Disc motor, powertrain, and electric vehicle

Abstract

Embodiments of the present application provide a disc motor, a powertrain, and an electric vehicle. A stator housing of the disc motor is used for fixing a stator core and integrating cooling flow channels of the stator core; the cooling flow channels include an end surface flow channel, a circumferential surface flow channel, and at least one coupling flow channel; an axial groove bottom of the stator housing is used for integrating the end surface flow channel; and a circumferential groove wall of the stator housing is used for integrating the circumferential surface flow channel. One end surface heat-dissipation segment of the end surface flow channel and a circumferential surface heat-dissipation segment of the circumferential surface flow channel are respectively used for guiding a coolant to flow through the axial groove bottom and the circumferential groove wall in at least one of a counterclockwise direction and a clockwise direction. The circumferential surface heat-dissipation segment and the end surface heat-dissipation segment are communicated with each other by means of one coupling flow channel. All the cooling flow channels are integrated in the stator housing, achieving a compact structure, such that the entire stator core is cooled, improving the cooling efficiency, thereby mitigating the overheating problem in the disc motor.

Description

Disc motors, powertrains and electric vehicles

[0001] This application claims priority to Chinese Patent Application No. 202410490065.2, filed on April 22, 2024, entitled "Disc Motor, Powertrain and Electric Vehicle", the entire contents of which are incorporated herein by reference. Technical Field

[0002] This application relates to the field of electric vehicle technology, and in particular to a disc motor, powertrain, and electric vehicle. Background Technology

[0003] Disc motors are used in electric vehicles and are characterized by their small axial dimensions, compact structure, high power density, and high efficiency. In range-extended electric vehicles, the generator's rated power is close to its peak power, and the vehicle requires the generator to operate continuously at rated power for extended periods, even long periods, making heat generation a particularly prominent issue for disc motors. Currently, cooling is mainly achieved by arranging cooling channels within the disc motor; however, current water-cooling structures for disc motors suffer from limited cooling efficiency and relatively high resistance in the cooling channels. Summary of the Invention

[0004] This application provides a disc motor, a powertrain, and an electric vehicle.

[0005] In a first aspect, embodiments of this application provide a disc motor, which includes a stator core and a slotted stator housing. The stator housing is used to fix the stator core and to integrate cooling channels for the stator core. The cooling channels include an end-face channel, a circumferential channel, and at least one coupling channel. An axial slot bottom of the stator housing is used to integrate an end-face channel, and a circumferential slot wall of the stator housing is used to integrate a circumferential channel. The end-face channel includes an end-face heat dissipation section, which guides coolant to flow through an axial slot bottom in at least one counterclockwise or clockwise direction. The circumferential channel includes a circumferential heat dissipation section, which guides coolant to flow through a circumferential slot wall in at least one counterclockwise or clockwise direction. The circumferential heat dissipation section and the end-face heat dissipation section are connected by a coupling channel.

[0006] In this embodiment, an axial groove bottom of the stator housing provides the possibility for integrating an end-face cooling channel for cooling the end face of the stator core. A circumferential groove wall of the stator housing provides the possibility for integrating a circumferential cooling channel for cooling the outer circumferential surface of the stator core. The stator housing integrates an end-face channel and a circumferential channel, resulting in a compact structure. This allows coolant to cool both the end face and outer circumferential surface of the stator core, effectively increasing the heat dissipation area of ​​the coolant on the stator core, improving the cooling efficiency of the disc motor, and helping to alleviate the overheating problem of the disc motor.

[0007] In this embodiment, an end-face flow channel includes an end-face heat dissipation section. The end-face heat dissipation section is used to guide the coolant to flow through an axial groove bottom in at least one of the counterclockwise or clockwise directions. This helps to extend the residence time and flow path of the coolant at the bottom of an axial groove, increase the heat dissipation area of ​​the coolant on the stator core, and thus improve the cooling efficiency of the end-face heat dissipation section on the end face of the stator core, thereby improving the cooling efficiency of the disc motor and ensuring the normal operation of the disc motor.

[0008] In this embodiment, a circumferential flow channel includes a circumferential heat dissipation section. The circumferential heat dissipation section is used to guide the coolant to flow through a circumferential groove wall in at least one of the counterclockwise or clockwise directions. This helps to prolong the residence time of the coolant on a circumferential groove wall and also helps to increase the heat dissipation area of ​​the coolant on the stator core. This improves the cooling efficiency of the circumferential heat dissipation section on the outer circumferential surface of the stator core, thereby improving the cooling efficiency of the disc motor, alleviating the overheating problem of the disc motor, and ensuring the normal operation of the disc motor.

[0009] In this embodiment, a peripheral heat dissipation section and an end heat dissipation section are connected by a coupling flow channel, allowing coolant to flow between the peripheral heat dissipation section and the end heat dissipation section. The peripheral flow channel and the end flow channel can flow in parallel or in series within the stator housing.

[0010] In one embodiment, a circumferential heat dissipation section guides the coolant to flow through a circumferential groove wall in at least one of a counterclockwise or clockwise direction, and the circumferential heat dissipation section is also used to guide the coolant to flow through a circumferential groove wall along the axial direction of the disc motor.

[0011] In this embodiment, a circumferential heat dissipation section guides the coolant to flow along the circumferential and axial directions of the disc motor through a circumferential groove wall, increasing the heat dissipation area between the circumferential heat dissipation section and the outer circumferential surface of the stator core, and also extending the flow length of the circumferential heat dissipation section in a circumferential groove wall. This is beneficial to improving the heat dissipation efficiency of the outer circumferential surface of the stator core, thereby improving the cooling efficiency of the disc motor. It also achieves cooling and temperature reduction of the disc motor along the axial and circumferential directions, exhibiting good heat dissipation performance and low flow resistance, which is beneficial to reducing energy consumption loss.

[0012] In one embodiment, along the axial direction of the disc motor, the length of a circumferential slot wall is less than or equal to the length of the stator core. The length of a circumferential heat dissipation section is greater than the circumference of a circumferential slot wall. Along the radial direction of the disc motor, the width of a circumferential heat dissipation section is less than the thickness of a circumferential slot wall.

[0013] In this embodiment, the length of a circumferential groove wall is less than or equal to the length of the stator core, so that the stator housing can only accommodate the stator core, and the coolant in the stator housing is only used to cool the stator core that generates more heat, thereby improving the cooling efficiency of the coolant on the disc motor and improving the power density and efficiency of the disc motor.

[0014] In this embodiment, the length of a circumferential heat dissipation segment is greater than the circumference of a circumferential slot wall, allowing the circumferential heat dissipation segment to circle the circumferential slot wall at least once along the circumference of the disc motor. Alternatively, the path of the circumferential heat dissipation segment is "S"-shaped and has a longer path, resulting in a longer flow length for the circumferential heat dissipation segment within the circumferential slot wall. This increases the heat dissipation area on the outer circumferential surface of the stator core, improving the cooling efficiency of the stator core and the disc motor. Furthermore, it facilitates the flow of coolant along the axial direction of the disc motor through the circumferential slot wall, both in a counter-clockwise and clockwise direction. For example, the shape of the circumferential heat dissipation segment arranged within the circumferential slot wall can be spiral, annular, toothed, or "S"-shaped.

[0015] In the embodiments of this application, the width of a circumferential heat dissipation section along the radial direction of the disc motor is less than the thickness of a circumferential groove wall. This is beneficial for integrating a circumferential heat dissipation section into a circumferential groove wall, improving the integration of the cooling channel of the disc motor with the stator housing, saving material of a circumferential groove wall, reducing costs, and ensuring the structural strength of the circumferential groove wall.

[0016] In this embodiment, the cooling effect of the cooling channel on the stator core is improved by the length of a circumferential slot wall along the axial direction of the disc motor being less than or equal to the length of the stator core, the length of a circumferential heat dissipation section being greater than the circumference of a circumferential slot wall, and the width of a circumferential heat dissipation section along the radial direction of the disc motor being less than the thickness of a circumferential slot wall.

[0017] In one embodiment, one end-face flow channel further includes another end-face heat dissipation section, which is connected to a circumferential heat dissipation section via another coupling flow channel. The one end-face heat dissipation section and the other end-face heat dissipation section are respectively used to guide the coolant to flow in the same direction through different parts of the bottom of an axial tank. The circumferential heat dissipation section is used to guide the coolant output from one end-face heat dissipation section and the coolant output from the other end-face heat dissipation section to flow in opposite directions through different parts of the circumferential tank wall.

[0018] In this embodiment, one end-face flow channel further includes another end-face heat dissipation section. The other end-face heat dissipation section is connected to a peripheral heat dissipation section through another coupling flow channel, allowing coolant to circulate between the other end-face heat dissipation section and the peripheral heat dissipation section. The inclusion of one end-face heat dissipation section and another end-face heat dissipation section in one end-face flow channel increases the heat dissipation area of ​​the end-face flow channel on the stator core end face, thereby improving the cooling efficiency of the disc motor.

[0019] In this embodiment, one end-face heat dissipation section and the other end-face heat dissipation section are respectively used to guide the coolant to flow in the same direction through different parts of an axial groove bottom. This facilitates the parallel cooling of the disc motor by the coolant in one end-face heat dissipation section and the other end-face heat dissipation section, reducing the flow resistance of the coolant and reducing losses. The inlets of one end-face heat dissipation section and the other end-face heat dissipation section are located on the same side along the circumference, so that one end-face heat dissipation section and the other end-face heat dissipation section are used to guide the coolant to flow in the same direction.

[0020] In this embodiment, a peripheral heat dissipation section guides the coolant output from one end-face heat dissipation section and the coolant output from the other end-face heat dissipation section to flow in opposite directions through different parts of a circumferential groove wall. This allows the heated coolant in one end-face heat dissipation section and the other end-face heat dissipation section to flow out of the cooling channel of the disc motor through a peripheral heat dissipation section. It also facilitates the parallel connection of the coolant output from one end-face heat dissipation section and the other end-face heat dissipation section, allowing them to flow through different parts of the circumferential groove wall and cool different parts of the stator core's outer peripheral surface. This shortens the path for the coolant to flow out of the disc motor from one end-face heat dissipation section and the other end-face heat dissipation section, allowing the low-temperature coolant in the external channel to enter the disc motor more quickly, thus improving the cooling efficiency of the disc motor. Compared to the two end-face heat dissipation sections, which each need to flow through all parts of a circumferential groove wall, a circumferential heat dissipation section guides the coolant output from one end-face heat dissipation section and the coolant output from the other end-face heat dissipation section to flow in opposite directions through different parts of a circumferential groove wall. This also helps to reduce the flow resistance of the coolant and reduce losses.

[0021] In one embodiment, the stator housing further includes a bearing sleeve for fixing the outer ring of a bearing and the inner ring of a bearing for fixing the motor shaft of the disc motor. The bearing sleeve includes a bearing flow channel. The bearing flow channel connects to another end-face heat dissipation section, and the bearing flow channel and the other end-face heat dissipation section respectively guide coolant to flow in different directions through a bearing sleeve and an axial groove bottom.

[0022] In this embodiment, a bearing helps reduce friction between the stator housing and the motor shaft, resulting in smoother rotation of the motor shaft and reduced energy loss. A bearing channel circulates coolant to cool the inner portion of the stator core, allowing the end faces, outer peripheral surfaces, and inner portions of the stator core to be cooled by the coolant, improving the cooling efficiency of the stator core and the disc motor, and mitigating overheating issues. The bearing channel also circulates coolant to cool the outer ring of a bearing, further enhancing the cooling efficiency of the disc motor.

[0023] In this embodiment, a bearing channel connects to another end-face heat dissipation section, allowing coolant to circulate between the other end-face heat dissipation section and the bearing channel. This improves the integration of the cooling channel within the stator housing. The bearing channel and the other end-face heat dissipation section guide the coolant to flow in different directions through a bearing sleeve and an axial groove bottom, respectively. This allows both the bearing channel and the other end-face heat dissipation section to simultaneously cool the inner diameter and end face of the stator core, improving the cooling efficiency of the disc motor.

