Rotor, motor, powertrain, and vehicle

Abstract

Embodiments of the present application relate to the technical field of motors, and disclose a rotor, a motor, a powertrain, and a vehicle. The rotor comprises a rotating shaft, permanent magnets, a flow guide structure sleeved on the rotating shaft, and a plurality of rotor laminations. The rotating shaft has a liquid storage cavity and a liquid discharge hole in communication with the liquid storage cavity. A flow guide groove in communication with the liquid discharge hole is provided on the flow guide structure. The plurality of rotor laminations are each located on two sides of the flow guide structure. A magnetic steel slot is provided on each rotor lamination. A permanent magnet is located in each magnetic steel slot, and a cooling gap is formed between the permanent magnet and an inner wall of the magnetic steel slot. A plurality of cooling gaps on a same side of the flow guide structure are sequentially in communication, forming a first cooling channel in communication with the flow guide groove. A cooling medium sequentially flows through the liquid storage cavity, the liquid discharge hole, the flow guide groove, and the first cooling channels to dissipate heat from the rotor. In this process, the cooling medium directly contacts the permanent magnets, thereby enhancing dissipation of heat from the permanent magnets. The plurality of first cooling channels can form parallel passages, balance the flow rates of the cooling medium at different positions, and alleviate the problem of local hot spots.

Description

Rotors, motors, powertrains and vehicles

[0001] This application claims priority to Chinese patent application filed on March 24, 2025, with application number 202510364073.7 and entitled "Rotor, Motor, Powertrain and Vehicle", the entire contents of which are incorporated herein by reference. Technical Field

[0002] This application relates to the field of electric motor technology, and more particularly to a rotor, electric motor, powertrain, and vehicle. Background Technology

[0003] The rotor in an electric motor typically consists of a rotor core and permanent magnets, with the permanent magnets installed in the magnetic slots of the rotor core. During rotor rotation (especially at high speeds), the loss density of the permanent magnets increases, and excessively high temperatures can cause the permanent magnets to demagnetize, affecting the motor's power performance and lifespan, and reducing vehicle safety. Summary of the Invention

[0004] This application provides a rotor, a motor, a powertrain, and a vehicle to improve the heat dissipation of the rotor, prevent permanent magnet demagnetization, improve the power performance and service life of the motor, and enhance vehicle safety.

[0005] To achieve the above objectives, the embodiments of this application adopt the following technical solutions:

[0006] In a first aspect, a rotor is provided for use in an electric motor, such as a drive motor or generator. The rotor includes: a shaft, a flow guiding structure, multiple rotor laminations, and a permanent magnet. The shaft has a liquid storage chamber, and an outlet hole communicating with the liquid storage chamber is formed on the outer peripheral wall of the shaft. The flow guiding structure is sleeved on the shaft and has a flow guiding groove that communicates with the outlet hole on the shaft. Multiple rotor laminations are sleeved on the shaft and located on opposite sides of the flow guiding structure. The multiple rotor laminations located on the same side of the flow guiding structure are, for example, stacked. Each rotor lamination has a magnetic groove. The permanent magnet is located within the magnetic groove, and a cooling gap is formed between the permanent magnet and the inner wall of the magnetic groove. The cooling gaps on the multiple rotor laminations located on the same side of the flow guiding structure are sequentially connected to form a first cooling channel, which communicates with the flow guiding groove on the flow guiding structure.

[0007] The rotor provided in some embodiments of this application, by sleeved with a flow-guiding structure and multiple rotor laminations on the rotating shaft, and inserting the flow-guiding structure between two adjacent rotor laminations, allows the flow-guiding grooves in the flow-guiding structure to communicate with the magnet slots in the multiple rotor laminations located on the same side of the flow-guiding structure. Specifically, the gap between the inner wall of the magnet slot on the rotor lamination and the permanent magnet located in the magnet slot is set, and this gap is reused as a cooling gap to accommodate the cooling medium. The cooling gaps on the multiple rotor laminations located on the same side of the flow-guiding structure are sequentially connected to form a first cooling channel, which is connected to the flow-guiding groove. By connecting the flow-guiding groove and the liquid outlet on the rotating shaft, a cooling path can be formed in which the liquid outlet, the flow-guiding groove, and the first cooling channel are sequentially connected.

