Motor and vehicle

Abstract

The utility model discloses a motor and a vehicle, the motor comprises a shell and a guide plate, the shell is provided with a cooling flow channel, a liquid inlet and a liquid outlet, the liquid inlet and the liquid outlet are communicated with the cooling flow channel and located at the two axial ends of the shell, and the guide plate is arranged in the cooling flow channel; the axial distance between every two adjacent flow guide plates adjacent to the liquid outlet is smaller than the axial distance between every two adjacent flow guide plates adjacent to the liquid inlet. Therefore, the cooling flow channel and the heat source are limited in the motor through the shell, the cooling liquid is injected into the cooling flow channel, and the multiple flow guide plates are arranged in the flowing direction of the cooling liquid, so that the flow area closer to the liquid outlet is smaller and the flow speed of the cooling liquid is higher by changing the distance between the adjacent flow guide plates. Therefore, the heat exchange efficiency between the cooling liquid close to the liquid outlet area and the heat source can be compensated, so that the cooling flow channel can uniformly dissipate heat of the motor, and the phenomenon that the cooling liquid close to the liquid outlet area is difficult to cool the motor is prevented.

Description

Technical Field

[0001] This application relates to the field of motor technology, and in particular to an electric motor and a vehicle. Background Technology

[0002] In related technologies, since motors generate heat during operation, cooling channels need to be set up around the motor to cool it down; however, the cooling effect produced by the cooling channels in conventional motors is uneven, which leads to poor heat dissipation and cooling of the cooling channels. Utility Model Content

[0003] This application aims to at least solve one of the technical problems existing in the prior art. To this end, one object of this application is to provide an electric motor and a vehicle, wherein the electric motor has cooling channels that can uniformly cool the electric motor to maintain a good cooling effect.

[0004] In a first aspect, embodiments of this application propose an electric motor, including a housing and a guide plate. The housing has a cooling channel and an inlet and an outlet connected to the cooling channel and located at both ends of the housing along the axial direction. The guide plate is disposed within the cooling channel. The axial distance between adjacent guide plates near the outlet is smaller than the axial distance between adjacent guide plates near the inlet.

[0005] According to the embodiments of this application, the motor confines the cooling channel and heat source within the motor housing. Coolant is injected into the cooling channel, and multiple guide vanes are arranged along the flow direction of the coolant. By changing the distance between adjacent guide vanes, the flow area closer to the outlet is smaller, and the coolant flow velocity is higher. This compensates for the reduced heat exchange efficiency between the coolant and the heat source near the outlet, allowing the cooling channel to dissipate heat evenly to the motor. This prevents the coolant near the outlet from failing to effectively cool the motor, thereby improving the cooling effect on the motor.

[0006] According to some embodiments of this application, the guide plate is constructed as a spiral plate segment, and multiple spiral plate segments are connected in sequence.

[0007] According to some embodiments of this application, the housing includes: an inner shell and an outer shell, a cooling flow channel is defined between the inner shell and the outer shell, and a guide plate is formed in the inner shell, and a liquid inlet and a liquid outlet are formed in the outer shell.

[0008] According to some embodiments of this application, a heat dissipation protrusion is provided on the surface of the outer shell facing the inner shell.

[0009] According to some embodiments of this application, there are multiple heat dissipation protrusions, and the multiple heat dissipation protrusions are arranged in an array on the side surface of the outer shell facing the inner shell.

[0010] According to some embodiments of this application, the heat dissipation protrusion is constructed as a hollow structure, and the heat dissipation protrusion is filled with a phase change cooling medium.

[0011] According to some embodiments of this application, an injection portion is formed on the heat dissipation protrusion, which is used to inject or extract the phase change cooling medium.

[0012] According to some embodiments of this application, the heat dissipation protrusion is constructed such that at least a portion of its cross-sectional profile is circular, and an injection hole is provided on the circular portion. The injection portion is constructed of sealing rubber and is sealed in the injection hole.

[0013] According to some embodiments of this application, the guide plate and the heat dissipation protrusion are radially spaced apart.

[0014] Secondly, this application proposes a vehicle equipped with the motor described in the above embodiments.