[0024] In one embodiment, a circumferential groove wall includes a plurality of circumferential grooves, which together form a circumferential heat dissipation section. At least one circumferential groove is connected to an end-face heat dissipation section via a coupling flow channel. Along the circumferential direction of the disc motor, the length of each circumferential groove is less than the circumference of a circumferential groove wall. Along the axial direction of the disc motor, the length of each circumferential groove is less than the length of a circumferential groove wall.

[0025] In this embodiment, at least one circumferential groove is used to connect an end-face heat dissipation section through a coupling flow channel, so that the coolant in the end-face heat dissipation section and the coolant in the circumferential heat dissipation section can flow together, which is beneficial for the circumferential heat dissipation section to guide the coolant output from the end-face heat dissipation section to flow through a portion of the circumferential groove of the circumferential groove wall.

[0026] In this embodiment, along the circumference of the disc motor, the length of each circumferential groove is less than the circumference of a circumferential groove wall, so that a circumferential groove wall has space to arrange multiple circumferential grooves. This helps to reduce the processing difficulty of the circumferential grooves of a circumferential groove wall. The spacing of a large number of circumferential grooves makes a circumferential groove wall have more solid structural parts, which helps to ensure the structural reliability of a circumferential groove wall and improve the overall performance of the disc motor.

[0027] In this embodiment, along the axial direction of the disc motor, the length of each circumferential groove is less than the length of a circumferential groove wall, providing space for a circumferential groove wall to arrange multiple circumferential grooves along the axial direction of the disc motor. The smaller length of each circumferential groove results in a smaller cross-sectional area of ​​each circumferential groove along the axial direction of the disc motor, which is beneficial to accelerate the flow speed of coolant along the circumferential direction in a circumferential heat dissipation section and improve the cooling efficiency of the disc motor.

[0028] In one embodiment, the plurality of circumferential grooves include two sets of circumferential grooves, one set of circumferential grooves and the other set of circumferential grooves are arranged along the axial direction of the disc motor. Along the circumferential direction of the disc motor, the plurality of circumferential grooves in each set are arranged at intervals, and the interval between two adjacent circumferential grooves in each set is less than the length of any one of the two circumferential grooves.

[0029] In this embodiment, a set of circumferential grooves and another set of circumferential grooves are arranged along the axial direction of the disc motor, so that the coolant in the circumferential heat dissipation section formed by the set of circumferential grooves and the other set of circumferential grooves can flow along the axial and circumferential directions of the disc motor through a circumferential groove wall, thereby improving the heat dissipation efficiency of the stator core. It also helps to increase the heat dissipation area of ​​the outer circumferential surface of the stator core by the circumferential heat dissipation section, thereby improving the heat dissipation efficiency of the stator core and thus improving the cooling efficiency of the disc motor.

[0030] In the embodiments of this application, along the circumference of the disc motor, multiple circumferential grooves of each group of circumferential grooves are arranged at intervals, so that a circumferential groove wall has multiple solid structural portions of adjacent two circumferential grooves of each group of circumferential grooves along the circumference of the disc motor, which is beneficial to improving the structural strength of the stator housing and thus improving the reliability of the disc motor.

[0031] In this embodiment, along the circumference of the disc motor, the interval between two adjacent circumferential grooves in each group of circumferential grooves is less than the length of any one of the two circumferential grooves. This is beneficial to increasing the length of the circumferential flow channel formed by the two groups of circumferential grooves along the circumferential direction of the disc motor, increasing the heat dissipation area of ​​the coolant on the outer circumferential surface of the stator core in a circumferential heat dissipation section, and improving the heat dissipation effect of a circumferential heat dissipation section on the outer circumferential surface of the stator core, thereby improving the cooling efficiency of the disc motor.

[0032] In one embodiment, along the axial direction of the disc motor, a portion of one circumferential groove in one set of circumferential grooves and a portion of another circumferential groove in another set of circumferential grooves are arranged adjacent to each other, and the portion of one circumferential groove and the portion of another circumferential groove are connected along the axial direction of the disc motor.

[0033] In this embodiment, a portion of one circumferential groove in one set of circumferential grooves and a portion of another circumferential groove in another set of circumferential grooves are arranged adjacent to each other. These two portions are connected along the axial direction of the disc motor, allowing the coolant in both grooves to flow in a continuous manner. This extends the flow path of a circumferential heat dissipation section within a circumferential groove wall, increases the heat dissipation area of ​​the coolant on the outer circumferential surface of the stator core, improves the cooling effect of the circumferential heat dissipation section on the outer circumferential surface of the stator core, enhances the cooling efficiency of the disc motor, and alleviates the overheating problem of the disc motor.

[0034] In one embodiment, at least one of the portions of a circumferential groove or another circumferential groove has a circumferential length greater than the axial length of at least one of the circumferential grooves or another circumferential groove.

[0035] In the embodiments of this application, at least one of the portions of a circumferential groove or another portion of a circumferential groove has a circumferential length greater than the axial length of at least one of the circumferential grooves or another portion of a circumferential groove. This is beneficial for reducing the flow resistance of coolant from one circumferential groove to another, and for the coolant in one circumferential heat dissipation section to smoothly change its flow direction along the circumferential and axial directions of the circumferential groove wall, thereby cooling the outer circumferential surface of the stator core and improving the cooling efficiency of the circumferential motor.

[0036] In one embodiment, an axial groove bottom includes at least one end face groove, which forms an end face heat dissipation section. Each end face groove is located around the center of the axial groove bottom in one of a clockwise or counterclockwise direction, and one or more of the at least one end face groove are used to connect to a circumferential heat dissipation section via a coupling flow channel.

[0037] In this embodiment of the application, an axial groove bottom includes at least one end face groove, which is used to form an end face heat dissipation section, so that coolant can flow in an axial groove bottom to cool the end face of the stator core.

[0038] In this embodiment, each end face groove surrounds the center of the axial groove bottom in either a clockwise or counterclockwise direction. This allows the coolant in the end face heat dissipation section formed by each end face groove to flow through the axial groove bottom in either a clockwise or counterclockwise direction. This provides more arrangement space for each end face groove in the axial groove bottom, increases the heat dissipation area of ​​the end face heat dissipation section on the stator core end face, improves the heat dissipation efficiency of the disc motor, and promotes uniform heat dissipation from the stator core end face, thus enhancing the cooling effect.

[0039] In the embodiments of this application, one or more end face grooves in at least one end face groove are used to connect a peripheral heat dissipation section through a coupling flow channel, so that one end face heat dissipation section in at least one end face groove can be connected to a peripheral heat dissipation section through a coupling flow channel, thereby facilitating the flow of coolant output from one end face heat dissipation section through a portion of the peripheral groove of a circumferential groove wall, further improving the cooling efficiency of the coolant for the disc motor.

[0040] In one embodiment, at least one end face groove includes a first end face groove and a second end face groove. The distance between the first end face groove and the center of the disc motor is greater than the distance between the second end face groove and the center of the disc motor along the radial direction of the disc motor. The first end face groove and the second end face groove are respectively connected to a circumferential heat dissipation section through different coupling flow channels, and the flow direction of the coolant in the first end face groove and the second end face groove is the same.

[0041] In this embodiment of the application, a first end face groove and a second end face groove are used to form one end face heat dissipation section and the other end face heat dissipation section, respectively.

[0042] In this embodiment, along the radial direction of the disc motor, the distance between a first end face groove and the center of the disc motor is greater than the distance between a second end face groove and the center of the disc motor. This allows one end face heat dissipation section formed by a first end face groove and another end face heat dissipation section formed by a second end face groove to simultaneously cool the inner and outer ring portions of the stator core end face, respectively. This is beneficial for improving the heat dissipation efficiency of the stator core and the cooling efficiency of the disc motor. It also helps to ensure that the first end face groove and the second end face groove are arranged neatly at the bottom of an axial groove.

[0043] In this embodiment, a first end face groove and a second end face groove are connected to a circumferential heat dissipation section through different coupling flow channels. This facilitates the flow of coolant from one end face heat dissipation section and the other end face heat dissipation section through a circumferential groove wall. The flow direction of the coolant in the first end face groove and the second end face groove is the same, which further facilitates the flow of coolant from one end face heat dissipation section and the other end face heat dissipation section through different parts of a circumferential groove wall in the same direction. Cooling different parts of the stator core's outer circumference shortens the path of the coolant flowing out of the disc motor from one end face heat dissipation section and the other end face heat dissipation section, allowing the low-temperature coolant in the external flow channel to enter the disc motor more quickly, thus improving the cooling efficiency of the disc motor.

[0044] In this embodiment of the application, the inlets of a first end face groove and a second end face groove are located on the same side along the circumference, so that the flow direction of the coolant in the two grooves is the same.

[0045] In one embodiment, at least one end face groove further includes a third end face groove and a radial groove. The radial groove connects a first end face groove and a third end face groove, and the third end face groove connects a second end face groove. Along the radial direction of the disc motor, the distance between the third end face groove and the center of the disc motor is less than the distance between the second end face groove and the center of the disc motor. Along the axial direction of the disc motor, the groove depth of the third end face groove is greater than the groove depth of the first end face groove and the groove depth of the second end face groove.

[0046] In this embodiment, a third end face groove forms a bearing flow channel, and a radial groove connects a first end face groove and a third end face groove. This allows coolant flowing through the radial groove to flow to both the first and third end face grooves, enabling parallel flow between a heat dissipation section in the first end face groove and a bearing flow channel in the third end face groove. This reduces flow resistance in the cooling channel, lowers losses, and improves the cooling efficiency of the disc motor. A third end face groove connects to a second end face groove, allowing series flow between a bearing flow channel in the third end face groove and another heat dissipation section in the second end face groove. This allows parallel flow between the heat dissipation sections in the disc motor, further reducing flow resistance, accelerating coolant flow in the disc motor, and improving cooling efficiency.

[0047] In this embodiment, along the radial direction of the disc motor, the distance between a third end face groove and the center of the disc motor is less than the distance between a second end face groove and the center of the disc motor. This allows a bearing flow channel formed by a third end face groove and another end face heat dissipation section formed by a second end face groove to simultaneously cool the inner diameter portion and end face of the stator core, respectively. This is beneficial for improving the heat dissipation efficiency of the stator core and the cooling efficiency of the disc motor. It also makes it easier for the third end face groove and the second end face groove to be arranged neatly at the bottom of an axial groove.

[0048] In this embodiment, along the axial direction of the disc motor, the groove depth of a third end face is greater than the groove depth of a first end face groove and a second end face groove. The smaller groove depths of the first and second end face grooves allow for a smaller axial thickness of the groove bottom at both the first and second end face grooves, saving material and reducing the space occupied by the disc motor along its axial direction. The third end face groove, located within a bearing sleeve, forms a bearing flow channel. The larger groove depth of the third end face provides a larger heat dissipation area for the inner diameter portion of the stator core along the disc motor's axial direction, improving the cooling efficiency of the bearing flow channel on the stator core, thus enhancing the cooling efficiency of the disc motor and mitigating overheating issues.

[0049] In one embodiment, at least one of the axial slot bottoms or the circumferential slot walls of the stator housing includes an inner shell and an outer shell. The inner shell and the outer shell of the axial slot bottom are arranged adjacent to each other along the axial direction of the disc motor, with multiple axial gaps between the inner shell and the outer shell. These multiple axial gaps form an end-face flow channel, and at least one axial gap forms an end-face portion of a coupling flow channel. The width of each axial gap along the radial direction of the disc motor is greater than its depth along the axial direction of the disc motor. Similarly, the inner shell and the outer shell of the circumferential slot wall are arranged adjacent to each other along the radial direction of the disc motor, with multiple radial gaps between the inner shell and the outer shell. These multiple radial gaps form a circumferential flow channel, and at least one radial gap forms a circumferential portion of a coupling flow channel. Two adjacent radial gaps along the circumferential direction of the disc motor are spaced apart, while two adjacent radial gaps along the axial direction of the disc motor are connected.

[0050] In the embodiments of this application, at least one of the axial groove bottom or the circumferential groove wall is composed of an inner shell and an outer shell, which makes the formation of the flow channel in at least one of the axial groove bottom or the circumferential groove wall simpler and more convenient, and the shape of the flow channel can be designed more flexibly to meet different cooling and heat dissipation requirements.