[0008] In this way, during the operation of the rotor or its motor, the cooling medium in the liquid storage chamber of the shaft can flow out from the outlet hole and flow radially into the guide groove. The cooling medium in the guide groove can then flow axially along the shaft to both sides of the guide structure, simultaneously flowing into the first cooling channels on both sides of the guide structure. This achieves cooling of the rotor, reducing the temperature of the rotor laminations and permanent magnets.

[0009] Because the first cooling channels, located on both sides of the guide structure and connected to the same guide groove, have essentially the same structure and only penetrate multiple rotor laminations located on the same side of the guide structure, the flow distribution of the cooling medium in the first cooling channels on both sides of the guide structure is relatively even. This not only significantly reduces the length of the first cooling channels, which is beneficial for meeting the high-speed miniaturization and cost requirements of the motors used in the rotors, but also improves the uniformity of the flow distribution of the cooling medium at different locations in each of the first cooling channels. This effectively mitigates the problem of localized hot spots in the permanent magnets, effectively improving the power performance and service life of the motors used in the rotors, as well as vehicle safety.

[0010] Furthermore, since the first cooling channel is composed of multiple interconnected cooling gaps formed between the inner wall of the magnet slot and the permanent magnet, the cooling medium flowing into the first cooling channel can fill the space between the inner wall of the magnet slot and the permanent magnet, directly contacting the permanent magnet and rotor laminations. In this way, the cooling medium can directly cool and dissipate heat from the permanent magnet and rotor laminations, greatly enhancing the heat dissipation effect, effectively improving the problem of permanent magnet overheating during rotor rotation, and facilitating the elimination of localized hot spots in the permanent magnet. This effectively improves the power performance and service life of the motor used in the rotor, as well as vehicle safety.

[0011] Furthermore, in this embodiment of the application, the gap between the inner wall of the magnet slot in each rotor lamination and the permanent magnet located in the magnet slot is reused as a cooling gap that can accommodate the cooling medium, thereby forming a first cooling channel. There is no need to set up an additional cooling channel. This not only avoids affecting the structural strength of the rotor lamination, but also reduces mold costs and production costs.

[0012] In one possible design aspect, each rotor lamination has multiple magnet slots spaced apart circumferentially along the rotor lamination. The flow guiding structure has multiple flow guiding grooves spaced apart circumferentially along the flow guiding structure. Along the axial direction of the rotation shaft, in adjacent flow guiding structures and rotor laminations, each flow guiding groove overlaps with at least one cooling gap.

[0013] In this way, after the cooling medium enters the guide groove, it can directly contact the end face of the rotor lamination and flow smoothly into the cooling gap formed in the rotor lamination, reducing the resistance encountered by the cooling medium when it flows inside the rotor.

[0014] Moreover, when each guide groove overlaps with at least two cooling gaps, the number of guide grooves in the guide structure can be reduced. This avoids affecting the structural strength of the guide structure and allows the guide grooves to have larger dimensions. This is beneficial for reducing the resistance encountered by the cooling medium when it flows in the guide groove, and also for increasing the contact area between the cooling medium and the end face of the rotor laminations, thereby improving the heat dissipation effect on the rotor laminations and the rotor.

[0015] In one possible design approach, multiple magnet slots are divided into multiple magnet slot units, which are distributed circumferentially along the rotor laminations. Each magnet slot unit includes at least two magnet slots that are symmetrical about a direct axis. Along the axial direction of the rotor shaft, in adjacent flow guide structures and rotor laminations, each flow guide slot overlaps with at least two cooling gaps in the magnet slot unit.

[0016] This helps to improve the uniformity of the flow distribution of the cooling medium in each guide channel and its connected first cooling channel, helps to improve the problem of local hot spots in the permanent magnet, and improves the power performance and service life of the drive motor or generator used in the rotor, as well as the safety of the vehicle.

[0017] In the first possible design approach, two magnetic slots symmetrical about the direct axis form a V-groove structure. Along the circumference of the axis of rotation, the size of the guide channel is greater than the minimum distance between the two magnetic slots in the V-groove structure.