[0015] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0016] The above and / or additional aspects and advantages of this application will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0017] Figure 1 This is a schematic diagram of the structure of an electric motor according to an embodiment of this application;

[0018] Figure 2 This is a cross-sectional structural schematic diagram of an electric motor according to an embodiment of this application;

[0019] Figure 3 This is a schematic diagram of the inner shell and guide plate structure according to an embodiment of this application;

[0020] Figure 4 This is a schematic diagram of the outer shell structure according to an embodiment of this application;

[0021] Figure 5 This is a schematic diagram of the heat dissipation protrusion structure according to an embodiment of this application;

[0022] Figure 6 This is a schematic diagram of the heat dissipation protrusion from another angle according to an embodiment of this application.

[0023] Figure label:

[0024] 100 - Motor;

[0025] 10-Shell;

[0026] 11-liquid inlet, 12-liquid outlet;

[0027] 13-Outer shell;

[0028] 131 - Heat dissipation protrusion, 1311 - Injection section;

[0029] 14-Inner shell;

[0030] 20-Blower plate;

[0031] 21-First section of board, 22-Second section of board, 23-Third section of board, 24-Fourth section of board, 25-Fifth section of board;

[0032] a-Cooling channel, b-Cavity, c-Cavity. Detailed Implementation

[0033] The embodiments of this application are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this application, and should not be construed as limiting this application.

[0034] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0035] In the description of this application, "first feature" and "second feature" may include one or more of the features.

[0036] In the description of this application, "multiple" means two or more.

[0037] In the description of this application, the first feature being "above" or "below" the second feature may include the first and second features being in direct contact, or the first and second features being in contact through another feature between them.

[0038] In the description of this application, the terms "above," "over," and "on top" for the first feature and the second feature include the first feature being directly above or diagonally above the second feature, or simply indicate that the first feature is at a higher horizontal level than the second feature.

[0039] Reference Figures 1-6To understand the motor 100 and the vehicle according to embodiments of this application.

[0040] refer to Figures 1-4 According to the embodiment of this application, the motor 100 includes a housing 10 and a guide plate 20.

[0041] While providing power, the motor 100 also generates heat, causing it to heat up. The increased temperature of the motor 100 may affect its working condition, or cause damage to its internal armature due to the high temperature.

[0042] In order to cool down the motor 100, the housing 10 of the motor 100 has a cooling channel a and an inlet 11 and an outlet 12 connected to the cooling channel a and located at both ends of the housing 10 in the axial direction. Coolant is filled into the cooling channel a, and heat is exchanged between the coolant and the housing 10. The heat source in the motor 100 can transfer heat to the housing 10, so as to indirectly cool the heat source inside the motor 100 through heat exchange between the coolant and the housing 10.

[0043] For example, the heat source in the motor 100 is an armature (not shown in the figure, which may include a stator assembly and a rotor assembly) used to generate power. The armature is disposed in the housing 10 and has a cooling channel a on its outer periphery. The cooling channel a and the armature can be separated by the housing 10, so that the armature and the cooling channel a can exchange heat through the housing 10. The heat generated by the armature is carried away by the coolant in the cooling channel a, thereby achieving the function of cooling.

[0044] However, the inventors discovered that after the coolant enters the cooling channel a through the inlet 11 and undergoes heat exchange with the motor 100, the temperature of the coolant will rise; as the coolant gradually flows to the outlet 12, its temperature will also gradually increase.

[0045] Therefore, in the cooling channel a, in the area near the inlet 11, the coolant maintains its temperature at the time of entering the cooling channel a because the degree of heat exchange between the coolant and the heat source is relatively low. During the flow of the coolant, the coolant flows in the cooling channel a and continuously exchanges heat with the heat source, causing the coolant temperature to gradually increase. Therefore, the coolant temperature is higher in the area closer to the outlet 12.

[0046] In other words, the coolant temperature varies in different areas of cooling channel a, resulting in different temperature differences between the coolant and the heat source of motor 100 in each area; specifically, the temperature difference between the coolant and the heat source is greater closer to the inlet 11 and smaller closer to the outlet 12. Furthermore, the smaller the temperature difference between the heat source and the coolant, the lower the heat exchange efficiency and the worse the cooling effect. Therefore, the cooling effect on the heat source is uneven in different areas of cooling channel a, leading to poor heat dissipation of motor 100.