[0051] In one embodiment, an inner shell and an outer shell of a circumferential groove wall are arranged radially adjacent to each other in the disc motor, and there are multiple radial gaps between the inner shell and the outer shell. The multiple radial gaps are used to form a circumferential flow channel, and at least one radial gap is used to form a circumferential portion of a coupling flow channel. Two radial gaps adjacent in the circumferential direction of the disc motor are spaced apart, and two radial gaps adjacent in the axial direction of the disc motor are connected.

[0052] In this embodiment, an inner shell and an outer shell of a circumferential groove wall are arranged radially adjacent to each other in the disc motor. Multiple radial gaps exist between the inner shell and the outer shell, providing the possibility of forming a circumferential flow channel between them for coolant flow. These multiple radial gaps form a circumferential flow channel, enabling coolant to flow circumferentially along the disc motor to cool the outer circumferential surface of the stator core. This improves the cooling efficiency of the disc motor and alleviates overheating issues. At least one radial gap forms the circumferential portion of a coupled flow channel, allowing coolant to flow between the circumferential flow channel and the end-face flow channel.

[0053] In this embodiment, two adjacent radial gaps along the circumferential direction of the disc motor are spaced apart, and there are multiple intervals between the multiple radial gaps. The intervals are solid structures, which helps to improve the structural strength of a circumferential slot wall, thereby improving the structural stability of the disc motor. Two adjacent radial gaps along the axial direction of the disc motor are connected, allowing coolant to flow between the two adjacent radial gaps. This facilitates the formation of a circumferential flow channel along the axial direction of the disc motor, cooling the outer circumferential surface of the stator core.

[0054] In one embodiment, an inner shell and an outer shell of an axial groove are arranged adjacent to each other along the axial direction of the disc motor, and there are multiple axial gaps between the inner shell and the outer shell. The multiple axial gaps are used to form an end face flow channel, and at least one axial gap is used to form an end face portion of a coupling flow channel. The width of each axial gap along the radial direction of the disc motor is greater than its depth along the axial direction of the disc motor.

[0055] In this embodiment, an inner shell and an outer shell with an axial groove bottom are arranged adjacent to each other along the axial direction of the disc motor. Multiple axial gaps exist between the inner shell and the outer shell, providing the possibility of forming an end-face flow channel between them for coolant flow. These multiple axial gaps form an end-face flow channel, allowing coolant to flow circumferentially along the disc motor to cool the end face of the stator core, thus improving the cooling efficiency of the disc motor and mitigating overheating issues. At least one axial gap forms the end-face portion of a coupled flow channel, allowing coolant to flow between the circumferential flow channel and the end-face flow channel.

[0056] In this embodiment, the radial width of each axial gap along the disc motor is greater than its axial depth. The larger radial width of each axial gap increases the heat dissipation area of ​​the end-face flow channel relative to the stator core end face, thus improving cooling of the disc motor. The smaller axial depth of each axial gap allows for a thinner bottom thickness along the axial direction of the disc motor, facilitating miniaturization of the disc motor.

[0057] Secondly, embodiments of this application provide a powertrain including a transmission device and a disc motor as described above. The disc motor is used to receive drive from an engine via a transmission device, or to drive wheels via a transmission device. The disc motor in the powertrain improves cooling efficiency by integrating cooling channels within the stator housing, thereby enhancing the performance of the powertrain.

[0058] Thirdly, embodiments of this application provide an electric vehicle, which includes a frame, a power battery, and a powertrain as described above. The frame is used to fix the power battery and the powertrain. The disc motor is used for driving using electrical energy provided by the power battery, or for charging the power battery using electrical energy provided by the disc motor. In the powertrain of this application, the disc motor integrates an end-face flow channel and a circumferential flow channel in one axial slot bottom and one circumferential slot wall, respectively. All cooling channels are integrated into the stator housing, resulting in a compact structure. This also allows for cooling of the end face and outer circumferential surface of the stator core, improving the cooling efficiency of the disc motor. The coolant can flow through at least one axial slot bottom and one circumferential slot wall in either a counter-clockwise or clockwise direction, increasing the heat dissipation area of ​​the coolant on the stator core, thus improving the cooling efficiency of the disc motor, mitigating overheating issues, enhancing the overall performance of the disc motor, and consequently improving the performance of the entire vehicle. Attached Figure Description

[0059] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the embodiments of this application will be described below.

[0060] Figure 1 is a structural schematic diagram of an electric vehicle provided in an embodiment of this application;

[0061] Figure 2 is a schematic diagram of the powertrain provided in an embodiment of this application;

[0062] Figure 3 is a schematic diagram of the structure of a disc motor provided in an embodiment of this application;

[0063] Figure 4 is an exploded view of a disc motor provided in an embodiment of this application;

[0064] Figure 5 is a cross-sectional view of the disc motor in Figure 3 along AA;

[0065] Figure 6 is a schematic diagram of the structure of a stator housing provided in an embodiment of this application;

[0066] Figure 7 is a schematic diagram of another structure of the stator housing provided in an embodiment of this application;

[0067] Figure 8 is a cross-sectional view of the stator housing along CC in Figure 6;

[0068] Figure 9 is a schematic diagram of a stator housing cooling channel provided in an embodiment of this application;

[0069] Figure 10 is a magnified view of part M1 in Figure 5;

[0070] Figure 11 is a magnified view of part M2 in Figure 8;

[0071] Figure 12 is a schematic diagram of the structure of a disc motor provided in another embodiment of this application;

[0072] Figure 13 is an exploded view of a disc motor provided in another embodiment of this application;

[0073] Figure 14 is a cross-sectional view of the disc motor in Figure 12 along BB;

[0074] Figure 15 is a schematic diagram of a stator housing cooling channel provided in another embodiment of this application. Detailed Implementation

[0075] The technical solutions of the embodiments of this application will be described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments.

[0076] For ease of understanding, the English abbreviations and related technical terms used in the embodiments of this application will be explained and described below.

[0077] Perpendicularity: The perpendicularity defined in the embodiments of this application is not limited to an absolute perpendicular intersection (with an included angle of 90 degrees). It is permissible for non-absolute perpendicular intersections caused by factors such as assembly tolerances, design tolerances, and structural flatness. It is permissible for errors within a small angular range, such as an assembly error range of 80 to 100 degrees, which can all be understood as a perpendicular relationship.

[0078] To cool the stator core, improve the cooling efficiency of the disc motor, and solve the overheating problem, this application provides a disc motor with an integrated cooling channel in the stator housing. The disc motor includes a stator core and a slotted stator housing. The stator housing is used to fix the stator core and to integrate the cooling channel for the stator core. The cooling channel includes an end face channel, a circumferential channel, and at least one coupling channel. An axial slot bottom of the stator housing is used to integrate an end face channel, and a circumferential slot wall of the stator housing is used to integrate a circumferential channel. The end face channel includes an end face heat dissipation section, which guides the coolant to flow through the axial slot bottom in at least one counterclockwise or clockwise direction. The circumferential channel includes a circumferential heat dissipation section, which guides the coolant to flow through the circumferential slot wall in at least one counterclockwise or clockwise direction. The circumferential heat dissipation section and the end face heat dissipation section are connected by a coupling channel. This application integrates an end-face flow channel and a circumferential flow channel into an axial slot bottom and a circumferential slot wall, respectively. All cooling channels are integrated into the stator housing, resulting in a compact structure. This also allows for cooling of the end faces and outer circumferential surfaces of the stator core, improving the cooling efficiency of the disc motor. The coolant can flow through at least one axial slot bottom and one circumferential slot wall in either a counter-clockwise or clockwise direction, increasing the heat dissipation area of ​​the coolant on the stator core. This further improves the cooling efficiency of the disc motor, alleviates overheating problems, and enhances the overall performance of the disc motor.

[0079] The disc motor provided in this application embodiment is applied to the powertrain, which is then applied to an electric vehicle to improve the overall performance of the electric vehicle.

[0080] Please refer to Figure 1, which is a schematic diagram of the structure of an electric vehicle 1 provided in an embodiment of this application. In this embodiment, the electric vehicle 1 includes a frame 20, a powertrain 10, and a power battery 30. The powertrain 10 and the power battery 30 are fixed to the frame 20. The power battery 30 is used to receive power from the powertrain 10.

[0081] In this embodiment of the application, the frame 20 can also be referred to as the vehicle body.

[0082] In this embodiment of the application, electric vehicle 1 refers to a wheeled device that is driven or towed by a power unit.

[0083] Please refer to Figures 1 and 2. Figure 2 is a schematic diagram of the structure of a powertrain 10 provided in an embodiment of this application. In one embodiment, the powertrain 10 includes a disc motor 100 and a transmission device (not shown). The motor shaft of the disc motor 100 is used for transmission connection with the transmission device or transmission connection with an engine (not shown). The powertrain 10 can be used for at least one of generating electricity and driving.

[0084] In one embodiment, the transmission device is a reducer 200, which includes a gear assembly, an input shaft, and an output shaft (not shown). The disc motor 100 includes a motor shaft, a motor stator, and a motor rotor (not shown). The input shaft of the reducer 200 receives power transmitted from the motor shaft of the disc motor 100 and transmits the power to the output shaft through the gear assembly. The gear assembly can be configured as needed and can be a single-speed, two-speed, or multi-speed reduction gear assembly. The motor rotor is fixedly sleeved on the motor shaft, and the motor stator is fixed to the housing of the disc motor 100. The motor rotor and motor stator are axially arranged, and there is an air gap between the motor rotor and the motor stator. The motor stator includes a stator core and a coil winding. The coil winding is fixed to the stator core 110. When the coil winding is energized, it interacts with the motor rotor, driving the motor rotor to rotate. When the motor rotor rotates, it can drive the motor shaft to rotate, and the disc motor 100 outputs power through the motor shaft.

[0085] In one embodiment, the powertrain 10 further includes a motor controller 300, which is electrically connected to the power battery 30. The motor controller 300 converts the direct current (DC) power transmitted from the power battery 30 into alternating current (AC) power and transmits it to the disc motor 100. The disc motor 100 receives the AC power, converts the electrical energy into mechanical energy, and transmits the mechanical energy to the reducer 200. The reducer 200 is connected to the wheel 40 and transmits power to the wheel 40 to drive the wheel 40 to rotate.

[0086] In one embodiment, the transmission device is an speed booster (not shown), and the output shaft of the engine is connected to the input shaft of the speed booster. The mechanical energy output by the engine is increased by the speed booster and then transmitted to the motor shaft of the disc motor 100, which drives the motor rotor of the disc motor 100 to rotate and generate electricity, thereby charging the power battery 30.

[0087] In one embodiment, the transmission device is an engine crankshaft, which is directly connected to the motor shaft of the disc motor 100. The engine directly transmits kinetic energy to the disc motor 100, converting the kinetic energy into electrical energy to charge the power battery.

[0088] The following will describe in detail the disc motor 100 with integrated cooling channels in the stator housing 120 provided in the embodiments of this application.

[0089] Please refer to Figures 3, 4, 5, 6, 7, 8, and 9. Figure 3 is a schematic diagram of the structure of a disc motor 100 provided in one embodiment of this application. Figure 4 is an exploded view of the disc motor 100 provided in one embodiment of this application. Figure 5 is a cross-sectional view of the disc motor 100 in Figure 3 along AA. Figure 6 is a schematic diagram of the structure of a stator housing 120 provided in one embodiment of this application. Figure 7 is another schematic diagram of the structure of a stator housing 120 provided in one embodiment of this application. Figure 8 is a cross-sectional view of the stator housing 120 in Figure 6 along CC. Figure 9 is a schematic diagram of the structure of the cooling channel of the stator housing 120 provided in one embodiment of this application.

[0090] In one embodiment, a disc motor 100 with an integrated cooling channel in a stator housing 120 includes a stator core 110 and a slotted stator housing 120, as shown in Figures 3 and 4. The stator housing 120 is used to fix the stator core 110 and the cooling channel for cooling the stator core 110.

[0091] As shown in Figure 4, in this embodiment, the stator core 110 has a fixed winding 193. The winding 193 is used to receive AC power output from the motor controller 300 to drive the motor shaft 194 and rotor 192 of the disc motor 100 to rotate. The slotted stator housing 120 is used to accommodate the stator core 110 and the winding 193. Both the stator core 110 and the winding 193 are impregnated and cured, and are fixedly connected to the stator housing 120 and integrally potted to form a single unit. In this embodiment, the stator housing 120 can be a one-piece molded structure (as shown in Figure 4) or a split structure (as shown in Figure 13).