[0018] In this way, the adjacent ends of the two magnetic slots in each V-groove structure can overlap with the guide groove, so that the guide groove and the cooling gap formed by each magnetic slot in the V-groove structure are connected. Based on this, the circumferential dimensions of the guide groove on the rotating shaft can be adjusted to ensure the structural strength of the guide structure and meet the flow distribution requirements of the cooling medium.

[0019] In one possible design approach, multiple guide channels form a rotationally symmetric structure, with the center of rotation of the rotational symmetry structure being the axis of rotation. That is, these multiple guide channels are distributed rotationally symmetrically about the axis of rotation.

[0020] This approach helps reduce the processing difficulty of the flow guide structure and improves the uniformity of the flow distribution of the cooling medium in different flow guide grooves, enabling uniform cooling and heat dissipation of the permanent magnets at different locations, and effectively improving the local hot spot problem of the permanent magnets.

[0021] In one possible design approach, the magnetic steel trough includes a connected magnetic steel receiving section and a magnetic shielding section, with the permanent magnet located within the magnetic steel receiving section. The cooling gap includes the magnetic shielding section.

[0022] By reusing the magnetic shielding section inherent in the magnet slot itself as a cooling gap, it is unnecessary to create additional cooling channels in the rotor laminations, thus avoiding significant changes to the rotor lamination structure. This approach preserves the original structural strength and magnetic conductivity of the rotor laminations while avoiding increased mold and production costs, thereby enhancing versatility.

[0023] In one possible design aspect, the inner wall of the magnet housing section has multiple spring-loaded protrusions that separate the inner wall of the magnet housing section from the permanent magnet, forming a gap between the inner wall of the magnet housing section and the permanent magnet. This gap is connected to the magnetically shielding section. The cooling gap also includes this gap. That is, the cooling gap can be composed of the gap and the magnetically shielding section. The cooling gap substantially surrounds the permanent magnet.

[0024] In this way, the cooling medium flowing into the cooling gap or the first cooling channel can essentially surround the permanent magnet, directly contacting various points on the permanent magnet and the inner wall of the magnet slot, directly cooling and dissipating heat at different locations on the permanent magnet and the magnet slot. In other words, by setting the spring-loaded protrusions, the contact area between the permanent magnet and the magnet slot can be reduced, while the contact area between the cooling medium and the permanent magnet and rotor laminations can be increased. This significantly improves the heat dissipation effect on the permanent magnet and rotor laminations, greatly mitigating the problem of permanent magnet overheating during rotor rotation. It also effectively eliminates localized hot spots within the permanent magnet, effectively improving the power performance and service life of the drive motor or generator used in the rotor, as well as vehicle safety.

[0025] In one possible design approach, a first de-weighting hole is formed on the rotor lamination. Along the axial direction of the shaft, a flow guiding structure covers the first de-weighting hole on the adjacent rotor lamination.

[0026] By setting the first de-weighting hole, on the one hand, the weight of the rotor laminations can be reduced, the moment of inertia of the rotor during rotation can be reduced, the influence of inertia on the rotor can be reduced, and the stability of the rotor during deceleration can be improved; on the other hand, it is beneficial to reduce the stress at the location of the first de-weighting hole.

[0027] Moreover, by covering the first de-weighting hole with the flow guiding structure, the cooling medium can be prevented from accidentally flowing into the first de-weighting hole and having an adverse effect on the rotation of the rotor.

[0028] In one possible design approach, the rotor laminations have first de-weighting holes, and multiple rotor laminations located on the same side of the flow guiding structure have their first de-weighting holes connected sequentially to form a second cooling channel. The flow guiding groove is also connected to this second cooling channel.

[0029] By setting the first de-weighting hole, on the one hand, the weight of the rotor laminations can be reduced, the moment of inertia of the rotor during rotation can be reduced, the influence of inertia on the rotor can be reduced, and the stability of the rotor during deceleration can be improved; on the other hand, it is beneficial to reduce the stress at the location of the first de-weighting hole.

[0030] Moreover, by reusing multiple sequentially connected first de-duplication holes as second cooling channels, on the one hand, the contact area between the cooling medium and the rotor laminations can be increased, greatly improving the heat dissipation effect on the rotor laminations, and thus improving the heat dissipation effect on the rotor; on the other hand, it can avoid changing the structure of the rotor laminations, ensuring the structural strength of the rotor laminations, avoiding increasing mold costs and production costs, and enhancing universality.

