct 23 with almost no direct frontal impact, thereby reducing the friction resistance and local eddy current loss of the external air duct 23, and thus improving energy utilization efficiency. Moreover, the smooth flow of the unimpeded airflow along the predetermined flow channel improves the heat dissipation and heat exchange utilization efficiency of the air-cooled motor 100 at all points.

[0028] Meanwhile, the external air duct 23 is arranged around the outer periphery of the housing 1, thereby achieving large-area forced convection heat transfer around the outer periphery of the housing 1. This allows the heat generated by the powertrain 8 during operation to be smoothly transferred to the housing 1 and from the housing 1 to the cooling airflow within the external air duct 23. The external air duct 23, being arranged around the outer periphery of the housing 1, can also quickly dissipate the heat accumulated in the housing 1, thus preventing localized hot spots and excessive temperature rise in the air-cooled motor 100. This keeps the long-term operating temperature of the air-cooled motor 100 within a reasonable range, improving the continuous operating stability of the air-cooled motor 100, delaying component aging, and extending the overall service life of the machine.

[0029] Furthermore, the air guide cover 2 has an air inlet 21 and an air outlet 221 that connect to the external air duct 23. The air inlet 21 and the air outlet 221 can be flexibly arranged according to the installation scenario. The airflow drive component 3 can be installed at the air inlet 21 or the air outlet 221 as needed, thereby adapting to different installation spaces and heat dissipation airflow requirements.

[0030] Fin assemblies 411 are arranged at both ends of the axial direction. The fin assemblies 411 are also placed in the external air duct 23 and cooled by forced airflow. Both ends of the air-cooled motor 100 have efficient heat dissipation capabilities. In this way, circumferential full-area shell heat exchange and the fin assemblies 411 at both ends can be combined to form heat dissipation, thereby improving the problem of uneven heat dissipation between the front and rear of the air-cooled motor 100 in the axial direction and improving the overall heat exchange utilization rate of the shell.

[0031] Meanwhile, the fin assembly 411 is housed inside the external air duct 23, and the forced cooling airflow continuously washes the fin surface, thereby improving the convective heat transfer capacity of the fin assembly 411 and enhancing the heat dissipation effect of the fin assembly 411.

[0032] Furthermore, the entire installation load is borne by the mounting support 5. The mounting support 5 and the fin assembly 411 are independent of each other and do not come into contact, so the load cannot be transferred to the fin assembly 411. The fin assembly 411 does not need to take into account the mechanical load-bearing capacity, and can be set with a more reasonable height-to-thickness ratio, thereby increasing the heat dissipation area and improving the air-cooling heat dissipation capacity.

[0033] The air-cooled motor 100 is installed and connected to external components via the mounting bracket 5, which makes the installation of the air-cooled motor 100 more convenient. The mounting bracket 5 can be arranged on the periphery of the housing 1 for foot mounting, or arranged on the axial end of the housing 1 for flange mounting, thereby meeting different installation requirements of the air-cooled motor 100.

[0034] Junction box 13 is located on the outside of housing 1 and provides wiring, power supply, or control interfaces for powertrain 8. In the illustrated assembly configuration, junction box 13 is positioned above housing 1, and the junction box 13 is connected to housing 1 via connecting component 12. Junction box 13 is not a mounting support component 5. When the entire unit is installed on external components, the installation load is transferred to the external components by mounting support component 5, thus preventing junction box 13 or fin assembly 411 from bearing the main installation load.

[0035] It should be noted that the air guide shroud 2 can be a single-piece shroud or a split shroud. A split shroud can be formed by joining two shrouds together in the diameter direction of the housing 1, or it can be formed by combining multiple enclosing plates. Each shroud or enclosing plate maintains a predetermined gap with the outer wall of the housing 1 to collectively define the external air duct 23.

[0036] The air inlet 21 and air outlet 221 can be round holes, strip openings, grilles, or interfaces for connecting to external air ducts. For applications that require connection to external air supply or exhaust ducts, the air inlet 21 and air outlet 221 can serve as airflow interfaces connected to the corresponding ducts; for applications without external air ducts, the air inlet 21 and air outlet 221 can face directly toward the external environment.

[0037] It should be noted that the airflow drive assembly 3 may include a fan, blower, or exhaust fan. The airflow drive assembly 3 has a rotatably mounted rotating baffle. When the rotating baffle rotates, it can pump cooling airflow into the external air duct 23 by relying on centrifugal force; alternatively, it can create a negative pressure at the air outlet 221 of the air duct to draw the airflow out of the external air duct 23. The specific structure of the airflow drive assembly 3 can be selected according to the air inlet direction, air outlet direction, external installation space, and the arrangement of the rotating parts of the disc motor.

[0038] The specific shape of the air guide shroud 2 can be adapted to the contour of the housing 1 and the external installation conditions, as long as the continuous airflow relationship of the external air duct 23 on the outer periphery of the housing 1 can be maintained. The external air duct 23 allows the cooling airflow to pass through the outer heat exchange area along the housing 1, which is beneficial for carrying away the heat transferred from the housing 1 away from the air-cooled motor 100.

[0039] The present invention does not impose specific restrictions on the form of the external air duct 23.

[0040] In some embodiments, please refer to Figures 1 to 7The external air duct 23 can adopt a two-way flow configuration arranged in sections along the outer periphery of the housing 1. The air inlet 21 is located axially opposite to the first end 11, and the air outlet 221 is located opposite to the outer peripheral sidewall of the housing 1 and close to the second end 12. After the cooling airflow enters the starting end of the external air duct 23 through the air inlet 21, it is distributed to the first flow path 231 and the second flow path 232 by the flow guide boundary formed between the air guide shroud 2 and the housing 1. Both the first flow path 231 and the second flow path 232 extend axially from the first end 11 toward the second end 12, so that the cooling airflow can cover different areas of the outer periphery of the housing 1.

[0041] In this embodiment, the air inlet 21 is directly opposite the axial position of the first end 11 of the housing 1, and the cooling airflow flows from the first end 11 into the starting end of the external air duct 23. The air outlet 221 is arranged on the outer peripheral side wall of the housing 1 and close to the second end 12, and the cooling airflow forms a flow path of air inlet at the first end 11 → axial conveying on the outer periphery → lateral exhaust.