[0092] In one embodiment, the disc motor 100 further includes a rotor housing 170, as shown in Figures 3 and 4. The rotor housing 170 is used to fix the stator housing 120 along the axial direction O of the disc motor. The space enclosed by the rotor housing 170 and the stator housing 120 is used to accommodate the stator core 110 and the motor rotor 192. In this embodiment, the stator housing 120 has cooling channels, while the rotor housing 170 does not have cooling channels.

[0093] In one embodiment, the rotor housing 170 is cooled by air.

[0094] In one embodiment, the rotor housing 170 integrates a rotor housing flow channel (not shown) whereby coolant cools the air surrounding the rotor 192, thereby cooling the disc motor 100. This rotor housing flow channel is not connected to the cooling flow channel within the stator housing 120, allowing for relatively independent cooling of the stator core 110 and the rotor 192.

[0095] In this embodiment of the application, the rotor housing 170 is used to accommodate the motor rotor 192 of the disc motor 100. The rotor housing 170 is fixed to the stator housing 120 along the axial direction O of the disc motor. The space enclosed by the rotor housing 170 and the stator housing 120 is used to accommodate the stator core 110 and the motor rotor 192.

[0096] In one embodiment, the cooling channel includes an end face channel 131, a circumferential channel 141, and at least one coupling channel 121, as shown in Figures 7 and 9. An axial groove bottom 130 of the stator housing 120 is used to integrate an end face channel 131, and a circumferential groove wall 140 of the stator housing 120 is used to integrate a circumferential channel 141. The end face channel 131 includes an end face heat dissipation section 132, which guides the coolant to flow through the axial groove bottom 130 in at least one of a counterclockwise N direction or a clockwise S direction. The circumferential channel 141 includes a circumferential heat dissipation section 142, which guides the coolant to flow through the circumferential groove wall 140 in at least one of a counterclockwise N direction or a clockwise S direction. The circumferential heat dissipation section 142 and the end face heat dissipation section 132 are connected by a coupling channel 122.

[0097] In this embodiment, an axial groove bottom 130 of the stator housing 120 provides the possibility for integrating an end face channel 131 of the cooling channel, which is used to cool the end face of the stator core 110. A circumferential groove wall 140 of the stator housing 120 provides the possibility for integrating a circumferential channel 141 of the cooling channel, which is used to cool the outer circumferential surface of the stator core 110. The stator housing 120 integrates an end face channel 131 and a circumferential channel 141, and all cooling channels are integrated into the stator housing 120, resulting in a compact structure. This allows coolant to be applied to both the end face and the outer circumferential surface of the stator core 110, effectively increasing the heat dissipation area of ​​the coolant on the stator core 110, improving the cooling efficiency of the disc motor 100, and helping to alleviate the overheating problem of the disc motor 100.

[0098] In this embodiment of the application, an end face flow channel 131 includes an end face heat dissipation section 132. The end face heat dissipation section 132 is used to guide the coolant to flow through an axial groove bottom 130 in at least one of the counterclockwise N direction or the clockwise S direction. This helps to prolong the residence time of the coolant in an axial groove bottom 130, increase the heat dissipation area of ​​the coolant on the stator core 110, and thus improve the cooling efficiency of the end face heat dissipation section 132 on the end face of the stator core 110, thereby improving the cooling efficiency of the disc motor 100 and ensuring the normal operation of the disc motor 100.

[0099] In one embodiment, the direction of coolant flow through an axial groove bottom 130, whether clockwise (S) or counterclockwise (N), is related to the flow channel arrangement of an end-face heat dissipation section 132 of the axial groove bottom 130. When the flow channel of an end-face heat dissipation section 132 in an axial groove bottom 130 first deflects counterclockwise (N) in a direction perpendicular to the axial axis O of the disc motor, the end-face heat dissipation section 132 guides the coolant to flow through the axial groove bottom 130 in a counterclockwise (N) direction. When the flow channel of an end-face heat dissipation section 132 in an axial groove bottom 130 first deflects clockwise (S) in a direction perpendicular to the axial axis O of the disc motor, the end-face heat dissipation section 132 guides the coolant to flow through the axial groove bottom 130 in a clockwise (S) direction. When an end face flow channel 131 in an axial groove bottom 130 includes both a flow channel deflected clockwise by S in a direction perpendicular to the axial direction O of the disc motor and a flow channel deflected counterclockwise by N in a direction perpendicular to the axial direction O of the disc motor, an end face heat dissipation section 132 is used to guide the coolant to flow through an axial groove bottom 130 in both the counterclockwise N direction and the clockwise S direction.

[0100] In this embodiment, a circumferential flow channel 141 includes a circumferential heat dissipation section 142. The circumferential heat dissipation section 142 is used to guide the coolant to flow through a circumferential groove wall 140 in at least one of the counterclockwise N direction or the clockwise S direction. This helps to prolong the residence time of the coolant in a circumferential groove wall 140, increase the heat dissipation area of ​​the coolant on the stator core 110, and thus improve the cooling efficiency of the circumferential heat dissipation section 142 on the outer circumferential surface of the stator core 110. This improves the cooling efficiency of the disc motor 100, alleviates the overheating problem of the disc motor 100, and ensures the normal operation of the disc motor 100.

[0101] In one embodiment, the direction of coolant flow through a circumferential groove wall 140, whether clockwise (S) or counterclockwise (N), is related to the flow channel arrangement of a circumferential heat dissipation section 142 of the circumferential groove wall 140. When the flow channel of a circumferential heat dissipation section 142 in a circumferential groove wall 140 first deflects counterclockwise (N) along the circumferential direction (C) of the disc motor, the circumferential heat dissipation section 142 guides the coolant to flow through the circumferential groove wall 140 in the counterclockwise (N) direction. When the flow channel of a circumferential heat dissipation section 142 in a circumferential groove wall 140 first deflects clockwise (S) along the circumferential direction (C) of the disc motor, the circumferential heat dissipation section 142 guides the coolant to flow through the circumferential groove wall 140 in the clockwise (S) direction. When a circumferential heat dissipation section 142 includes both a flow channel deflected clockwise (S) along the circumferential C direction of the disc motor and a flow channel deflected counterclockwise (N) along the circumferential C direction of the disc motor, the circumferential heat dissipation section 142 is used to guide the coolant to flow through the circumferential groove wall 140 in both the counterclockwise (N) and clockwise (S) directions.

[0102] In this application, a peripheral heat dissipation section 142 and an end heat dissipation section 132 are connected by a coupling flow channel 122, allowing coolant in the peripheral heat dissipation section 142 and coolant in the end heat dissipation section 132 to flow. The peripheral flow channel 141 and the end flow channel 131 can flow in parallel or in series within the stator housing 120.

[0103] In one embodiment, an end-face flow channel 131 includes a connected end-face coupling section 135 and an end-face heat dissipation section 132, and a peripheral flow channel 141 includes a connected peripheral coupling section 143 and a peripheral heat dissipation section 142, wherein the peripheral coupling section 143 is used to connect to the end-face coupling section 135. One of the coupling flow channels 122 includes at least one of an end-face coupling section 135 and a peripheral coupling section 143.

[0104] As shown in Figures 7 and 9, in this embodiment, an end-face flow channel 131 includes an end-face coupling section 135 and an end-face heat dissipation section 132 that are connected to each other. Both the end-face coupling section 135 and the end-face heat dissipation section 132 can cool the end face of the stator core 110. The end-face coupling section 135 can connect the end-face heat dissipation section 132 and a peripheral flow channel 141, allowing the coolant in the end-face flow channel 131 and the coolant in the peripheral flow channel 141 to flow together.

[0105] As shown in Figures 7 and 9, in this embodiment, a peripheral flow channel 141 includes a peripheral coupling section 143 and a peripheral heat dissipation section 142 that are connected to each other. Both the peripheral coupling section 143 and the peripheral heat dissipation section 142 can cool the outer peripheral surface of the stator core 110. The peripheral coupling section 143 is used to connect an end coupling section 135. The peripheral coupling section 143 can connect a peripheral heat dissipation section 142 and an end coupling section 135 of the end flow channel 131, so that the coolant in the peripheral flow channel 141 and the coolant in the end flow channel 131 can flow together, improving the integration of the cooling channels in the stator housing 120.

[0106] In one embodiment, a circumferential heat dissipation section 142 guides the coolant to flow through a circumferential groove wall 140 in at least one of the counterclockwise N direction or the clockwise S direction. The circumferential heat dissipation section 142 is also used to guide the coolant to flow through a circumferential groove wall 140 along the axial direction O of the disc motor 100.

[0107] As shown in Figures 6, 7, and 9, in this embodiment of the application, a circumferential heat dissipation section 142 guides the coolant to flow along the circumferential C and axial O of the disc motor 100 through a circumferential groove wall 140. This increases the heat dissipation area of ​​the circumferential heat dissipation section 142 and the outer circumferential surface of the stator core 110, and also extends the flow length of the circumferential heat dissipation section 142 in a circumferential groove wall 140. This is beneficial to improving the heat dissipation efficiency of the outer circumferential surface of the stator core 110, thereby improving the cooling efficiency of the disc motor 100. It also achieves cooling and temperature reduction of the disc motor 100 along the axial O and circumferential C, exhibiting good heat dissipation performance and low flow resistance, which is beneficial to reducing energy consumption loss.

[0108] Please refer to Figures 5 and 10. Figure 10 is a partial enlarged view of part M1 in Figure 5. In one embodiment, along the axial direction O of the disc motor 100, the length of a circumferential slot wall 140 is greater than or equal to the length of the stator core 110.

[0109] As shown in Figure 10, in this embodiment, the axial length of a circumferential slot wall 140 is denoted as L1, and the axial length of the stator core 110 is denoted as L2. A larger L1 allows for a larger arrangement space for a circumferential flow channel 141 in the circumferential slot wall 140. It also allows the coolant in the circumferential flow channel 141 to have a larger heat dissipation area on the outer circumferential surface of the stator core 110 along the axial O and circumferential C directions of the disc motor, thus cooling the entire outer circumferential surface of the stator core 110. This facilitates faster cooling of the stator core 110 and improves the cooling efficiency of the disc motor 100. Since L1 ≥ L2, the stator housing 120 can also be used to accommodate the motor rotor 192, allowing the circumferential flow channel 141 in the circumferential slot wall 140 to flow over the outer circumferential surface of the motor rotor 192 of the disc motor 100, partially cooling the motor rotor 192 as well. This further improves the cooling efficiency of the disc motor 100 and alleviates the overheating problem of the disc motor 100.

[0110] In one embodiment, along the axial direction O of the disc motor 100, the length of a circumferential slot wall 140 is less than or equal to the length of the stator core 110. This ensures that the stator housing 120 can only accommodate the stator core 110, and that the coolant within the stator housing 120 is used only to cool the stator core 110, which generates significant heat. This improves the cooling efficiency of the coolant on the disc motor 100, thereby increasing the power density and efficiency of the disc motor 100.

[0111] In one embodiment, the length of a circumferential heat dissipation segment 142 is greater than the circumference of a circumferential slot wall 140. As shown in FIG9, in this embodiment of the application, the length of a circumferential heat dissipation segment 142 is greater than the circumference of a circumferential slot wall 140, such that the circumferential heat dissipation segment 142 circles a circumferential slot wall 140 at least once along the circumferential direction C of the disc motor, or the path of the circumferential heat dissipation segment 142 is "S"-shaped and has a long path, so that the arrangement of the circumferential heat dissipation segment 142 in a circumferential slot wall 140 has a long flow length, which is beneficial to increase the heat dissipation area of ​​the outer circumferential surface of the stator core 110 by the circumferential heat dissipation segment 142, and improve the cooling efficiency of the stator core 110 and the disc motor 100. Furthermore, as the circumferential heat dissipation section 142 guides the coolant to flow through the circumferential groove wall 140 in at least one of the counterclockwise N direction or clockwise S direction, the circumferential heat dissipation section 142 can also guide the coolant to flow along the axial direction O of the disc motor 100 through the circumferential groove wall 140. For example, the shape of the circumferential heat dissipation section 142 arranged on the circumferential groove wall 140 can be spiral, annular, toothed, or "S"-shaped (as shown in Figure 9).