[0047] To ensure a more even heat exchange in all areas of the cooling channel a and thus improve the heat dissipation of the motor 100, guide plates 20 are installed within the cooling channel a. The axial distance between adjacent guide plates 20 near the liquid outlet 12 is smaller than the axial distance between adjacent guide plates 20 near the liquid inlet 11. Specifically, multiple guide plates 20 are arranged sequentially along the axial direction of the housing 10 in the cooling channel a. The channels defined by two adjacent guide plates 20 are interconnected, forming a flow path from the liquid inlet 11 to the liquid outlet 12. Furthermore, the closer the channel is to the liquid outlet 12, the smaller the flow area it defines due to the reduced axial distance between adjacent guide plates 20.

[0048] For example Figure 2 As shown, exemplarily, the cooling channel a includes five guide plates 20 arranged sequentially along the axis of the housing 10. The two guide plates 20 near the end of the housing 10 are attached to the end plate of the housing 10. Between each adjacent guide plate 20, four channel segments are sequentially defined along the axis of the housing 10. These channel segments are connected sequentially to form a guiding channel within the cooling channel a, used to guide the flow of coolant. The five guide plates 20 are all arranged around the periphery of the armature and are inclined to guide the coolant to flow around the periphery of the armature. In this way, the coolant can enter from the inlet 11 and flow to the outlet 12 under the guiding action of the guiding channels defined by the guide plates 20, thereby achieving cooling and heat dissipation of the armature.

[0049] Here, the five guide vanes 20 are defined as the first section 21, the second section 22, the third section 23, the fourth section 24, and the fifth section 25, respectively.

[0050] The axial distance between the first plate segment 21 and the second plate segment 22 along the axis of the housing 10 is the largest, and the flow area of ​​the channel segment defined by the two segments is the largest. The axial distance between the second plate segment 22 and the third plate segment 23, and the axial distance between the fourth plate segment 24 and the fifth plate segment 25 gradually decrease, and the flow area of ​​the corresponding channel segments decreases in turn. Furthermore, the axial distance between the fourth plate segment 24 and the fifth plate segment 25 along the axis of the housing 10 is the smallest, and the flow area of ​​the channel segment defined by the two segments is the smallest.

[0051] Therefore, when the flow rate of the coolant is constant, as the flow area of ​​the coolant gradually decreases while the flow rate remains essentially constant, the flow velocity of the coolant through each channel segment gradually increases. Consequently, the coolant flow velocity is faster closer to the outlet 12. When the coolant flows past the heat source at a higher velocity, the relative velocity between it and the heat source increases. This means that the coolant can carry away the heat generated by the heat source more quickly, thereby promoting the efficiency of heat transfer from the heat source to the coolant and improving the heat exchange effect. Furthermore, increasing the fluid velocity also increases turbulence, which also helps to enhance the heat exchange effect.

[0052] Thus, although the temperature of the coolant is higher, the temperature difference between it and the heat source is smaller, and the heat exchange effect is worse in the area closer to the outlet 12 in the cooling channel a, the flow area of ​​each area of ​​the cooling channel a is limited by the guide plate 20, so that the flow area of ​​the channel section closer to the outlet 12 is smaller. This increases the flow velocity of the coolant in the area closer to the outlet 12, thereby improving the heat exchange effect between the coolant and the heat source in the corresponding area by increasing the flow velocity in the corresponding area. That is, the coolant flow velocity is higher closer to the outlet 12, so as to compensate for the reduced heat exchange effect between the heat source and the coolant due to the reduced temperature difference. This makes the overall heat exchange effect between the cooling channel a and the heat source more uniform in each area, so that the overall heat exchange generated by the cooling channel a for the motor 100 is better.

[0053] According to the embodiment of this application, the motor 100 confines the cooling channel a and the heat source within the motor 100 via the housing 10. Coolant is injected into the cooling channel a, and multiple guide plates 20 are arranged along the flow direction of the coolant. By changing the distance between adjacent guide plates 20, the flow area closer to the outlet 12 is smaller, and the coolant flow velocity is higher. This compensates for the reduced heat exchange efficiency between the coolant and the heat source near the outlet 12, enabling the cooling channel a to uniformly dissipate heat from the motor 100. This prevents the coolant near the outlet 12 from failing to effectively cool the motor 100, thereby improving the cooling effect on the motor 100.

[0054] Of course, cooling channel a can be constructed in various ways. Following this, taking a spiral cooling channel a as an example, we will combine it with... Figures 2-4 The following is an exemplary description.