[0042] The cooling airflow is concentrated at the first end 11 to ensure a consistent initial temperature of the airflow entering the external air duct 23. The exhaust point is close to the second end 12, requiring the cooling airflow to complete its axial journey from the first end 11 to the second end 12 before being exhausted. This prevents the cooling airflow from short-circuiting and flowing out prematurely, ensuring that the entire axial outer wall of the casing 1 is fully flushed and heat-exchanged by the cooling airflow, thus achieving more thorough axial heat dissipation across the entire casing 1.

[0043] Meanwhile, the external air duct 23 includes two branch flow paths arranged in sections along the outer periphery of the casing 1. The two branch flow paths have the same source of air intake, extend axially in parallel, and converge at the outlet 221 at their ends. The two branch flow paths divide the outer periphery of the casing 1 into two heat exchange channels. The two airflows travel axially along both sides of the casing 1 simultaneously, providing full coverage of the outer wall of the casing 1, further making the temperature distribution on the outer periphery of the casing 1 more uniform.

[0044] The cooling airflow is evenly distributed from a single air inlet 21 to two branch channels. The cross-sectional area of ​​each branch channel is smaller, the airflow velocity is increased, the forced convection heat transfer coefficient is increased, and the heat transfer per unit area is higher. In addition, the two branch channels have symmetrical structures and the flow resistance along the path is basically the same, which makes the air volume distribution balanced and the heat dissipation consistent.

[0045] Specifically, the two diversion paths include the first diversion path 231 and the second diversion path 232.

[0046] The first flow path 231 extends axially along a partial outer wall on one side of the outer periphery of the housing 1. The starting end of the first flow path 231 is connected to the air inlet 21, and its end extends toward the circumferential position where the air outlet 221 is located, so that the airflow of the first flow path 231 can directly enter the discharge area near the air outlet 221.

[0047] The second flow path 232 extends from the first end 11 to the second end 12 along a partial outer wall on the other side of the outer periphery of the housing 1. After reaching a position near the second end 12, the second flow path 232 bends in a different direction toward the side where the first flow path 231 is located, so that the end of the second flow path 232 is on the same side as the end of the first flow path 231 and corresponds to the air outlet 221. The purpose of the bend is to allow the airflow located on the other side of the housing 1 to change its flow direction in the vicinity of the second end 12 and converge to the same side of the discharge position as the first flow path 231.

[0048] In this embodiment, the airflow exchanges heat around the outer wall of the housing 1 entirely within the external air duct 23, without penetrating into the stator to absorb heat sequentially. Furthermore, the two airflows within the first flow path 231 and the second flow path 232 simultaneously cool both sides of the housing 1 circumferentially, resulting in a uniform temperature rise across the entire housing 1. The front and rear stators achieve synchronous heat dissipation through heat conduction within the housing 1, thereby reducing the temperature difference between the front and rear stators, improving the uniformity of the overall temperature field, and ultimately enhancing the heat dissipation effect of the air-cooled motor 100.

[0049] Meanwhile, the airflow in the first flow path 231 and the second flow path 232 is finally discharged from the air outlet 221 in the same area of ​​the air guide shroud 2. The air outlet 221 is concentrated and not dispersed, which not only enables directional exhaust of the first flow path 231 and the second flow path 232, but also prevents hot air from being emitted from multiple places around the air-cooled motor 100, avoiding hot air reflow and being sucked back into the air inlet 21 to form a hot air circulation, thereby preventing the intake air temperature from rising and reducing the cooling capacity.

[0050] Furthermore, in order to achieve simultaneous exhaust from the first flow path 231 and the second flow path 232 on the same side, the end of the second flow path 232 bends in the opposite direction toward the side where the first flow path 231 is located. When the end of the second flow path 232 bends in the opposite direction, the airflow direction changes slightly, generating moderate turbulence in the bending area, thereby increasing the convective heat transfer coefficient in that area. The bending position is located at the second end 12 of the casing 1, which precisely targets the area where heat easily accumulates at the second end 12 of the air-cooled motor 100, enhancing heat dissipation and further reducing the axial temperature difference of the entire unit.

[0051] The present invention does not impose specific restrictions on the arrangement and coverage area of ​​the first flow path 231 and the second flow path 232.

[0052] In the first embodiment, please refer to Figures 1 to 4 The first flow path 231 and the second flow path 232 are arranged opposite each other in the diametrical direction of the housing 1. The first flow path 231 corresponds to a local area on one side of the outer periphery of the housing 1, and the second flow path 232 corresponds to a local area on the other side of the outer periphery of the housing 1. The circumferential coverage of the two flow paths complement each other to cover the entire outer periphery of the housing 1. After the cooling airflow enters through the air inlet 21, it can flow towards the second end 12 along the opposite outer periphery areas, thereby avoiding the airflow from concentrating only on one side of the outer wall of the housing 1.

[0053] In this embodiment, the first flow path 231 and the second flow path 232 are arranged in a convective manner and fully cover the outer periphery of the housing 1, so that the entire circumferential outer wall of the housing 1 is wrapped and cooled by the two airflows. The heat at each position of the stator in the circumference can be quickly carried away by the airflow through the housing 1, thereby further reducing the circumferential temperature difference.

[0054] The airflow coming in through the air inlet 21 is directly divided into two opposing flow paths. After the airflow is divided into two, each flows forward. The two airflows are mutually separated and depressurized, reducing the overall airflow resistance of the air duct. Under the same fan power, the cooling air volume is larger and the heat dissipation efficiency is higher.

[0055] Meanwhile, the complete outer perimeter of the full-coverage housing 1 means that the entire axial outer surface of the housing 1 is covered by airflow. The heat exchange conditions of the first end 11 and the second end 12 of the housing 1 are the same, the axial temperature rise gradient of the housing 1 itself is extremely small, and the front and rear stators rely on the uniform heat conduction of the housing 1 to dissipate heat, further reducing the temperature difference between the front and rear stators, improving the uniformity of the temperature field of the whole machine, and thus improving the heat dissipation effect of the air-cooling system 100.