[0031] In one possible design approach in the first aspect, along the axial direction of the shaft, in adjacent guide structures and rotor laminations, each guide groove overlaps with at least one first deweighting hole.

[0032] In this way, the cooling medium in the guide groove can directly contact the end face of the rotor lamination and flow into the first weight-removing hole formed in the rotor lamination more smoothly, reducing the resistance encountered by the cooling medium when flowing inside the rotor.

[0033] Moreover, when each guide groove overlaps with at least two first de-weighting holes, the number of guide grooves in the guide structure can be reduced. This avoids affecting the structural strength of the guide structure and allows the guide grooves to have a larger size. This is beneficial for reducing the resistance encountered by the cooling medium when it flows in the guide groove, and also for increasing the contact area between the cooling medium and the end face of the rotor lamination, thereby improving the heat dissipation effect on the rotor lamination and the rotor.

[0034] In the first possible design approach, a guide groove covers the outlet hole along its axial direction. This allows the cooling medium flowing from the outlet hole to directly flow into the corresponding guide groove, shortening the flow path of the cooling medium from the outlet hole to the guide groove and reducing the resistance encountered by the cooling medium when flowing between the outlet hole and the guide groove.

[0035] In one possible design approach, the liquid outlet and the guide structure are staggered along the axial direction of the shaft. A groove is formed on the inner circumferential surface of the rotor lamination located between the liquid outlet and the guide structure, and this groove connects the guide channel and the liquid outlet. In this way, the cooling medium flowing out of the liquid outlet can flow into this groove, and then into the guide channel. This arrangement allows for flexible arrangement of the liquid outlet along the axial direction of the shaft, enhancing the flexibility of the rotor and the motor used in its application.

[0036] In one possible design approach, the flow guiding structure is a flow guide plate. Alternatively, the flow guiding structure comprises multiple flow guiding blades stacked along the axial direction of the shaft.

[0037] In one possible design approach, the flow guiding structure is provided with a second de-weighting hole, and the second de-weighting hole and the flow guiding groove are spaced apart.

[0038] By setting a second de-weighting hole, on the one hand, the weight of the flow guiding structure can be reduced, the moment of inertia of the rotor during rotation can be reduced, the influence of inertia on the rotor can be reduced, and the stability of the rotor during deceleration can be improved; on the other hand, it is beneficial to reduce the stress at the location of the second de-weighting hole.

[0039] In one possible design approach, the flow guiding structure is provided with multiple flow guiding grooves and multiple second de-weighting holes, with the flow guiding grooves and second de-weighting holes alternately arranged along the circumference of the rotating shaft.

[0040] This balances the structural strength at different locations of the flow guide structure, reducing its weight and ensuring good structural stability.

[0041] In one possible design approach, a mounting groove is formed on the outer peripheral wall of the shaft, and a mounting key is provided on the inner peripheral surface of the flow guide structure, extending into the mounting groove. The mounting key and the flow guide groove are spaced apart.

[0042] By setting mounting keys and mounting slots, the flow guide structure and the rotating shaft can be fixed together. By spacing the mounting keys and flow guide slots, the transmission of the cooling medium can be avoided, thus preventing interference with the normal operation of the rotor and motor.

[0043] In a second aspect, an electric motor is provided, which can be a drive motor or a generator. The motor includes a rotor as described in any of the designs in the first aspect, and a stator. The stator is mounted on the rotor, and the rotor is rotatable relative to the stator.

[0044] Thirdly, a powertrain is provided, comprising: an electric motor as described in any of the designs in the second aspect, and a transmission. The transmission is connected to the electric motor.

[0045] Fourthly, a vehicle is provided, comprising: a powertrain as described in any of the designs in the third aspect, a transmission mechanism, and wheels. The transmission mechanism is connected to the powertrain, and the wheels are connected to the transmission mechanism. The powertrain can drive the wheels via the transmission mechanism.