[0055] The housing 10 includes an inner shell 14 and an outer shell 13. Both the inner shell 14 and the outer shell 13 are constructed as hollow cylinders. The outer shell 13 is fitted outside the inner shell 14 to define a cooling flow channel a between the inner shell 14 and the outer shell 13. A guide plate 20 is formed on the inner shell 14, and a liquid inlet 11 and a liquid outlet 12 are formed on the outer shell 13. The cooling flow channel a is defined between the inner shell 14 and the outer shell 13.

[0056] Specifically, the inner shell 14 defines a chamber b, within which a heat-generating armature (not shown in the figure) is disposed. The outer peripheral wall of the armature contacts the inner shell 14, such that the outer peripheral wall of the armature fits against the cooling channel a, thus isolating the armature within it. In this way, the heat from the armature is dissipated to the inner shell 14, and then heat exchange occurs between the inner shell 14 and the coolant. The coolant carries away the heat from the armature by contacting the inner shell 14, thereby achieving the heat dissipation function.

[0057] It is understandable that the inner shell 14 and the outer shell 13 define a cooling flow channel a, so as to enclose the armature inside the cavity b defined by the inner shell, thereby isolating the armature from the coolant and preventing the coolant from seeping into the armature and affecting the normal operation of the armature.

[0058] like Figure 2 and Figure 3 In the corresponding example, the first plate 21, the second plate 22, the third plate 23, the fourth plate 24 and the fifth plate 25 are all constructed as spiral plate segments, and each spiral plate segment is set on the outer peripheral wall of the inner shell 14. Multiple spiral plate segments are connected in sequence to form a complete spiral plate.

[0059] The spiral axis of the spiral plate segment is aligned with the cylindrical axis of the inner shell 14. The spiral plate segment also extends to the inner side near the outer shell 13, thus defining a spiral channel segment between the outer shell 13 and the inner shell 14. When all the spiral plate segments are connected, the channel segment also connects to form a spiral-shaped flow channel. Furthermore, in each spiral plate segment arranged sequentially from the inlet 11 to the outlet 12 along the axial direction of the shell 10, the axial distance between adjacent spiral plate segments near the outlet 12 is smaller than the axial distance between adjacent spiral plate segments near the inlet 11, so that the coolant flow rate is faster closer to the outlet 12.

[0060] It is understandable that constructing the guide plate 20 as a spiral plate segment and finally connecting it into a spiral plate body to define a spiral flow channel that communicates with the liquid outlet 12 and the liquid inlet 11 can ensure that the coolant in the cooling channel a can flow smoothly through the flow channel defined by the guide plate 20; and the spiral plate segment surrounds the armature, so that the cooling channel a can fully contact various areas of the outer periphery of the armature, increasing the contact area between the cooling channel a and the armature, making the cooling effect of the cooling channel a more uniform.

[0061] In some embodiments, continue to refer to Figure 4 As shown, a heat dissipation protrusion 131 is provided on the side surface of the outer shell 13 facing the inner shell 14, and the protrusion direction of the heat dissipation protrusion 131 is towards the inner shell 14; therefore, when the motor 100 is working, the coolant flowing in the cooling channel a will pass through the heat dissipation protrusion 131 provided on the outer shell 13.

[0062] In this way, when the coolant flows through the heat dissipation protrusion 131, the flow path of the coolant will be disturbed by the protruding structure of the heat dissipation protrusion 131, and it will no longer maintain a smooth laminar flow state, but will change into a turbulent flow state. Compared with the laminar flow state, the turbulent flow state has a higher flow velocity change and a more complex vortex structure, which makes the heat exchange between the coolant and the heat source of the motor 100 (such as the armature) more complete, thereby improving the efficiency of heat exchange.

[0063] Furthermore, in the area near the outlet 12, the flow area of ​​the channel segment defined by the adjacent guide plate 20 is reduced, resulting in an increase in coolant velocity. Consequently, the turbulence effect generated when flowing through the heat dissipation protrusion 131 is more significant; that is, when the coolant with a higher flow velocity encounters the heat dissipation protrusion 131, the disturbance of its flow path is more pronounced, causing it to form stronger vortices and velocity changes, thereby improving the heat exchange effect in the corresponding area.