[0056] Furthermore, the entire outer periphery of the casing 1 serves as an effective airflow duct, with no idle, windless areas. This prevents localized air stagnation and heat accumulation around the casing 1, ensuring that the entire outer periphery of the casing 1 participates in forced convection heat exchange, thereby further improving space utilization and heat dissipation efficiency.

[0057] In the second embodiment, please refer to Figures 5 to 7 The outer periphery of the casing 1 can also be provided with two sets of external air ducts 23 facing each other along the first diameter direction. Each set of external air ducts 23 includes a first flow path 231 and a second flow path 232. The first flow path 231 and the second flow path 232 in each set are arranged separately along the second diameter direction, with the first diameter direction and the second diameter direction forming an angle. The flow path arrangements of the two sets of external air ducts 23 are reversed.

[0058] Please see Figure 8 The directional coordinate system in the diagram further provides spatial indications for the up / down, left / right, and front / back directions. The housing 1 can select two intersecting diameter reference directions, where the first diameter direction and the second diameter direction are set at an angle. The angle between the first diameter direction and the second diameter direction can be a right angle or another angle to meet the requirements of staggered airflow arrangement. Please refer to... Figure 8 and Figure 9 The axial direction can be front-to-back, the first diameter direction can be up-and-down, and the second diameter direction can be left-and-right. These front-to-back, up-and-down, and left-and-right directions are merely illustrative orientations for the illustrated installation position; the product can still be installed in other spatial orientations after being rotated.

[0059] That is, in the illustrated example, the two flow paths within each group are arranged separately in the left-right direction. The airflow input from the air inlet 21 is distributed to the upper and lower external air ducts 23 respectively. Since the flow path arrangement of the two external air ducts 23 is reversed, the first flow path 231 and the second flow path 232 within the upper and lower groups are distributed in opposite directions in the left-right position, thus making the two groups of airflow relationships mirror or reversed.

[0060] It should be noted that the two sets of external air ducts 23 can be arranged symmetrically, approximately symmetrically, or not symmetrically due to the constraints of the positions of the air inlet 21, air outlet 221, junction box-like structural components 3 and external connection interfaces.

[0061] Meanwhile, the air guide shroud 2 is provided with two air outlets 221 at positions corresponding to the two first flow paths 231 respectively. Each air outlet 221 is connected to the end of the flow path of the corresponding set of external air ducts 23, and the cooling airflow can be discharged to the outside through its respective air outlet 221.

[0062] In other words, the air guide hood 2 can be provided with two air outlets 221 in the second diameter direction. The two air outlets 221 are staggered in the first diameter direction, so that the upper external air duct 23 and the lower external air duct 23 can both work according to the logic of "the first flow path 231 directly sends and discharges, and the second flow path 232 sends and then reverses to discharge".

[0063] The staggered arrangement here can be understood as the two air outlets 221 not being located in exactly the same vertical position, but rather corresponding to the height sections of their respective external air ducts 23. The two sets of external air ducts 23 can be arranged approximately symmetrically, or they can have local dimensional differences due to assembly space, shell connection area, or external interference; the amount of misalignment between the two air outlets can also be determined according to the shell width, installation interference, and exhaust path adaptation.

[0064] Specifically, the first diameter direction is the up-down direction, and the two sets of external air ducts 23 are arranged opposite each other in the up-down direction; the second diameter direction is the left-right direction, and the first flow path 231 and the second flow path 232 in each set of external air ducts 23 are arranged separately in the left-right direction, and the flow path arrangement orientations of the two sets of external air ducts 23 are reversed.

[0065] That is, the first flow path 231 located on the left side in the upper external air duct 23 can be located on the right side in the lower external air duct 23, and the second flow path 232 located on the right side in the upper external air duct 23 can be located on the left side in the lower external air duct 23. Through this inverted relationship, the exhaust position is more easily distributed in both vertical and horizontal directions, which helps to reduce the situation where multiple streams of hot air are concentrated on the same local area.

[0066] In this embodiment, the upper and lower sets of external air ducts 23 face each other and surround the entire outer wall of the housing 1. Forced airflow scours and heats the entire outer wall of the housing 1 on the upper, lower, left and right sides, which not only eliminates the axial front and rear stator temperature difference, but also avoids circumferential local hot spots, thereby reducing the circumferential and axial temperature gradient of the housing, improving the uniformity of the temperature field of the whole machine, and thus improving the heat dissipation effect of the air cooling system 100.

[0067] The upper and lower sets of external air ducts 23 allow the airflow to be gradually split after entering through the air inlet 21. Each air duct has a smaller cross-sectional area and a more regular airflow path, thereby reducing turbulence and pressure loss along the flow path. Furthermore, the multiple air paths distribute the total air volume, and the single-path flow velocity is reasonable. This avoids both excessive wind speed causing loud noise and insufficient air volume resulting in inadequate heat dissipation, thus enhancing the overall stability of air supply.

[0068] Meanwhile, the two air outlets 221 are separated horizontally and staggered vertically. This opposite-side exhaust avoids turbulent airflow, ensuring smooth exhaust without mutual interference. The staggered arrangement disperses the exhausted hot air in different directions, preventing concentrated hot air from flowing back into the air inlet 21, thus avoiding hot air recirculation that could lead to increased intake temperature and reduced heat dissipation. Furthermore, the zoned airflow allows for easy connection to external ductwork as needed, adapting to different installation conditions.

[0069] In the aforementioned single or double duct schemes, several optional structural limitations may also be adopted.

[0070] Please see Figure 7 , Figure 8 and Figure 9 In one embodiment, two air outlets 221 may be provided on the same side. The two air outlets 221 serve as the discharge areas of two branching paths, respectively. The end of the first flow path 231 is connected to one of the air outlets 221, and the end of the second flow path 232 is connected to the other air outlet 221; or, the first flow path 231 and the second flow path 232 are respectively connected to two corresponding air outlet areas according to a predetermined flow direction.