[0112] In one embodiment, the width of a circumferential heat dissipation section 142 along the radial direction R of the disc motor is less than the thickness of a circumferential slot wall 140. As shown in FIG10, in this embodiment of the application, the width of a circumferential heat dissipation section 142 along the radial direction R of the disc motor is denoted as L3, and the thickness of a circumferential slot wall 140 along the radial direction R of the disc motor is denoted as L4, where L3 < L4. This facilitates the integration of a circumferential heat dissipation section 142 into a circumferential slot wall 140, improves the integration of the cooling channel of the disc motor 100 with the stator housing 120, saves material of the circumferential slot wall 140, reduces costs, and ensures the structural strength of the circumferential slot wall 140.

[0113] In one embodiment, one end-face flow channel 131 further includes another end-face heat dissipation section 133, which is connected to a circumferential heat dissipation section 142 via another coupling flow channel 123. The one end-face heat dissipation section 132 and the other end-face heat dissipation section 133 are respectively used to guide the coolant to flow in opposite directions through different parts of an axial groove bottom 130.

[0114] In this embodiment, one end-face flow channel 131 further includes another end-face heat dissipation section 133. The other end-face heat dissipation section 133 is connected to a peripheral heat dissipation section 142 through another coupling flow channel 123, allowing the coolant in the other end-face heat dissipation section 133 and the peripheral heat dissipation section 142 to circulate. The end-face flow channel 131, including one end-face heat dissipation section 132 and another end-face heat dissipation section 133, is beneficial for increasing the heat dissipation area of ​​the end-face flow channel 131 on the end face of the stator core 110, thereby improving the cooling efficiency of the disc motor 100.

[0115] In this embodiment, one end-face heat dissipation section 132 and the other end-face heat dissipation section 133 are respectively used to guide the coolant to flow in opposite directions through different parts of an axial groove bottom 130. This allows one end-face heat dissipation section 132 and the other end-face heat dissipation section 133 to simultaneously cool different parts of the end face of the stator core 110, thereby improving the cooling efficiency of the disc motor 100. It also allows one circumferential heat dissipation section 142 to guide the coolant output from one end-face heat dissipation section 132 and the coolant output from the other end-face heat dissipation section 133 to flow in opposite directions through different parts of a circumferential groove wall 140.

[0116] In one embodiment, one end-face heat dissipation section 132 and the other end-face heat dissipation section 133 are respectively used to guide the coolant to flow in the same direction through different parts of an axial groove bottom 130. As shown in FIG9, in this embodiment of the application, it is beneficial for the coolant in one end-face heat dissipation section 132 and the other end-face heat dissipation section 133 to cool the disc motor 100 in parallel, thereby reducing the flow resistance of the coolant and reducing losses. In the embodiment shown in FIG9, the inlets of one end-face heat dissipation section 132 and the other end-face heat dissipation section 133 are located on the same side along the circumferential direction C, so that one end-face heat dissipation section 132 and the other end-face heat dissipation section 133 are used to guide the coolant to flow in the same direction.

[0117] In one embodiment, a circumferential heat dissipation section 142 is used to guide the coolant output from one end heat dissipation section 132 and the coolant output from another end heat dissipation section 133 to flow in opposite directions through different parts of a circumferential groove wall 140.

[0118] As shown in Figures 7 and 9, in this embodiment, a peripheral heat dissipation section 142 guides the coolant output from one end heat dissipation section 132 and the coolant output from another end heat dissipation section 133 to flow in opposite directions through different parts of a circumferential groove wall 140. This allows the heated coolant in one end heat dissipation section 132 and the other end heat dissipation section 133 to flow out of the cooling channel of the disc motor 100 through the peripheral heat dissipation section 142. It also facilitates the cooling of different parts of the stator core 110 by the parallel connection of the coolant output from one end heat dissipation section 132 and the other end heat dissipation section 133, thereby shortening the path of the coolant flowing out of the disc motor 100. This allows the low-temperature coolant in the external channel to enter the disc motor 100 more quickly, improving the cooling efficiency of the disc motor 100. Compared to the fact that one end-face heat dissipation section 132 and the other end-face heat dissipation section 133 need to flow through all parts of a circumferential groove wall 140 respectively, the circumferential heat dissipation section 142 guides the coolant output from one end-face heat dissipation section 132 and the coolant output from the other end-face heat dissipation section 133 to flow in opposite directions through different parts of a circumferential groove wall 140, which also helps to reduce the flow resistance of the coolant and reduce losses.

[0119] In one embodiment, the stator housing 120 further includes a bearing sleeve 150, as shown in Figures 4 and 5. The bearing sleeve 150 is used to fix the outer ring of a bearing 190, and the inner ring of the bearing 190 is used to fix the motor shaft 194 of the connected disc motor 100. The bearing sleeve 150 includes a bearing flow channel 151. As shown in Figures 6 and 7, the bearing flow channel 151 is used to connect to another end face heat dissipation section 133. The bearing flow channel 151 and the other end face heat dissipation section 133 are respectively used to guide the coolant to flow through a bearing sleeve 150 and an axial groove bottom 130 in different directions.

[0120] In this embodiment, a bearing 190 helps reduce friction between the stator housing 120 and the motor shaft 194, resulting in smoother rotation of the motor shaft 194 and reduced energy loss. A bearing flow channel 151 is used for circulating coolant to cool the inner portion of the stator core 110, thereby allowing the end face, outer peripheral surface, and inner portion of the stator core 110 to be cooled by the coolant, improving the cooling efficiency of the stator core 110 and the disc motor 100, and alleviating the overheating problem of the disc motor 100. A bearing flow channel 151 is also used for circulating coolant to cool the outer ring of a bearing 190, which helps improve the cooling efficiency of the disc motor 100.

[0121] In this embodiment, a bearing channel 151 connects to another end-face heat dissipation section 133, allowing coolant to circulate between the other end-face heat dissipation section 133 and the bearing channel 151. This improves the integration of the cooling channel within the stator housing 120. The bearing channel 151 and the other end-face heat dissipation section 133 guide the coolant in different directions through a bearing sleeve 150 and an axial groove bottom 130, respectively. This allows both the bearing channel 151 and the other end-face heat dissipation section 133 to simultaneously cool the inner diameter portion and end face of the stator core 110, improving the cooling efficiency of the disc motor 100. In the embodiment shown in Figure 7, a bearing channel 151 guides the coolant counterclockwise through a bearing sleeve 150, and the other end-face heat dissipation section 133 guides the coolant clockwise through an axial groove bottom 130.

[0122] In one embodiment, a circumferential groove wall 140 includes a plurality of circumferential grooves 141a, as shown in Figures 6, 7, and 9. The plurality of circumferential grooves 141a are used to form a circumferential heat dissipation section 142, and at least one circumferential groove 141a is used to connect to an end-face heat dissipation section 132 through a coupling flow channel 121. As shown in Figure 9, along the circumferential direction C of the disc motor 100, the length of each circumferential groove 141a is less than the circumference of a circumferential groove wall 140. Along the axial direction O of the disc motor 100, the length of each circumferential groove 141a is less than the length of a circumferential groove wall 140.

[0123] It should be noted that Figure 9 is a schematic diagram of the coolant flow path. In order to clearly illustrate the structure of the stator housing, the labels shown in Figure 9 indicate the structure corresponding to the location of each section of coolant. For the actual structure, please refer to Figures 6, 7 and 8.

[0124] As shown in Figure 9, in this embodiment of the application, at least one peripheral groove 141a is used to connect an end face heat dissipation section 132 through a coupling flow channel 121, so that the coolant in the end face heat dissipation section 132 and the coolant in the peripheral groove 142 can flow together, which is beneficial for the peripheral groove 141a of the peripheral groove 142 to guide the coolant output from the end face heat dissipation section 132 through a portion of the peripheral groove 141a of the circumferential groove wall 140.

[0125] In this embodiment, along the circumferential direction C of the disc motor 100, the length of each circumferential groove 141a is less than the circumference of a circumferential groove wall 140, so that a circumferential groove wall 140 has space to arrange multiple circumferential grooves 141a. This helps to reduce the processing difficulty of the circumferential grooves 141a of a circumferential groove wall 140. The spaced arrangement of a large number of circumferential grooves 141a makes a circumferential groove wall 140 have more solid structural parts, which helps to ensure the structural reliability of a circumferential groove wall 140 and improve the overall performance of the disc motor 100.

[0126] As shown in Figure 10, in this embodiment of the application, the length of each circumferential groove 141a along the axial direction O of the disc motor 100 is denoted as L5, and the length of a circumferential groove wall 140 is L1, where L5 < L1. This provides space for arranging multiple circumferential grooves 141a along the axial direction O of the disc motor 100 using a circumferential groove wall 140. The smaller L5 results in a smaller cross-sectional area of ​​each circumferential groove 141a along the axial direction O of the disc motor, which is beneficial for accelerating the flow speed of coolant along the circumferential direction in a circumferential heat dissipation section 142 and improving the cooling efficiency of the disc motor 100.

[0127] In one embodiment, the opening of each circumferential groove 141a is used to seal with a first seal 102a, as shown in FIG4. At least one circumferential groove 141a and a first seal 102a corresponding to its opening together form a circumferential heat dissipation section 142. The length of each circumferential groove 141a along the circumferential direction C of the disc motor is greater than its length along the axial direction O of the disc motor.

[0128] In this embodiment, the opening of each circumferential groove 141a is used to seal with a first sealing element 102a, which can be achieved by friction stir welding. The opening of each circumferential groove 141a is formed when a circumferential groove wall 140 is machined to form the circumferential groove 141a. The first sealing element 102a is used to seal the opening of each circumferential groove 141a, thereby preventing the coolant flowing through each circumferential groove 141a from leaking into other components of the disc motor 100 and causing malfunction of the disc motor 100. At least one circumferential groove 141a and its corresponding first sealing element 102a together form a circumferential heat dissipation section 142, thereby providing the possibility for coolant to flow in a counterclockwise N direction or clockwise S direction in a circumferential heat dissipation section 142 to cool the outer circumferential surface of the stator core 110, which is beneficial for cooling the disc motor 100, improving the overheating problem of the disc motor 100, and ensuring the normal operation of the disc motor 100.

[0129] In this embodiment of the application, as shown in FIG9, the length of each circumferential groove 141a along the circumferential direction C of the disc motor is denoted as L6, and the length of each circumferential groove 141a along the axial direction O of the disc motor is denoted as L5. The larger L6 and the smaller L5 make it possible to open multiple circumferential grooves 141a along the axial direction O of the disc motor in one circumferential groove wall 140. In addition, L6 > L5, which is beneficial to guide the coolant to flow through one circumferential heat dissipation section 142 in a counterclockwise N direction or a clockwise S direction. If L5 is larger, the possibility of turbulence in each circumferential groove 141a when the coolant flows along the circumferential direction C will increase due to the larger length along the axial direction O of the disc motor, which will increase the flow resistance and thus hinder the smooth flow of the coolant in one circumferential heat dissipation section 142, reduce the cooling efficiency of the coolant on the outer circumferential surface of the stator core 110, and affect the heat dissipation effect of the disc motor 100.

[0130] In one embodiment, the plurality of circumferential grooves 141a include two sets of circumferential grooves 142a and 143a, as shown in FIG9. One set of circumferential grooves 142a and the other set of circumferential grooves 143a are arranged along the axial direction O of the disc motor 100, respectively. Along the circumferential direction C of the disc motor 100, the plurality of circumferential grooves 141a in each set of circumferential grooves 142a and 143a are arranged at intervals, and the interval between two adjacent circumferential grooves 141a in each set of circumferential grooves 142a and 143a is less than the length of any one of the two circumferential grooves 141a.

[0131] In this embodiment, a set of circumferential grooves 142a and another set of circumferential grooves 143a are arranged along the axial direction O of the disc motor 100, so that the coolant in the circumferential heat dissipation section 142 formed by the set of circumferential grooves 142a and the other set of circumferential grooves 143a can flow along the axial direction O and circumferential direction C of the disc motor through a circumferential groove wall 140, thereby improving the heat dissipation efficiency of the stator core 110. It also helps to increase the heat dissipation area of ​​the circumferential heat dissipation section 142 on the outer circumferential surface of the stator core 110, thereby improving the heat dissipation efficiency of the stator core 110 and improving the cooling efficiency of the disc motor 100.