[0046] The technical effects of any of the design methods in the second to fourth aspects can be found in the technical effects of different design methods in the first aspect, and will not be repeated here. Attached Figure Description

[0047] Figure 1 is a structural diagram of a vehicle provided in an embodiment of this application;

[0048] Figure 2 is an architectural diagram of a powertrain provided in an embodiment of this application;

[0049] Figure 3 is a structural diagram of a motor provided in an embodiment of this application;

[0050] Figure 4a is a three-dimensional structural diagram of a rotor provided in an embodiment of this application;

[0051] Figure 4b is a partial perspective structural diagram of a rotor provided in an embodiment of this application;

[0052] Figure 5a is a cross-sectional view of a rotor provided in an embodiment of this application;

[0053] Figure 5b is a cross-sectional view of another rotor provided in an embodiment of this application;

[0054] Figure 6 is a three-dimensional structural diagram of a rotating shaft provided in an embodiment of this application;

[0055] Figure 7a is a plan view of a flow guiding structure provided in an embodiment of this application;

[0056] Figure 7b is a planar structural diagram of another flow guiding structure provided in an embodiment of this application;

[0057] Figure 8a is a planar structural diagram of a rotor lamination provided in an embodiment of this application;

[0058] Figure 8b is a planar structural diagram of another rotor lamination provided in an embodiment of this application;

[0059] Figure 9a is a planar structural diagram of a rotor lamination and a permanent magnet provided in an embodiment of this application;

[0060] Figure 9b is a planar structural diagram of another rotor lamination and permanent magnet provided in an embodiment of this application;

[0061] Figure 10a is a planar structural diagram of a flow guiding structure and rotor lamination provided in an embodiment of this application;

[0062] Figure 10b is a planar structural diagram of another flow guiding structure and rotor lamination provided in an embodiment of this application;

[0063] Figure 11 is a cross-sectional structural diagram of another rotor provided in an embodiment of this application;

[0064] Figure 12 is a three-dimensional structural diagram of another rotating shaft provided in an embodiment of this application;

[0065] Figure 13 is a planar structural diagram of another rotor lamination provided in an embodiment of this application;

[0066] Figure 14 is a three-dimensional structural diagram and a partial structural diagram of a rotor lamination provided in an embodiment of this application;

[0067] Figure 15 is a planar structural diagram of another flow guiding structure and rotor lamination provided in an embodiment of this application;

[0068] Figure 16 is a cross-sectional structural diagram of another rotor provided in an embodiment of this application;

[0069] Figure 17 is a planar structural diagram of another flow guiding structure and rotor lamination provided in an embodiment of this application;

[0070] Figure 18 is a partial cross-sectional view of a rotor provided in an embodiment of this application. Detailed Implementation

[0071] The technical solutions of the embodiments of this application will now be described with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments provided in this application are within the scope of protection of this application.

[0072] In the description of the embodiments of this application, unless otherwise stated, "multiple" means two or more. "At least one" or similar expressions refer to any combination of these items, including any combination of a single item or a plurality of items. For example, at least one of a, b, and c can represent: a, b, c, ab, ac, bc, or abc, where a, b, and c can be single or multiple. "a and / or b" includes the following three combinations: only a, only b, and a combination of a and b. "Spacing" refers, for example, to the minimum distance between two adjacent structures.

[0073] Furthermore, to facilitate a clear description of the technical solutions in the embodiments of this application, the terms "first" and "second" are used in the embodiments of this application to distinguish identical or similar items with substantially the same function and effect. Those skilled in the art will understand that the terms "first" and "second" do not limit the quantity or execution order, and that "first" and "second" do not necessarily imply difference. Meanwhile, in the embodiments of this application, the terms "exemplary" or "for example" are used to indicate that something is being used as an example, illustration, or description. Any embodiment or design scheme described as "exemplary" or "for example" in the embodiments of this application should not be construed as being better or more advantageous than other embodiments or design schemes. Specifically, the use of terms such as "exemplary" or "for example" is intended to present related concepts in a concrete manner for ease of understanding. Additionally, the use of "based on" implies openness and inclusivity, because processes, steps, calculations, or other actions "based on" one or more of the stated conditions or values ​​may in practice be based on additional conditions or values ​​beyond those stated.

[0074] As used herein, “parallel,” “perpendicular,” and “equal” include the described situation and situations that are similar to the described situation, within an acceptable range of deviation, which is determined by those skilled in the art taking into account the measurement under discussion and the error associated with the measurement of a particular quantity (i.e., the limitations of the measurement system). For example, “parallel” includes absolute parallelism and approximate parallelism, where an acceptable range of deviation for approximate parallelism may be, for example, within 5°; “perpendicular” includes absolute perpendicularity and approximate perpendicularity, where an acceptable range of deviation for approximate perpendicularity may also be, for example, within 5°; “equal” includes absolute equality and approximate equality, where an acceptable range of deviation for approximate equality may be, for example, a difference between the two equals being less than or equal to 5% of either one.