[0071] In this embodiment, the end of the first flow path 231 is connected to one of the air outlets 221, and the end of the second flow path 232 is connected to the other air outlet 221. The airflow from the two branched flow paths is directly discharged from their respective corresponding air outlet areas, making the flow field at the air outlet 221 more stable. This reduces the additional pressure loss caused by the exhaust from the same side of the first flow path 231 and the second flow path 232, thereby reducing the kinetic energy loss of the airflow and improving the overall flow efficiency of the air-cooling system 100.

[0072] Meanwhile, the two branch paths correspond one-to-one with the two air outlets 221, so that the pressure gradient of the entire air duct from the air inlet to the air outlet is continuous and smooth, thereby enabling the airflow to flow along the outer circumference of the casing 1 at a stable flow rate, thus making the heat exchange intensity of the casing 1 consistent from the first end 11 to the second end 12, and further improving the uniformity of the temperature field of the whole machine.

[0073] Specifically, the flow boundaries of the two branch paths are jointly defined by the inner wall of the air guide shroud 2 and the outer wall of the casing 1. The inner wall of the air guide shroud 2 defines the boundary for the outward dissipation of airflow, while the outer wall of the casing 1 forms the surface for heat exchange of the airflow.

[0074] 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 casing 1, and flows close to the outer surface of the casing 1 along this channel. Since the flow boundary is jointly defined by the inner wall of the air guide shroud 2 and the outer wall of the casing 1, the airflow can be pushed forward along the outer wall of the casing 1 in a restricted manner, thereby allowing the cold airflow to participate more fully in the heat exchange of the outer wall of the casing 1.

[0075] A partition 13 protrudes from the outer peripheral sidewall of the housing 1 near the second end 12. The partition 13 extends along the diameter of the housing 1 and is inserted into the air outlet 22. The partition 13 divides the air outlet 22 into two air outlets 221 and ensures that the two branch paths maintain their respective flow boundaries when approaching the air outlet position.

[0076] Thus, although the first flow path 231 and the second flow path 232 are air outlets on the same side, they are clearly separated at the outlet end by a solid partition 13. The first flow path 231 is discharged from one of the air outlets 221, and the second flow path 232 is discharged from the other air outlet 221.

[0077] In addition to the two-way branching configuration with zoned layouts, please refer to [link / reference]. Figures 8 to 10 In the third embodiment, the external air duct 23 can also adopt a straight-through configuration that completely surrounds the outer periphery of the housing 1 in the circumferential direction. In this embodiment, the air inlet 21 is located axially opposite to the first end 11, and the air outlet 221 is located axially opposite to the second end 12. The air guide shroud 2 forms a continuous annular guiding space around the outer periphery of the housing 1, and the external air duct 23 extends from the first end 11 to the second end 12. After entering through the air inlet 21, the cooling airflow can flow axially along the complete outer periphery of the housing 1 towards the second end 12 and be discharged through the air outlet 221.

[0078] In this embodiment, the air guide shroud 2 is completely covered around the outer periphery of the housing 1, forming a sandwich-type external air duct 23 between the air guide shroud 2 and the housing 1. The external cooling airflow enters from the air inlet 21 at the second end 12 position and flows backward along the external air duct 23. The airflow sweeps across the surface of the housing 1 for heat exchange without frontal forced impact, thus avoiding direct impact of the airflow on the housing 1.

[0079] The air guide shroud 2 and the casing 1 together form a through and directional external air duct 23. The airflow is constrained within the fixed channel and flows orderly from front to back in a unidirectional manner, avoiding disorderly diffusion and impact losses. At the same time, the airflow is driven by the airflow drive component 3 to flow from the air inlet 21 into the external air duct 23 and out of the air outlet 221, rather than being forcibly pushed by the airflow from the second end 12. This makes the airflow within the external air duct 23 orderly and stable, with little turbulence and pressure loss, thereby reducing airflow resistance and minimizing the ineffective loss of airflow kinetic energy.

[0080] Meanwhile, the external air duct 23 is arranged around the outer periphery of the casing 1. The large area of ​​the outer circumference of the casing 1 can contact and exchange heat with the cooling airflow in the external air duct 23, thereby increasing the air cooling coverage and allowing heat to be transferred from multiple parts of the casing 1 to the airflow simultaneously, thus improving the heat exchange efficiency.

[0081] Furthermore, the external air duct 23 is arranged around the outer periphery of the housing 1, and the airflow covers the outer side of the housing 1 circumferentially and flows continuously along the axial direction. The air cooling conditions in all areas of the housing 1 are balanced, thereby preventing heat from accumulating at a certain location of the air-cooled motor 100 and avoiding local hot spots and excessive temperature rise. As a result, the long-term operating temperature of the air-cooled motor 100 is kept within a reasonable range, which can improve the continuous operation stability of the air-cooled motor 100, delay the aging of components, and extend the service life of the entire machine.

[0082] In addition to the axially extended configuration described above, please refer to the external flow channel 23 for other configurations. Figures 11 to 13 In the fourth embodiment, the housing 1 includes a front housing 15 and a rear housing 16 joined together axially. The air guide shroud 2 has opposing air inlets 21 and outlets 221 at positions corresponding to the periphery of the housing 1. The external air duct 23 includes a front air duct 233 formed around the periphery of the front housing 15 and a rear air duct 234 formed around the periphery of the rear housing 16. The starting ends of the front air duct 233 and the rear air duct 234 are connected to the air inlets 21, and their ending ends are connected to the outlets 221.

[0083] In this embodiment, a front air duct 233 and a rear air duct 234 are arranged in parallel. The cold airflow entering from the air inlet 21 enters the front air duct 233 to wrap around the front housing 15 and directly exchange heat with the front stator area; the other enters the rear air duct 234 to wrap around the rear housing 16 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 air-cooled motor 100.

[0084] Meanwhile, both the air inlet 21 and the air outlet 221 are located on the periphery of the housing 1, and the front air duct 233 and the rear air duct 234 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 air-cooled motor 100. Furthermore, the air inlet 21 or the air outlet 221 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 233 and optimizes the heat dissipation conditions in the front stator area, but also enhances the assembly versatility of the air-cooled motor 100.