[0064] Understandably, the heat dissipation protrusion 131 can increase the turbulence of the coolant, thereby increasing the heat transfer coefficient between the coolant and the heat source by increasing the turbulence, so that the cooling effect of the cooling channel a is better; and the turbulence of the coolant is more obvious in the area near the outlet 12, so as to further enhance the heat exchange effect in the area of ​​the outlet 12 and make the heat dissipation more uniform.

[0065] Specifically, there are multiple heat dissipation protrusions 131, and these protrusions 131 are arranged in an array on the surface of the outer shell 13 facing the inner shell 14; for example... Figure 4 As shown, heat dissipation protrusions 131 are arranged around the inner peripheral wall of the housing 13 and are arranged sequentially along the axial direction of the housing 10 to form an array structure.

[0066] It is understandable that, since the heat dissipation protrusions 131 are arranged in an array, the flow rate of the coolant changes based on the axial distance between each adjacent guide plate 20; and, the presence of heat dissipation protrusions 131 in each region enables cooling and temperature reduction in each region of the cooling channel a, thereby improving the uniformity of heat dissipation in the cooling channel a.

[0067] Combination Figure 2 It is understood that the guide plate 20 and the heat dissipation protrusion 131 are radially spaced apart, wherein the guide plate 20 is spaced a certain distance from the edge of the housing 10 along the circumferential direction and the heat dissipation protrusion 131, so that the heat dissipation protrusion 131 is arranged in various areas of the cooling channel a, such as on the inner circumferential wall of the housing 13.

[0068] Specifically, the radial distance between the circumferential edge of the guide plate 20 and the heat dissipation protrusion 131 is small to ensure the guiding effect. In this way, it can be ensured that the coolant is guided through the guide plate 20 and flows efficiently along a predetermined spiral path, while allowing the heat dissipation protrusion 131 to effectively interfere with the coolant flow, promote turbulence formation, and enhance heat exchange.

[0069] For example, the radial spacing between the guide plate 20 and the heat dissipation protrusion 131 can be configured to be within 10 mm to ensure that the guide plate 20 can effectively guide the coolant to be evenly distributed around the armature, while the heat dissipation protrusion 131 can interfere with the coolant flow with minimal flow resistance, forming an ideal turbulent state, thereby achieving efficient and uniform heat exchange in the entire cooling channel a.

[0070] It is understandable that the guide plate 20 and the heat dissipation protrusion 131 are radially spaced so that the coolant is evenly distributed in the cooling channel a and can fully contact the heat dissipation protrusion 131 located on the inner wall of the housing 13; so as to ensure both the fluidity and turbulence of the coolant, thereby improving the cooling efficiency of the motor 100.

[0071] In some preferred examples, refer to Figures 5-6 As shown, the heat dissipation protrusion 131 has a hollow structure, and the heat dissipation protrusion 131 is filled with a phase change cooling medium. The phase change cooling medium can be any type of phase change material. The phase change material is selected such that when the ambient temperature is higher than the phase change point, it absorbs heat through phase change, and when the ambient temperature is lower than the phase change point, it releases heat through phase change. The absorption and release of heat are achieved through the energy conversion process of phase change.

[0072] When the motor 100 is operating, after heat exchange between the coolant and the armature, the coolant temperature rises above the phase change material's phase change temperature. At this point, the phase change material absorbs heat, and some of the coolant's heat is transferred to the phase change material, thus cooling the coolant. As the overall coolant temperature decreases, the coolant temperature near the outlet 12 will be even lower, increasing the temperature difference between the coolant and the heat source in the outlet 12 area, thereby enhancing the cooling effect in that area. When the motor 100 is not operating, the coolant and surrounding ambient temperature are below the phase change material's phase change temperature. The phase change material releases heat, which is transferred to the cooling water and the surrounding environment. Since the ambient temperature is low at this time, the motor 100 is not operating.

[0073] Therefore, the heat release process does not have an adverse effect on the motor 100 itself. Specifically, during the non-operating period of the motor 100, when the temperature of the coolant and the ambient temperature around the motor 100 gradually decreases below the phase change temperature of the phase change material, the phase change material begins to release heat, for example, the phase change material changes from a solid to a liquid state, and releases the heat previously absorbed; so that after the phase change material completes the heat release, its state returns to the initial stage where it can absorb heat again, preparing it for efficient heat absorption when the motor 100 operates again.