[0132] In this embodiment of the application, along the circumferential direction C of the disc motor 100, multiple circumferential grooves 141a of each group of circumferential grooves 142a, 143a are arranged at intervals, so that a circumferential groove wall 140 has multiple solid structural portions of adjacent two circumferential grooves 141a of each group of circumferential grooves 142a, 143a along the circumferential direction C of the disc motor, which is beneficial to improving the structural strength of the stator housing 120 and thus improving the reliability of the disc motor 100.

[0133] In this embodiment, along the circumferential direction C of the disc motor 100, the interval between two adjacent circumferential grooves 141a in each group of circumferential grooves 142a and 143a is denoted as L8, and the length of any one of the two circumferential grooves 141a is L6, where L8 < L6. This is beneficial to increasing the length of the circumferential flow channel 141 formed by the two groups of circumferential grooves 142a and 143a along the circumferential direction C of the disc motor, increasing the heat dissipation area of ​​the coolant in the circumferential heat dissipation section 142 on the outer circumferential surface of the stator core 110, and improving the heat dissipation effect of the circumferential heat dissipation section 142 on the outer circumferential surface of the stator core 110, thereby improving the cooling efficiency of the disc motor 100.

[0134] In one embodiment, along the axial direction O of the disc motor 100, a portion 142c of one circumferential groove 142b in a set of circumferential grooves 142a and a portion 143c of another circumferential groove 143b in another set of circumferential grooves 143a are arranged adjacent to each other, as shown in FIG9. The portion 142c of one circumferential groove 142b and the portion 143c of another circumferential groove 143b are connected along the axial direction O of the disc motor 100.

[0135] As shown in Figure 9, in this embodiment of the application, a portion 142c of one circumferential groove 142b in one set of circumferential grooves 142a and a portion 143c of another circumferential groove 143b in another set of circumferential grooves 143a are arranged adjacent to each other. The portion 142c of one circumferential groove 142b in one set of circumferential grooves 142a and the portion 143c of another circumferential groove 143b in another set of circumferential grooves 143a are connected along the axial direction O of the disc motor 100, thereby enabling one circumferential groove 142b in one set of circumferential grooves 142a and the other circumferential groove 143b in another set of circumferential grooves 143a to communicate. The coolant in one of the peripheral grooves 143a and the other of the peripheral grooves 143b can flow in a continuous manner, thereby allowing the coolant in one set of peripheral grooves 142a and the other set of peripheral grooves 143a to flow in a continuous manner. This helps to extend the flow path of one peripheral heat dissipation section 142 in a circumferential groove wall 140, increase the heat dissipation area of ​​the coolant on the outer peripheral surface of the stator core 110, improve the cooling effect of one peripheral heat dissipation section 142 on the outer peripheral surface of the stator core 110, improve the cooling efficiency of the disc motor 100, and alleviate the overheating problem of the disc motor 100.

[0136] In one embodiment, the groove orientation of one set of circumferential grooves 142a along the axial direction of the disc motor is opposite to the groove orientation of another set of circumferential grooves 143a.

[0137] As shown in Figures 7 and 9, in this embodiment of the application, the groove opening orientation of one set of circumferential grooves 142a along the axial direction O of the disc motor is opposite to that of another set of circumferential grooves 143a. This is beneficial for machining one set of circumferential grooves 142a and another set of circumferential grooves 143a at both ends of a circumferential groove wall 140 along the axial direction O of the disc motor, which helps to make the overall structural strength of a circumferential groove wall 140 greater and ensure the reliability of the disc motor 100.

[0138] In one embodiment, at least one of a portion 142c of a circumferential groove 142b or a portion 143c of another circumferential groove 143b has a length along the circumferential direction C of the disc motor 100 that is greater than the length along the axial direction O of at least one of the circumferential grooves 142b or the other circumferential groove 143b.

[0139] As shown in Figure 9, in this embodiment of the application, the length of at least one of the portions 142c of one circumferential groove 142b or the portion 143c of another circumferential groove 143b along the circumferential C of the disc motor 100 is denoted as L9, and the length of at least one of the portions 142b or the other circumferential groove 143b along the axial O of the disc motor 100 is denoted as L10. L9 > L10, which helps to reduce the flow resistance of coolant flowing from one circumferential groove 142b into another circumferential groove 143b. It also helps the coolant in one circumferential heat dissipation section 142 to smoothly change its flow direction along the circumferential C and axial O of the disc motor and flow through a circumferential groove wall 140 to cool the outer circumferential surface of the stator core 110 and improve the cooling efficiency of the disc motor 100.

[0140] In one embodiment, a circumferential groove wall 140 further includes a plurality of axial through holes 144, as shown in FIG9. One axial through hole 144 connects a portion 142c of a circumferential groove 142b and a portion 143c of another circumferential groove 143b. Specifically, along the axial direction O of the disc motor, one axial through hole 144 penetrates both a portion 142c of the circumferential groove 142b and a portion 143c of the other circumferential groove 143b. In the embodiment shown in FIG9, the axial through hole 144 is only shown in the diagram; it may not be present in the embodiment shown in FIG9. In other embodiments, a circumferential groove wall 140 further includes the axial through hole 144 as described above. In one embodiment, an axial through hole 144 is provided between a circumferential groove 142b and another circumferential groove 143b.

[0141] In this embodiment, a plurality of axial through holes 144 in a circumferential groove wall 140 provide the possibility of connecting a circumferential groove 142b and another circumferential groove 143b with opposite groove orientations, connecting a set of circumferential grooves 142a and another set of circumferential grooves 143a on a circumferential groove wall 140 into a whole, which is beneficial to the smooth flow of coolant in a circumferential groove wall 140.

[0142] In this embodiment, an axial through hole 144 along the axial direction O of the disc motor penetrates a portion 142c of a circumferential groove 142b and a portion 143c of another circumferential groove 143b, thereby allowing coolant to flow through two adjacent circumferential grooves 142b and 143b. This facilitates the staggered flow of coolant in the circumferential grooves 141a of one set of circumferential grooves 142a and 141a of another set of circumferential grooves 143a. This allows the coolant to flow not only along the circumferential direction C of the disc motor but also along the axial direction O of the disc motor within a circumferential groove wall 140, extending the flow path of the coolant within the circumferential groove wall 140 and increasing the heat dissipation area on the outer circumferential surface of the stator core 110. This improves the cooling efficiency of the circumferential heat dissipation section 142 on the outer circumferential surface of the stator core 110, thus mitigating the overheating problem of the disc motor 100.

[0143] In one embodiment, an axial groove bottom 130 includes at least one end face groove 131a, as shown in Figures 7 and 9. The at least one end face groove 131a is used to form an end face heat dissipation section 132. Each end face groove 131a is arranged around the center of the axial groove bottom 130 along one of the clockwise S direction or the counterclockwise N direction. One or more end face grooves 131a are used to connect to a circumferential heat dissipation section 142 through a coupling flow channel 122.

[0144] In this embodiment of the application, an axial groove bottom 130 includes at least one end face groove 131a, which is used to form an end face heat dissipation section 132, so that coolant can flow in an axial groove bottom 130 to cool the end face of the stator core 110.

[0145] In this embodiment, each end face groove 131a surrounds the center of the axial groove bottom 130 along one of the clockwise S direction or the counterclockwise N direction, so that the coolant in the end face heat dissipation section 132 formed by each end face groove 131a can flow through the axial groove bottom 130 along one of the clockwise S direction or the counterclockwise N direction. This is beneficial for each end face groove 131a to have more arrangement space in the axial groove bottom 130, which is beneficial for increasing the heat dissipation area of ​​the end face heat dissipation section 132 on the end face of the stator core 110, which is beneficial for improving the heat dissipation efficiency of the disc motor 100, and also beneficial for uniform heat dissipation on the end face of the stator core 110, thus improving the cooling effect.

[0146] In this embodiment of the application, one or more end face grooves 131a in at least one end face groove 131a are used to connect a peripheral heat dissipation section 142 through a coupling flow channel 122, so that one end face heat dissipation section 132 in at least one end face groove 131a can be connected to a peripheral heat dissipation section 142 through a coupling flow channel 122, thereby facilitating the flow of coolant output from one end face heat dissipation section 132 through a portion of the peripheral groove 141a of a circumferential groove wall 140 by a peripheral heat dissipation section 142, and further improving the cooling efficiency of the coolant on the disc motor 100.

[0147] In one embodiment, at least one end face groove 131a includes a first end face groove 132a and a second end face groove 133a. As shown in FIG7, along the radial direction R of the disc motor 100, the distance between the first end face groove 132a and the center of the disc motor 100 is greater than the distance between the second end face groove 133a and the center of the disc motor 100. The first end face groove 132a and the second end face groove 133a are respectively connected to a circumferential heat dissipation section 142 through different coupling flow channels 121, and the flow direction of the coolant in the first end face groove 132a and the second end face groove 133a is the same.

[0148] In this embodiment of the application, a first end face groove 132a and a second end face groove 133a are respectively used to form an end face heat dissipation section 132 and another end face heat dissipation section 133.

[0149] In this embodiment, along the radial direction R of the disc motor 100, the distance between a first end face groove 132a and the center of the disc motor 100 is denoted as L11, and the distance between a second end face groove 133a and the center of the disc motor 100 is denoted as L12, where L11 > L12. This allows one end face heat dissipation section 132 formed by the first end face groove 132a and another end face heat dissipation section 133 formed by the second end face groove 133a to simultaneously cool the inner and outer ring portions of the stator core 110 end face, which is beneficial to improving the heat dissipation efficiency of the stator core 110 and the cooling efficiency of the disc motor 100. It also helps to ensure that the first end face groove 132a and the second end face groove 133a are arranged neatly in an axial groove bottom 130.

[0150] In this embodiment, a first end face groove 132a and a second end face groove 133a are respectively connected to a circumferential heat dissipation section 142 through different coupling flow channels 121. This facilitates the circumferential heat dissipation section 142 guiding the coolant output from one end face heat dissipation section 132 and the coolant output from the other end face heat dissipation section 133 through a circumferential groove wall 140. The flow direction of the coolant in the first end face groove 132a and the second end face groove 133a is the same, which facilitates the circumferential heat dissipation section 142 guiding the coolant output from one end face heat dissipation section 132 and the coolant output from the other end face heat dissipation section 133 to flow in the same direction through different parts of a circumferential groove wall 140. Cooling different parts of the outer periphery of the stator core 110 shortens the path of the heat dissipation section 132 on one end face and the heat dissipation section 133 on the other end face out of the disc motor 100, which is conducive to the low temperature coolant in the external flow channel entering the disc motor 100 more quickly and improving the cooling efficiency of the disc motor 100.

[0151] As shown in Figure 7, in this embodiment of the application, the inlets of a first end face groove 132a and a second end face groove 133a are located on the same side along the circumference, so that the flow direction of the coolant in the two grooves is the same.

[0152] In one embodiment, the flow direction of coolant in a first end face groove 132a is opposite to that in a second end face groove 133a.

[0153] In one embodiment, the opening of a first end face groove 132a is used to seal with a second seal 102b, as shown in FIG8. The first end face groove 132a and its corresponding second seal 102b form an end face heat dissipation section 132. The opening of a second end face groove 133a is used to seal with a third seal 102c. The second end face groove 133a and its corresponding third seal 102c form another end face heat dissipation section 133.

[0154] In this embodiment, the slot of a first end face groove 132a and the slot of a second end face groove 133a are formed by machining a first end face groove 132a and a second end face groove 133a from an axial groove bottom 130. The slot of a first end face groove 132a is used to seal with a second seal 102b, and the slot of a second end face groove 133a is used to seal with a third seal 102c. This prevents the coolant flowing through the first end face groove 132a and the second end face groove 133a from leaking into other components of the disc motor 100, thus preventing malfunction of the disc motor 100. A first end face groove 132a is used to form an end face heat dissipation section 132 with a corresponding second seal 102b, and a second end face groove 133a is used to form another end face heat dissipation section 133 with a corresponding third seal 102c. This allows the coolant to flow in the counterclockwise N direction or clockwise S direction in one end face heat dissipation section 132 and the other end face heat dissipation section 133 to cool the end face of the stator core 110, which is beneficial for cooling the disc motor 100 and ensuring the normal operation of the disc motor 100.