[0085] Please see Figures 11 to 13 The front housing 15 and the rear housing 16 enclose the inner cavity of the housing 1, within which the powertrain 8 is located. The rotor shaft 81 of the powertrain 8 extends axially along the housing 1, with both ends of the rotor shaft 81 passing through the front housing 15 and the rear housing 16, respectively. The rotor shaft 81 is capable of outputting rotational power during operation of the powertrain 8. The flexible transmission member 6 is bent, with one end connected to the rotor shaft 81 and the other end connected to the airflow drive assembly 3.

[0086] In this embodiment, during the operation of the powertrain 8, the rotational power output by the rotor shaft 81 is transmitted to the airflow drive assembly 3 via the flexible transmission component 6, enabling the airflow drive assembly 3 to synchronously generate cooling airflow. This transmission method utilizes the rotation of the rotor shaft 81 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.

[0087] Meanwhile, the flexible transmission component 6 can be bent and rotated arbitrarily, without being limited by the angle or distance between the extended end of the rotor shaft 81 and the installation position of the airflow drive component 3. In the above embodiment, the air inlet 21 and the air outlet 221 are arranged on the periphery of the housing 1. The rotor shaft 81 extends along the axial direction of the air-cooled motor 100, 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 6, without modifying the main air duct structure of the housing 1 and the air guide shroud 2.

[0088] The flexible transmission component 6 can be a transmission component capable of transmitting rotational power and allowing for a bending path. When transmitting power, the flexible transmission component 6 should maintain effective transmission engagement with the rotor shaft 81 and the airflow drive assembly 3 at both ends respectively. When the path of the flexible transmission component 6 needs to bypass the outer periphery of the housing 1, its bending path can be adjusted according to the relative positions of the air guide shroud 2, the air duct, and the air outlet.

[0089] Specifically, the flexible transmission component 6 can be located in the front air duct 233 or the rear air duct 234. One end of the flexible transmission component 6 is connected to the rotor shaft 81, and the other end is bent and extended radially along the housing 1, and extends out from the air inlet 21 or the air outlet 221 to the outside of the air guide shroud 2 and then connected to the airflow drive assembly 3.

[0090] When the flexible transmission component 6 is arranged in the front air duct 233, it can extend along the air duct space around the front shell 15; when the flexible transmission component 6 is arranged in the rear air duct 234, it can extend along the air duct space around the rear shell 16. The specific bending direction of the flexible transmission component 6 can be selected based on the different positions of the airflow drive component 3 at the air inlet 21 or the air outlet 221.

[0091] In this embodiment, the flexible transmission component 6 is directly arranged in the front air duct 233 or the rear air duct 234, rather than being exposed on the outside of the air guide shroud 2; only the end of the flexible transmission component 6 passes through the air inlet 21 or the air outlet 221 and connects with the airflow drive component 3, thereby making the overall outer contour of the air-cooled motor 100 neat and simple.

[0092] Furthermore, the flexible transmission component 6 is mostly made of polymer or rubber materials such as belts, nylon transmission belts, and flexible chains, which are prone to heat generation and aging under long-term stress and friction. The flexible transmission component 6 travels through the front air duct 233 or the rear air duct 234 throughout the entire process. The cooling airflow continuously surrounds and washes the flexible transmission component 6, carrying away the heat generated by transmission friction, preventing the flexible transmission component 6 from softening, loosening, and breaking at high temperatures, thereby reducing the wear rate of the flexible transmission component 6.

[0093] In one embodiment, please refer to Figure 2 and Figure 3 A power assembly 8 is housed within the housing 1. The rotor shaft 81 of the power assembly 8 extends axially along the housing 1, with its two ends facing the first end 11 and the second end 12, respectively, and passing through their respective end regions. The disc motor also includes a back plate 42, which is detachably mounted to at least one of the first end 11 and the second end 12. The back plate 42 is a plate-shaped receiving component located between the end of the housing 1 and the fin assembly 411. Its side facing the housing 1 can be fitted with the end face of either the first end 11 or the second end 12, while its side facing away from the housing 1 is used to mount the fin assembly 411.

[0094] The back plate 42 has a through hole that extends through the back plate 42 along the axial direction of the housing 1, allowing the end of the rotor shaft 81 to pass through. The wall of the through hole maintains the clearance relationship required for rotation between the back plate 42 and the rotor shaft 81, so that the back plate 42 does not obstruct the operation of the power assembly 8 due to the end of the rotor shaft 81 passing through.

[0095] The fin assembly 411 is disposed on the side surface of the back plate 42 facing away from the housing 1. The back plate 42 serves as both the mounting base surface for the fin assembly 411 and a heat transfer component at the end of the housing 1, allowing heat from the end of the housing 1 to be transferred to the thin plate 4111 via the back plate 42.

[0096] The fin assembly 411 is broken at the location corresponding to the through hole and the area surrounding the through hole. The area surrounding the through hole is a buffer zone extending outward from the through hole, which is used to accommodate the movement, assembly, or maintenance space near the end of the rotor shaft 81. The thin plate 4111 does not cross the through hole, nor does it form a continuous obstruction in the area surrounding the through hole, allowing the end of the rotor shaft 81 to pass axially through the back plate 42 and providing assembly space for external components connected to the end of the rotor shaft 81. The break position can be manifested as a partial absence of the thin plate 4111, an enlarged gap between adjacent thin plates 4111, or an outward retraction of the extension boundary of the thin plate 4111 in the area surrounding the through hole; the specific break form can be determined according to the dimensions of the end of the rotor shaft 81 and the external connection type.

[0097] For configurations suitable for installation onto an external support base, please refer to [link / reference]. Figure 2 and Figure 5 In the first embodiment, a mounting protrusion 7 is provided on the peripheral side of the housing 1 at the corresponding bottom position. The mounting protrusion 7 protrudes outward from the peripheral outer wall of the housing 1 and forms a shape that matches the mounting foot 51 along the axial or circumferential direction of the housing 1.