[0074] It is understandable that phase change materials can effectively absorb and disperse heat when the motor 100 is running, thereby further reducing the temperature of the coolant and improving the heat dissipation efficiency of the cooling channel. They can also exchange heat with the surrounding environment through a heat release process when the motor 100 is not working, without damaging the motor 100.

[0075] Furthermore, continue to refer to Figures 5-6 As shown, the heat dissipation protrusion 131 is constructed such that at least a portion of its cross-sectional profile is circular, and an injection hole is provided on the circular portion. The injection part 1311 is constructed of sealing rubber and seals the injection hole. Of course, the heat dissipation protrusion 131 can also be constructed in other shapes, and similarly, the injection hole can also be provided in other areas of the heat dissipation protrusion 131.

[0076] Specifically, the heat dissipation protrusion 131 is a hemispherical and bowl-shaped protrusion structure. Its outer shell 13 is made of metal, and an injection hole is constructed at the center of the fixed part area of ​​the heat dissipation protrusion 131. The sealing rubber filled in the injection hole defines a cavity c inside the heat dissipation protrusion 131, so as to isolate the phase change material in the heat dissipation protrusion 131 from the coolant in the cooling channel a.

[0077] Therefore, when the phase change material reaches the end of its service life or fails, it needs to be replaced. For example, the phase change material can be injected and extracted by puncturing the injection section 1311 with a syringe; after one puncture and extraction of the injection section 1311, the sealing rubber will automatically seal the puncture area to restore the seal due to its elastic properties. Of course, the sealing rubber can also be replaced with other materials with equivalent functions.

[0078] Understandably, the injection hole and injection section 1311 constructed in the heat dissipation protrusion 131 allow for the extraction and replenishment of the phase change material using a syringe. This enables timely replacement of the phase change material after it fails, ensuring the motor's heat dissipation performance. Furthermore, the replacement method is relatively simple and easy for users to operate.

[0079] The vehicle according to the embodiments of this application is equipped with the motor 100 in the above embodiments. The motor 100 has a good heat dissipation effect so that it can operate in a better working environment, thereby ensuring that the vehicle obtains stable driving force.

[0080] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0081] Although embodiments of this application have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of this application, the scope of which is defined by the claims and their equivalents.

Claims

1. An electric motor, characterized in that, include: The housing (10) has a cooling channel (a) and an inlet (11) and an outlet (12) connected to the cooling channel (a) and located at both ends of the housing (10) in the axial direction. A guide vane (20) is disposed within the cooling channel (a); wherein The axial distance between adjacent guide plates (20) near the liquid outlet (12) is smaller than the axial distance between adjacent guide plates (20) near the liquid inlet (11).

2. The motor according to claim 1, characterized in that, The guide plate (20) is constructed as a spiral plate segment, and multiple spiral plate segments are connected in sequence.

3. The motor according to claim 1, characterized in that, The housing (10) includes an inner shell (14) and an outer shell (13), wherein the cooling channel (a) is defined between the inner shell (14) and the outer shell (13), and the guide plate (20) is formed in the inner shell (14), and the liquid inlet (11) and the liquid outlet (12) are formed in the outer shell (13).

4. The motor according to claim 3, characterized in that, The outer shell (13) has a heat dissipation protrusion (131) on the side surface facing the inner shell (14).

5. The motor according to claim 4, characterized in that, There are multiple heat dissipation protrusions (131), and the multiple heat dissipation protrusions (131) are arranged in an array on the side surface of the outer shell (13) facing the inner shell (14).

6. The motor according to claim 4, characterized in that, The heat dissipation protrusion (131) is constructed as a hollow structure, and the heat dissipation protrusion (131) is filled with a phase change cooling medium.

7. The motor according to claim 6, characterized in that... An injection portion (1311) is formed on the heat dissipation protrusion (131), which is used to inject or extract the phase change cooling medium.

8. The motor according to claim 7, characterized in that, The heat dissipation protrusion (131) is constructed such that at least a portion of its cross-sectional profile is circular, and an injection hole is provided on the circular portion. The injection part (1311) is constructed of sealing rubber and is sealed in the injection hole.

9. The motor according to claim 4, characterized in that, The guide plate (20) and the heat dissipation protrusion (131) are radially spaced apart.

10. A vehicle, characterized in that, The motor is provided as described in any one of claims 1-9.

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