[0155] Please refer to Figures 7, 8, and 11. Figure 11 is a partially enlarged view of part M2 in Figure 8. In one embodiment, at least one end face groove 131a further includes a third end face groove 134a and a radial groove 136a, as shown in Figure 7. The radial groove 136a connects a first end face groove 132a and a third end face groove 134a, and the third end face groove 134a connects a second end face groove 133a. Along the radial direction R of the disc motor 100, the distance between the third end face groove 134a and the center of the disc motor 100 is less than the distance between the second end face groove 133a and the center of the disc motor 100. Along the axial direction O of the disc motor 100, the groove depth of the third end face groove 134a is greater than the groove depth of the first end face groove 132a and the groove depth of the second end face groove 133a.

[0156] In this embodiment, a third end face groove 134a is used to form a bearing flow channel 151, and a radial groove 136a is used to connect a first end face groove 132a and a third end face groove 134a, so that the coolant flowing through the radial groove 136a can flow to the first end face groove 132a and the third end face groove 134a respectively. In other words, a heat dissipation section 132 in a first end face groove 132a and a bearing flow channel 151 in a third end face groove 134a can flow in parallel, which helps to reduce the flow resistance in the cooling channel, reduce losses, and improve the cooling efficiency of the disc motor 100. A third end face groove 134a is used to connect a second end face groove 133a, so that a bearing flow channel 151 in a third end face groove 134a and another end face heat dissipation section 133 in a second end face groove 133a can flow in series, thereby allowing one end face heat dissipation section 132 and the other end face heat dissipation section 133 to flow in parallel in the disc motor 100, which helps to reduce flow resistance, accelerate the flow speed of coolant in the disc motor 100, and improve the cooling efficiency of the disc motor 100.

[0157] In this embodiment, along the radial direction R of the disc motor 100, the distance between a third end face groove 134a and the center of the disc motor 100 is denoted as L13, and the distance between a second end face groove 133a and the center of the disc motor 100 is L12, where L13 < L12. This allows a bearing flow channel 151 formed by a third end face groove 134a and another end face heat dissipation section 133 formed by a second end face groove 133a to simultaneously cool the inner diameter portion and end face of the stator core 110, respectively. This is beneficial for improving the heat dissipation efficiency of the stator core 110 and the cooling efficiency of the disc motor 100. It also helps to ensure that the third end face groove 134a and the second end face groove 133a are arranged neatly in an axial groove bottom 130.

[0158] In this embodiment of the application, as shown in FIG11, along the axial direction O of the disc motor 100, the groove depth of a third end face groove 134a is denoted as L14, the groove depth of a first end face groove 132a is denoted as L15, and the groove depth of a second end face groove 133a is L7, where L14 > L15 and L14 > L7. The smaller L15 and L7 are beneficial to the fact that the thickness of the axial groove bottom 130 at the first end face groove 132a and the second end face groove 133a along the axial direction O can be smaller, which is beneficial to saving materials and also to reducing the space occupied by the disc motor 100 along the disc motor axial direction O. A third end face groove 134a is located inside a bearing sleeve 150, forming a bearing flow channel 151. The larger L14 facilitates a larger heat dissipation area of ​​the bearing flow channel 151 along the axial direction O of the disc motor to the inner diameter portion of the stator core 110, which helps to improve the cooling efficiency of the bearing flow channel 151 to the stator core 110, improve the cooling efficiency of the disc motor 100, and alleviate the overheating problem of the disc motor 100.

[0159] Referring to Figure 7, in one embodiment, the distance between a first end face groove 132a and a second end face groove 133a is greater than the groove width of at least one of the first end face groove 132a or the second end face groove 133a. This is beneficial for increasing the area of ​​the solid portion of an axial groove bottom 130, and for ensuring that the axial groove bottom 130 still has strong structural stability after the first end face groove 132a and the second end face groove 133a are formed.

[0160] Please refer to Figures 4, 6 and 8. In one embodiment, a groove of a third end face groove 134a is used to seal with a fourth seal 102d, and a third end face groove 134a is used to form a bearing flow channel 151 with its corresponding fourth seal.

[0161] In this embodiment, the opening of a third end face groove 134a is formed by machining a third end face groove 134a from an axial groove bottom 130. The opening of the third end face groove 134a is used to seal with a fourth seal 102d, so that the coolant flowing through the third end face groove 134a will not leak into other components of the disc motor 100, causing malfunction of the disc motor 100. The third end face groove 134a and its corresponding fourth seal 102d form a bearing flow channel 151, so that the coolant can flow in a counterclockwise N direction or a clockwise S direction in the bearing flow channel 151 to cool down the inner diameter of the stator core 110, which is beneficial to cooling down the disc motor 100 and ensuring the normal operation of the disc motor 100.

[0162] In one embodiment, the total length of at least one end-face groove 131a is greater than the circumference of the outer peripheral surface of the stator core 110. This results in a longer flow path of one end-face channel 131 at the bottom of an axial groove 130, which helps to increase the heat dissipation area of ​​the coolant in the end-face channel 131 on the end face of the stator core 110, improves the heat dissipation efficiency of the end-face channel 131 on the end face of the stator core 110, and facilitates cooling of the disc motor 100.

[0163] In one embodiment, one of the axial groove bottom 130 and the circumferential groove wall 140 is further used to integrate two interfaces 161 and 162 and a connecting channel 136. The two interfaces 161 and 162 are used to receive coolant and output coolant, respectively. One interface 161 is used to connect to a heat dissipation section of one of the axial groove bottom 130 and the circumferential groove wall 140. The connecting channel 136 is used to connect the other interface 162 to a heat dissipation section of the other of the axial groove bottom 130 and the circumferential groove wall 140.

[0164] As shown in Figures 4 and 9, in this embodiment, one of the axial groove bottom 130 and the circumferential groove wall 140 is also used to integrate two interfaces 161 and 162 and a connecting channel 136 for cooling channels. The two interfaces 161 and 162 are used to receive coolant and output coolant, respectively. The connecting channel 136 can input coolant into the disc motor 100 or output coolant from the disc motor 100. The two interfaces 161 and 162 can realize the input and output of coolant in the disc motor 100, thereby ensuring that the coolant in the disc motor 100 can be replaced in real time, keeping the coolant at a lower temperature and ensuring the cooling effect of the coolant on the disc motor 100.

[0165] In this embodiment, an axial groove bottom 130 includes an end face flow channel 131, a circumferential groove wall 140 includes a circumferential flow channel 141, and an interface 161 is used to connect a heat dissipation section of one of the axial groove bottom 130 and the circumferential groove wall 140, thereby connecting an external cooling flow channel with a heat dissipation section of one of the end face flow channel 131 and the circumferential flow channel 141 through the interface 161. A connecting flow channel 136 is used to connect another interface 162 and a heat dissipation section of the other of the axial groove bottom 130 and the circumferential groove wall 140, thereby connecting an external cooling flow channel with a heat dissipation section of the other of the end face flow channel 131 and the circumferential flow channel 141 through the other interface 162 and the connecting flow channel 136. In the embodiment shown in FIG4, an interface 161 is used to connect a circumferential heat dissipation section 142 of a circumferential groove wall 140, and a connecting flow channel 136 is used to connect another interface 162 and an end face heat dissipation section 132 of the axial groove bottom 130. Alternatively, in another implementation, an interface 161 connects to an end-face heat dissipation section 132 of an axial groove bottom 130, and a connecting channel 136 connects to another interface 162 and a circumferential heat dissipation section 142 of a circumferential groove wall 140. This facilitates the input and output of coolant in the disc motor 100, ensuring that the coolant in the disc motor 100 can be replaced with the coolant in the external cooling system in real time, keeping the coolant at a lower temperature and ensuring the cooling effect of the coolant on the disc motor 100.

[0166] As shown in Figures 4, 7, and 9, in one embodiment, coolant flows into a connecting channel 136 from another interface 162. Subsequently, coolant flows from a radial groove 136a of the axial groove bottom 130 into a bearing channel 151 of a bearing sleeve 150 and an end face heat dissipation section 132 of the axial groove bottom 130. Then, coolant in one bearing channel 151 flows into another end face heat dissipation section 133 of the axial groove bottom 130. Finally, coolant converges in a circumferential heat dissipation section 142 of a circumferential groove wall 140 and flows out of the disc motor 100 from an interface 161. The parallel and series cooling channels achieve cooling and temperature reduction of the disc motor 100 along the axial direction O, radial direction R, and circumferential direction C, resulting in good heat dissipation performance, low flow resistance, and reduced energy loss.

[0167] In one embodiment, a circumferential groove wall 140 of the stator housing 120 is a one-piece molded structure, as shown in FIG8. The circumferential groove wall 140 forms a circumferential flow channel 141 by forming a circumferential groove 141a inside it and sealing the groove opening of the circumferential groove 141a with the sealing member 102a. The one-piece molded structure of the circumferential groove wall 140 gives it good structural strength and a simple structure, requiring no additional structural components and simplifying the installation process.

[0168] In one embodiment, an axial groove bottom 130 and a circumferential groove wall 140 of the stator housing 120 are integrally formed, as shown in Figures 8 and 9. An end face groove 131a is formed on the surface of the axial groove bottom 130 opposite to the circumferential groove wall 140. The groove opening of the end face groove 131a is sealed with the sealing elements 102b and 102c to form an end face flow channel 131. The integrally formed structure of the axial groove bottom 130 and the circumferential groove wall 140 can improve the structural strength of the stator housing 120, making the structure of the stator housing 120 simple, eliminating the need for additional structural components, and simplifying the installation process.

[0169] Please refer to Figures 12, 13, 14, and 15. Figure 12 is a structural schematic diagram of a disc motor 100 provided in another embodiment of this application. Figure 13 is an exploded view of the disc motor 100 provided in another embodiment of this application. Figure 14 is a cross-sectional view of the disc motor 100 in Figure 12 along BB. Figure 15 is a schematic diagram of the cooling channel structure of the stator housing 120 provided in another embodiment of this application.

[0170] In one embodiment, at least one of the axial groove bottom 130 or the circumferential groove wall 140 of the stator housing 120 includes an inner shell 145 and an outer shell 146. In this embodiment, at least one of the axial groove bottom 130 or the circumferential groove wall 140 is composed of an inner shell 145 and an outer shell 146, which makes the formation of the flow channel in at least one of the axial groove bottom 130 or the circumferential groove wall 140 simpler and more convenient, and the shape of the flow channel can be designed more flexibly to meet different cooling and heat dissipation requirements.

[0171] As shown in Figures 13 and 14, in one embodiment, an inner shell 145 and an outer shell 146 of a circumferential groove wall 140 are arranged adjacent to each other along the radial direction R of the disc motor 100. There are multiple radial gaps 147 between the inner shell 145 and the outer shell 146 (as shown in Figure 14). The multiple radial gaps 147 are used to form a circumferential flow channel 141. At least one radial gap 147 is used to form a circumferential portion of a coupling flow channel 122. Two adjacent radial gaps 147 along the circumferential direction C of the disc motor 100 are spaced apart (as shown in Figure 13). Two adjacent radial gaps 147 along the axial direction O of the disc motor 100 are connected (as shown in Figure 13).

[0172] In this embodiment, an inner shell 145 and an outer shell 146 of a circumferential groove wall 140 are arranged adjacent to each other along the radial direction R of the disc motor 100. Multiple radial gaps 147 exist between the inner shell 145 and the outer shell 146, providing the possibility of forming a circumferential flow channel 141 between the inner shell 145 and the outer shell 146 for the flow of coolant. The multiple radial gaps 147 form a circumferential flow channel 141, enabling coolant to flow along the circumferential direction C of the disc motor to cool the outer circumferential surface of the stator core 110. This improves the cooling efficiency of the disc motor 100 and alleviates the overheating problem. At least one radial gap 147 forms a circumferential portion of a coupling flow channel 122, allowing coolant to flow between the circumferential flow channel 141 and the end face flow channel 131.