[0098] The mounting support 5 is configured as a plate-shaped mounting foot 51, which is located at the bottom of the side of the housing 1. The lower surface of the mounting foot 51 forms a mounting surface facing the external support base. The mounting foot 51 is provided with a mounting groove 52, which opens to the side facing the housing 1, and the shape of its groove wall is adapted to the mounting protrusion 7.

[0099] During assembly, the mounting protrusion 7 is inserted into the mounting groove 52 along the opening direction of the mounting groove 52. The mounting groove 52 forms a lateral containment and positional constraint on the mounting protrusion 7. Then, the mounting foot 51 is fixed to the housing 1 through a detachable connection.

[0100] After the mounting protrusion 7 is inserted into the mounting groove 52, the mounting foot 51 can form a relatively stable load-bearing support on the side of the housing 1. The mounting groove 52 can extend axially along the housing 1, allowing the mounting foot 51 to be inserted from one end of the housing 1. This assembly direction is suitable for installation when the end of the housing 1 is open.

[0101] Alternatively, a local groove shape corresponding to the bottom contour of the housing 1 can be used, so that the mounting feet 51 approach the housing 1 radially or obliquely and complete the fitting. This assembly direction is suitable for installation from the periphery after the main body of the housing 1 has been assembled.

[0102] Mounting feet 51 may have mounting holes on their mounting surfaces for connecting to an external support base. The positions of the mounting holes correspond to the connection holes of the external support base. After the mounting bolts pass through the mounting holes, the mounting feet 51 are fixed to the external support base. Mounting feet 51 may also have threaded holes for tightening or auxiliary positioning, but their specific number and distribution are determined according to the connection layout of the external support base and are not limited to the number shown in the figure.

[0103] The insertion and engagement of the mounting protrusion 7 and the mounting groove 52 is mainly used to limit the relative movement between the mounting foot 51 and the housing 1. The overall weight of the machine, the installation reaction force and the installation load during operation applied by the external support base are transmitted to the mounting foot 51 through the mounting surface, and then to the mounting protrusion 7 and the housing 1 through the groove wall and the fixed connection of the mounting groove 52.

[0104] The fin assembly 411 is located at the end of the housing 1 or in other non-load-bearing areas. The mounting feet 51 are not supported by abutting against the fin assembly 411, so the load path will not pass through the thin plate 4111. The mounting feet 51 can be axially offset from the fin assembly 411, radially spaced, or pass through the non-finned area of ​​the back plate 42. For disc motors that require disassembly and maintenance, the fixed connection between the mounting feet 51 and the housing 1 can be released first, and then the mounting feet 51 can be removed along the mating direction of the mounting groove 52; the fin assembly 411 can remain on the housing 1 or be removed separately.

[0105] Please see Figure 6 , Figure 8 and Figure 9 In the second embodiment, the mounting support 5 is configured as a mounting plate 53, which is located on the side of the fin assembly 411 facing away from the housing 1 and towards the end mounting position of the external equipment. The mounting plate 53 has a mounting surface that faces away from the fin assembly 411 and is exposed outward for docking with the mounting part on the external equipment. The mounting plate 53 has a clearance space 54 that is provided towards the fin assembly 411 for accommodating the fin assembly 411 when the mounting plate 53 is assembled to the housing 1.

[0106] The clearance space 54 can be a recess, opening, or frame-shaped receiving area formed by the mounting plate 53 on the side facing the fin assembly 411, with its boundary avoiding the thin plate 4111, so that the mounting plate 53 will not press on the thin plate 4111 when bearing external loads.

[0107] Mounting plate 53 has an axial clearance hole that passes through it, allowing the end of the rotor shaft 81 of the powertrain 8 to pass through. When mounting plate 53 is aligned with housing 1, the clearance hole corresponds to the axis of rotor shaft 81. As mounting plate 53 moves axially toward housing 1, the end of rotor shaft 81 enters the clearance hole, preventing mounting plate 53 from blocking rotor shaft 81.

[0108] A stop portion 55 protrudes from the end face of the mounting plate 53 opposite to the fin assembly 411, and the stop portion 55 is arranged around the outer edge of the clearance hole. The stop portion 55 can be annular, segmented annular, or have a circumferential structure with multiple positioning protrusions, for insertion into a mating part on the external equipment. The mating part on the external equipment can be a positioning hole, positioning groove, or annular step that mates with the outer or inner circumference of the stop portion 55. When the mounting plate 53 is close to the external equipment, the stop portion 55 first inserts and positions itself with the mating part, and then locks it in place through the mounting hole and fasteners. In this way, the docking load of the external equipment is transferred to the housing 1 by the mounting surface of the mounting plate 53 and the stop portion 55, instead of being borne by the fin assembly 411.

[0109] The mounting plate 53 can be fixed to the housing 1 through the connection area around the periphery of the mounting plate 53, the solid area at the end of the housing 1, or the connection area on the back plate 42. The mounting plate 53 and the fin assembly 411 have an axial clearance space 54, so even if the mounting plate 53 covers the projected area of ​​the fin assembly 411, it will not directly abut against the thin plate 4111. The mounting plate 53 can be fitted from the axial end after the main body of the housing 1 is assembled, or it can be first assembled into a mounting module with the back plate 42 or other end components and then connected to the housing 1.

[0110] If the external equipment requires the mounting surface to be located at the first end 11, the mounting plate 53 can be arranged at the first end 11; if the mounting surface is required to be located at the second end 12, the mounting plate 53 can be arranged at the second end 12. When both ends need to be connected, mounting plates 53 can be set at both ends respectively, but each mounting plate 53 should maintain an independent avoidance relationship with the fin assembly 411 and the end of the rotor shaft 81.

[0111] The present invention does not impose specific restrictions on the arrangement of the heat dissipation fins 41.

[0112] Please see Figure 18 In the first arrangement embodiment of the heat dissipation fins 41, the heat dissipation structure 4 includes at least four sets of fin groups 411 arranged around the shaft hole 14. The four sets of fin groups 411 are arranged in a cross-shaped orthogonal symmetrical distribution with the center of the end of the housing 1 as the array center.