[0173] In this embodiment, two adjacent radial gaps 147 along the circumferential direction C of the disc motor 100 are spaced apart, and there are multiple intervals between the radial gaps 147. The intervals are solid structures, which helps to improve the structural strength of a circumferential groove wall 140, thereby improving the structural stability of the disc motor 100. Two adjacent radial gaps 147 along the axial direction O of the disc motor 100 are connected, allowing the coolant in the two adjacent radial gaps 147 to flow. This facilitates the formation of a circumferential flow channel 141 along the axial direction O of the disc motor 100, which cools the outer circumferential surface of the stator core 110.

[0174] In one embodiment, an inner shell (not shown) and an outer shell (not shown) of an axial groove bottom 130 are arranged adjacent to each other along the axial direction O of the disc motor 100. There are multiple axial gaps (not shown) between the inner shell and the outer shell. The multiple axial gaps are used to form an end face flow channel 131. At least one axial gap is used to form an end face portion of a coupling flow channel 121. The width of each axial gap along the radial direction R of the disc motor 100 is greater than its depth along the axial direction O of the disc motor 100.

[0175] In this embodiment, an inner shell and an outer shell of an axial groove bottom 130 are arranged adjacent to each other along the axial direction of the disc motor 100. Multiple axial gaps exist between the inner shell and the outer shell, providing the possibility of forming an end-face flow channel 131 between the inner shell and the outer shell for coolant flow. These multiple axial gaps form an end-face flow channel 131, enabling coolant to flow along the circumferential direction C of the disc motor to cool the end face of the stator core 110, thereby improving the cooling efficiency of the disc motor 100 and mitigating its overheating problem. At least one axial gap forms the end-face portion of a coupling flow channel 121, allowing coolant to flow between a circumferential flow channel 141 and an end-face flow channel 131.

[0176] In this embodiment, the width of each axial gap along the radial direction R of the disc motor 100 is greater than its depth along the axial direction O of the disc motor 100. The larger width of each axial gap along the radial direction R of the disc motor 100 is beneficial for increasing the heat dissipation area of ​​one end-face flow channel 131 along the radial direction R of the disc motor 100 to the end face of the stator core 110, thus facilitating cooling of the disc motor 100. The smaller depth of each axial gap along the axial direction O of the disc motor 100 is beneficial for the axial groove bottom 130 to have a smaller thickness along the axial direction O of the disc motor, thus facilitating the miniaturization of the disc motor 100.

[0177] In one embodiment, an axial groove bottom 130 and a circumferential groove wall 140 are separate structures, as shown in Figures 13 and 14. The rotor housing 170 and the outer shell 146 of the circumferential groove wall 140 are integral structures. The rotor housing 170 and the circumferential groove wall 140 form a groove-shaped structure. An axial groove bottom 130 is used to cover the groove opening of the groove-shaped structure. The bearing sleeve 150 and the axial groove bottom 130 are integrally formed structures.

[0178] In one embodiment, an axial groove bottom 130 and a circumferential groove wall 140 of the outer shell 146 are integrally structured, making the implementation of the stator housing 120 more flexible.

[0179] In one embodiment, an end-face flow channel 131 of an axial groove bottom 130 includes an end-face heat dissipation section 132 and another end-face heat dissipation section 133, as shown in FIG13. The end-face heat dissipation section 132 and the other end-face heat dissipation section 133 are arranged at intervals along the circumferential direction C of the disc motor 100. The coolant in the end-face heat dissipation section 132 and the other end-face heat dissipation section 133 flows in the same direction. The inlet of one end-face heat dissipation section 132 is connected to an interface 161 to receive coolant. The outlet of one end-face heat dissipation section 132 is connected to the inlet of a bearing flow channel 151 of the bearing sleeve 150. The outlet of one bearing flow channel 151 is connected to the inlet of the other end-face heat dissipation section 133. The outlet of the other end-face heat dissipation section 133 is connected to another interface 162. The end-face heat dissipation section 132, the bearing flow channel 151, and the other end-face heat dissipation section 133 are connected in series. The flow directions of the end-face heat dissipation section 132 and the bearing flow channel 151 are opposite.

[0180] In one embodiment, each of the end-face heat dissipation section 132 and the other end-face heat dissipation section 133 is "S"-shaped, increasing the path of the end-face heat dissipation section 132 and the other end-face heat dissipation section 133, so that the coolant can flow through a larger area of ​​the axial groove bottom 130, thereby improving the cooling effect on the stator core.

[0181] In one embodiment, one interface 161 is used to connect to an end face heat dissipation section 132 of an axial groove bottom 130, and another interface 162 is used to connect to a circumferential heat dissipation section 142 of a circumferential groove wall 140. As shown in Figures 13 and 15, coolant flows into the disc motor 100 from one interface 161, then into an end face heat dissipation section 132, flows into a bearing flow channel 151 of a bearing sleeve 150, flows out from the other end face heat dissipation section 133, and then flows into a circumferential heat dissipation section 142, flowing along the circumferential direction C of the disc motor, and then flows out of the disc motor 100 from the other interface 162. By using a series cooling flow channel structure, cooling and temperature reduction of the disc motor 100 along the axial direction O, radial direction R, and circumferential direction C are achieved, resulting in good heat dissipation performance.

[0182] The disc motor, powertrain, and electric vehicle provided in the embodiments of this application have been described in detail above. Specific examples have been used to illustrate the principles and embodiments of this application. The description of the embodiments above is only for the purpose of helping to understand the method and core ideas of this application. At the same time, for those skilled in the art, there will be changes in specific embodiments and application scope based on the ideas of this application. Therefore, the content of this specification should not be construed as a limitation of this application.

Claims

1. A disc motor, characterized in that, The disc motor includes a stator core and a slotted stator housing. The stator housing is used to fix the stator core and to integrate cooling channels for the stator core. The cooling channels include an end face channel, a circumferential channel, and at least one coupling channel. An axial slot bottom of the stator housing is used to integrate the end face channel, and a circumferential slot wall of the stator housing is used to integrate the circumferential channel, wherein: The end face flow channel includes an end face heat dissipation section, which is used to guide the coolant to flow through the bottom of the axial groove in at least one of the counterclockwise or clockwise directions. The circumferential flow channel includes a circumferential heat dissipation section, which is used to guide the coolant to flow through the circumferential groove wall in at least one of a counterclockwise or clockwise direction. The peripheral heat dissipation section and the end heat dissipation section are connected by a coupling flow channel.

2. The disc motor according to claim 1, characterized in that, During the process of guiding the coolant to flow through the circumferential groove wall in at least one of the counterclockwise or clockwise directions, the circumferential heat dissipation section is also used to guide the coolant to flow through the circumferential groove wall along the axial direction of the disc motor.

3. The disc motor according to any one of claims 1-2, characterized in that, Along the axial direction of the disc motor, the length of one circumferential slot wall is less than or equal to the length of the stator core; The length of one circumferential heat dissipation section is greater than the circumference of one circumferential groove wall; The width of the circumferential heat dissipation section along the radial direction of the disc motor is less than the thickness of the circumferential groove wall.

4. The disc motor according to any one of claims 1-3, characterized in that, The one end-face flow channel further includes another end-face heat dissipation section, the other end-face heat dissipation section being connected to the one peripheral heat dissipation section via another coupling flow channel, wherein: The one end face heat dissipation section and the other end face heat dissipation section are respectively used to guide the coolant to flow in the same direction through different parts of the bottom of the axial groove; The circumferential heat dissipation section is used to guide the coolant output from the one end heat dissipation section and the coolant output from the other end heat dissipation section to flow in opposite directions through different parts of the circumferential groove wall.

5. The disc motor according to claim 4, characterized in that, The stator housing further includes a bearing sleeve for fixing the outer ring of a bearing, and the inner ring of the bearing for fixing the motor shaft of the disc motor. The bearing sleeve includes a bearing flow channel, wherein: The bearing flow channel is used to connect the other end face heat dissipation section, and the bearing flow channel and the other end face heat dissipation section are respectively used to guide the coolant to flow through the bearing sleeve and the bottom of the axial groove in different directions.

6. The disc motor according to any one of claims 1-5, characterized in that, The circumferential groove wall includes a plurality of circumferential grooves, the plurality of circumferential grooves being used to form the circumferential heat dissipation section, and at least one of the circumferential grooves being used to connect to an end face heat dissipation section through a coupling flow channel, wherein: Along the circumferential direction of the disc motor, the length of each of the circumferential grooves is less than the circumference of the circumferential groove wall; Along the axial direction of the disc motor, the length of each of the circumferential grooves is less than the length of the circumferential groove wall.

7. The disc motor according to claim 6, characterized in that, The plurality of circumferential grooves includes two sets of circumferential grooves, one set of circumferential grooves and the other set of circumferential grooves are arranged along the axial direction of the disc motor, wherein: Along the circumference of the disc motor, multiple circumferential grooves in each group of circumferential grooves are arranged at intervals, and the interval between two adjacent circumferential grooves in each group of circumferential grooves is less than the length of any one of the two circumferential grooves.

8. The disc motor according to claim 7, characterized in that, Along the axial direction of the disc motor, a portion of one of the circumferential grooves in one set of circumferential grooves and a portion of another circumferential groove in another set of circumferential grooves are arranged adjacent to each other, and the portion of one circumferential groove and the portion of another circumferential groove are connected along the axial direction of the disc motor.

9. The disc motor according to claim 8, characterized in that, At least one of the portions of one circumferential groove or the other circumferential groove has a circumferential length greater than the axial length of at least one of the circumferential grooves or the other circumferential groove.

10. The disc motor according to any one of claims 1-9, characterized in that, The bottom of the axial groove includes at least one end face groove, the at least one end face groove being used to form the end face heat dissipation section, wherein: Each of the end face grooves is located around the center of the bottom of the axial groove in one of a clockwise or counterclockwise direction, and one or more of the at least one end face grooves are used to connect a peripheral heat dissipation section through one of the coupling channels.

11. The disc motor according to claim 10, characterized in that, The at least one end face groove includes a first end face groove and a second end face groove, wherein: Along the radial direction of the disc motor, the distance between the first end face groove and the center of the disc motor is greater than the distance between the second end face groove and the center of the disc motor. The first end face groove and the second end face groove are respectively connected to the peripheral heat dissipation section through different coupling flow channels, and the flow direction of the coolant in the first end face groove and the second end face groove is the same.

12. The disc motor according to claim 11, characterized in that, The at least one end face groove further includes a third end face groove and a radial groove, wherein the radial groove connects the first end face groove and the third end face groove, and the third end face groove connects the second end face groove, wherein: Along the radial direction of the disc motor, the distance between the third end face groove and the center of the disc motor is less than the distance between the second end face groove and the center of the disc motor. Along the axial direction of the disc motor, the groove depth of the third end face is greater than the groove depth of the first end face groove and the groove depth of the second end face groove.

13. The disc motor according to any one of claims 1-12, characterized in that, At least one of the axial groove bottoms or the circumferential groove walls of the stator housing includes an inner shell and an outer shell, wherein: The inner shell and the outer shell of the axial groove bottom are arranged adjacent to each other along the axial direction of the disc motor. There are multiple axial gaps between the inner shell and the outer shell. The multiple axial gaps are used to form the end face flow channel. At least one of the axial gaps is used to form the end face portion of the coupling flow channel. The width of each axial gap along the radial direction of the disc motor is greater than its depth along the axial direction of the disc motor. The inner shell and the outer shell of the circumferential groove wall are arranged adjacent to each other in the radial direction of the disc motor. There are multiple radial gaps between the inner shell and the outer shell. The multiple radial gaps are used to form the circumferential flow channel. At least one of the radial gaps is used to form the circumferential portion of the coupling flow channel. Two radial gaps adjacent in the circumferential direction of the disc motor are spaced apart, and two radial gaps adjacent in the axial direction of the disc motor are connected.

14. A powertrain, characterized in that, The powertrain includes a transmission and a disc motor as described in any one of claims 1-13, the disc motor being used to receive drive from an engine via the transmission, or the disc motor being used to drive wheels via the transmission.

15. An electric vehicle, characterized in that, The electric vehicle includes a frame, a power battery, and a powertrain as described in claim 14. The frame is used to fix the power battery and the powertrain. The disc motor is used to drive the vehicle using electrical energy provided by the power battery, or to charge the power battery using electrical energy provided by the disc motor.

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