[0113] The fin assembly 411 extends in a fan shape from the center of the end of the housing 1 to its periphery, including multiple layers of thin plates 4111 arranged radially. A heat dissipation channel 412 is formed between two adjacent layers of thin plates 4111 along the axial direction. Each thin plate 4111 extends radially outward from the central region of the end of the housing 1 and is partially bent. The extended end of the thin plate 4111 extends beyond the outer edge of the housing 1 and is bent and extended axially along the outer peripheral sidewall of the housing 1, so that the heat dissipation channel 412 on the end of the housing 1 extends to the outer periphery of the housing 1.

[0114] In the technical solution of the present invention, four sets of fin groups 411 are arranged around the shaft hole 14 at the end of the housing, and are distributed in a cross-shaped orthogonal symmetrical manner. Each set of fins is composed of multiple layers of parallel radial thin sheets, and adjacent thin sheets form an axially connected heat dissipation channel 412. The fin sheets are bent and extended radially outward from the central region at the end of the housing 1, and extend beyond the outer edge of the housing 1. The outer end of the thin sheet is attached to the outer wall of the housing 1 and bends and extends axially, so that the heat dissipation channel 412 at the end of the housing 1 is connected and extends to the outer periphery of the housing 1.

[0115] Four sets of fins 411 are provided at the end of the casing 1. The four sets of fins 411 are arranged in a cross-shaped orthogonal symmetrical distribution with the center of the end of the casing 1 as the array center, and a circumferentially transparent clearance is naturally formed between the sets. The fin sets 411 extend in a fan shape from the center of the end of the casing 1 to its periphery, including multiple layers of thin plates 4111 arranged radially. A heat dissipation channel 412 is formed between adjacent layers of thin plates 4111 along the axial direction. In this way, the cooling airflow can be allowed to enter and exit directly along the axial direction along the heat dissipation channel 412, and the circumferential circulation and lateral convection can be achieved by utilizing the partition gaps of the four sets.

[0116] The thin plate 4111 extends radially outward from the central region of the end of the housing 1 and is partially bent. The extended end of the thin plate 4111 extends beyond the outer edge of the housing 1 and is bent axially along the outer peripheral sidewall of the housing 1, so that the heat dissipation channel 412 on the end of the housing 1 extends to the outer periphery of the housing 1. In this way, the heat dissipation channel 412 at the end of the housing 1 can be extended and connected to the outer periphery of the housing 1, forming a continuous and through three-dimensional heat dissipation channel 412 at the end of the housing 1 and the outer periphery of the housing 1. The airflow can circumferentially circumferentially and axially pass through, thereby improving the circumferential heat dissipation capacity.

[0117] The fin assembly 411 extends radially from the central area at the end of the housing 1 and then bends to cover the housing 1, forming a continuous heat conduction path from the end of the housing 1 to the fins to the outer wall of the housing 1. Heat inside the motor can be quickly conducted to the external heat dissipation parts, resulting in uniform temperature rise throughout the unit, preventing localized overheating, and ensuring consistent cooling. Furthermore, the zoned layout combined with axial straight-through flow channels reduces wind resistance compared to densely distributed fins, ensuring smooth airflow, preventing dust accumulation and clogging of the air ducts, and maintaining stable long-term heat dissipation performance.

[0118] Meanwhile, the four sets of fins 411 are symmetrically orthogonal, and the thin plates 4111 of the fin sets 411 are all radially extended and then axially bent along the outer wall of the housing 1, avoiding excessive radial expansion. This results in a regular and symmetrical overall layout with a controllable outer contour, ensuring heat dissipation performance while constraining the radial dimensions of the entire motor, making it suitable for narrow installation spaces. Furthermore, the four sets of fins are symmetrically orthogonal, ensuring uniform distribution of stress and heat dissipation loads at the ends of the housing 1, thereby reducing housing deformation.

[0119] Please see Figure 19In the second arrangement embodiment of the heat dissipation fins 41, two sets of fin groups 411 are provided at the end of the housing 1 and are symmetrically distributed along its horizontal axis. The fin group 411 includes a plurality of thin plates 4111 arranged in parallel in the vertical direction. Both ends of the thin plates 4111 extend beyond the outer edge of the housing 1 and are bent and extended axially along its outer wall. A portion of the thin plates 4111 located in the central region of the end of the housing 1 is broken at the position corresponding to the shaft hole 14 and its surrounding area. A portion of the thin plates 4111 is connected to the arc-shaped guide section 4112 along the circumference of the shaft hole 14 at its break point.

[0120] In the technical solution of the present invention, multiple thin plates 4111 are arranged vertically and parallel. Both ends of the thin plates 4111 extend beyond the outer edge of the housing 1 and are bent and extended axially along its outer wall. In this way, the total heat exchange area of ​​the fin assembly 411 can be increased, thereby enhancing the heat dissipation efficiency and meeting the heat dissipation requirements of the disc motor under high load conditions.

[0121] Meanwhile, the thin plate 4111 in the central area is disconnected at the shaft hole 14 and its surrounding area, which directly reserves installation space for components such as shafts and bearings. There is no need to reduce the main structure of the thin plate 4111 to avoid the shaft hole 14, thus taking into account both heat dissipation performance and shaft installation requirements.

[0122] Furthermore, a portion of the thin plate 4111 located in the central region of the end of the casing 1 is broken at the position corresponding to the shaft hole 14 and its surrounding area. At the break point, the portion of the thin plate 4111 connects to the arc-shaped guide section 4112 along the circumference of the shaft hole 14. The arc-shaped guide section 4112 smoothly transitions the end of the broken thin plate 4111, forming a continuous guide surface surrounding the shaft hole 14. This eliminates airflow vortices and dead zones near the shaft hole 14, enhances airflow disturbance, further improves the convective heat transfer coefficient, and avoids local overheating in the central region.

[0123] The two sets of fins 411 are symmetrically distributed along the horizontal axis, and the heat can be evenly conducted to the upper and lower sides. Combined with the airflow guidance of the arc-shaped guide section 4112, the temperature field distribution at the end of the housing 1 is more uniform, thereby avoiding damage to the motor windings and bearings due to local overheating, and thus improving the stability and life of the motor operation.

[0124] Furthermore, the two ends of the thin plate 4111 are bent and extended axially along the outer wall of the housing 1, forming an auxiliary support structure for the housing 1. This improves the overall rigidity of the housing 1, reduces vibration deformation under high load conditions, and thus reduces noise and the risk of fatigue failure. The arc-shaped guide section 4112 smoothly connects the broken thin plate 4111, avoiding stress concentration at the break point of the thin plate 4111. This improves the strength and service life of the fin assembly 411, thereby enhancing the overall structural reliability and stability.

[0125] 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. An air-cooled motor, characterized in that, include: The housing has a first end and a second end opposite each other in its axial direction; An air guide cover is provided to cover the outer periphery of the housing, and an external air duct is formed between the two and arranged around the outer periphery of the housing. The cooling airflow in the external air duct flows and exchanges heat around the outer periphery of the housing. An air inlet and an air outlet are provided on the air guide cover to connect the external air duct. An airflow drive component is located at the air inlet or the air outlet; A heat dissipation structure includes heat dissipation fins disposed at the first end and / or the second end, the heat dissipation fins being in thermal contact with the housing and housed within the external air duct; and, The mounting support is detachably installed on the housing and is independent of and does not abut against the heat dissipation fins. The mounting support is assembled with the air guide shroud, and its side surface facing away from the air guide shroud forms an exposed mounting surface for docking with the external components.

2. The air-cooled motor according to claim 1, characterized in that, The air guide shroud has an air inlet at a position axially opposite to the first end, and an air outlet at a position opposite to the outer peripheral sidewall of the housing and close to the second end. The external air duct includes two branch paths arranged in sections along the outer periphery of the housing. Both branch paths extend axially from the first end toward the second end, and their starting ends are connected to the air inlet, while their ending ends are connected to the air outlet on the same side.

3. The air-cooled motor according to claim 1, characterized in that, The air guide shroud has an air inlet at a position axially opposite to the first end and an air outlet at a position axially opposite to the second end. The external air duct is arranged to completely surround the outer periphery of the housing in the circumferential direction, and extends axially from the first end to the second end, so as to communicate with the air inlet and the air outlet respectively in the axial direction.

4. The air-cooled motor according to claim 1, characterized in that, The housing includes a front housing and a rear housing joined together along the axial direction; the air guide shroud has corresponding air inlets and outlets at positions corresponding to the periphery of the housing. The external air duct includes a front air duct formed on the periphery of the front shell and a rear air duct formed on the periphery of the rear shell. The starting ends of the front air duct and the rear air duct are connected to the air inlet, and the ending ends of the two air ducts are connected to the air outlet.

5. The air-cooled motor according to claim 1, characterized in that, The housing is used to house the powertrain, and the two ends of the rotor shaft of the powertrain pass through the first end and the second end, respectively. The heat dissipation structure also includes a back plate, which is detachably installed at the first end and / or the second end, and the back plate has a through hole for the end of the rotor shaft to pass through. The heat dissipation fins are disposed on the side surface of the back plate away from the housing, and the heat dissipation fins are broken at the positions corresponding to the through holes and their surrounding areas.

6. The air-cooled motor according to claim 1, characterized in that, The peripheral side of the housing has a mounting protrusion at a position corresponding to its bottom. The mounting support is configured as a plate-shaped mounting foot, which is located on the periphery of the housing and corresponds to the bottom of the housing. The mounting foot has a mounting groove for interlocking with the mounting protrusion during assembly. The mounting foot is used to install the housing onto an external support base.

7. The air-cooled motor according to claim 1, characterized in that, The interior of the housing is used to house the powertrain; The mounting support is configured as a mounting plate, which is located on the side of the heat dissipation fins away from the housing. The mounting plate has a clearance space to accommodate the heat dissipation fins when it is assembled to the housing. The mounting plate has a clearance hole along the axial direction to allow the end of the rotor shaft of the powertrain to pass through. The end face of the mounting plate away from the heat dissipation fins has a protruding stop portion, which is arranged around the outer edge of the clearance hole and is inserted and positioned with the mating part on the external equipment when the mounting plate is assembled with the external equipment.

8. The air-cooled motor according to claim 1, characterized in that, The housing is used to house the powertrain, and both the first and second ends have shaft holes for the rotor shaft to pass through. The heat dissipation structure includes two sets of heat dissipation fins, which are respectively disposed at the first end and the second end. Each set of heat dissipation fins forms a clearance area at the position corresponding to the shaft hole and its surrounding area. The end of the heat dissipation fin extends beyond the peripheral outer edge of the housing and is bent and extended axially along its peripheral outer wall.

9. The air-cooled motor according to claim 8, characterized in that, Each set of heat dissipation fins includes at least four sets of fins arranged around the periphery of the shaft hole, and the four sets of fins are arranged in a cross-shaped orthogonal symmetrical distribution with the center of the end of the housing as the array center; The fin assembly extends in a fan shape from the center of the end of the housing to its periphery, including multiple layers of thin plates arranged radially. A heat dissipation channel is formed between two adjacent layers of thin plates along the axial direction. Each thin plate extends radially outward from the central region of the end of the housing and is partially bent. The extended end of the thin plate extends beyond the outer edge of the housing and is bent and extended axially along the outer peripheral sidewall of the housing, so that the heat dissipation channel on the end of the housing extends to the outer periphery of the enclosure.

10. The air-cooled motor according to claim 8, characterized in that, Each set of heat dissipation fins includes two fin groups, which are symmetrically distributed along the first diameter direction of the housing. Each fin group includes multiple thin plates arranged parallel to each other along the second diameter direction of the housing. Both ends of the thin plates extend beyond the outer edge of the housing and are bent and extended axially along the outer peripheral sidewall of the housing. A portion of the thin plates located in the central region of the housing end is broken at the position corresponding to the shaft hole and its surrounding area to form the clearance area. At the break point, a portion of the thin plates is connected to an arc-shaped guide section along the circumference of the shaft hole.

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