[0075] In this application embodiment, the terms "upper," "lower," "left," and "right" are not limited to the orientation of the components schematically placed in the accompanying drawings. It should be understood that these directional terms can be relative concepts used for description and clarification, and can vary accordingly depending on the orientation of the components in the accompanying drawings. In the drawings, for clarity, the thickness of layers and regions is exaggerated, and the dimensional proportions between the parts in the illustrations do not reflect actual dimensional proportions. Therefore, variations in shape relative to the drawings due to, for example, manufacturing techniques and / or tolerances are conceivable. Therefore, exemplary embodiments should not be construed as being limited to the shapes of the areas shown in this application, but rather include shape deviations due to, for example, manufacturing. For example, an etched area shown as rectangular would typically have a curved feature. Therefore, the areas shown in the drawings are schematic in nature, and their shapes are not intended to show the actual shapes of the areas of the device, nor are they intended to limit the scope of the exemplary embodiments.

[0076] Furthermore, the architecture and scenarios described in the embodiments of this application are for the purpose of more clearly illustrating the technical solutions of the embodiments of this application, and do not constitute a limitation on the technical solutions provided in the embodiments of this application. As those skilled in the art will know, with the evolution of architecture and the emergence of new scenarios, the technical solutions provided in the embodiments of this application are also applicable to similar technical problems.

[0077] Some embodiments of this application provide a vehicle, including an electric vehicle (EV), such as, but not limited to, a battery electric vehicle (BEV / PEV), a hybrid electric vehicle (HEV), a range-extended electric vehicle (REEV), a plug-in hybrid electric vehicle (PHEV), or a new energy vehicle (NEV). In some examples, the vehicle may be a sedan, SUV, bus, or truck. Furthermore, the vehicle may also be various special-purpose vehicles with specific functions, such as emergency rescue vehicles, water trucks, sewage suction trucks, cement mixer trucks, crane trucks, and medical vehicles.

[0078] The following description, in conjunction with the accompanying drawings, illustrates a vehicle according to an embodiment of this application. Figure 1 is a structural diagram of a vehicle according to an embodiment of this application, and Figure 2 is an architectural diagram of a powertrain according to an embodiment of this application. Those skilled in the art will understand that the vehicle architecture shown in Figures 1 and 2 does not constitute a limitation on the vehicle. The vehicle may include more or fewer components than those shown in Figures 1 and 2, or may combine some of the components shown in Figures 1 and 2, or may have a different component arrangement than those shown in Figures 1 and 2.

[0079] In some embodiments, as shown in FIG1, the vehicle may include a powertrain 1000, a transmission mechanism 2000, and wheels 3000. The powertrain 1000 and the transmission mechanism 2000 are connected, and the transmission mechanism 2000 is connected to the wheels 3000. The powertrain 1000 converts electrical energy into mechanical energy, and the transmission mechanism 2000 drives the powertrain 1000 and the wheels 3000 through a transmission mechanism 2000, allowing the powertrain 1000 to drive the wheels 3000 to rotate.

[0080] As shown in Figure 2, the powertrain 1000 may include a drive motor 100 and a transmission 200. The drive motor 100 and the transmission 200 are connected, for example, by a transmission connection; the transmission 200 is connected to the transmission mechanism 2000. The drive motor 100 can transmit power to the transmission 200, thereby driving the vehicle's transmission mechanism 2000 through the transmission 200.

[0081] Here, the drive motor 100 includes, but is not limited to, a permanent magnet synchronous motor (PMSM). PMSMs have advantages such as high power density, high operating efficiency, and high-speed miniaturization, and occupy a relatively important position in the main drive motors of vehicles (especially electric vehicles). The transmission 200 can be replaced by a reducer.

[0082] For example, the powertrain 1000 may further include an engine and a generator. The engine is driven by a transmission 200 for outputting power to the transmission 200. The generator is driven by a component (e.g., gears) within the transmission 200. The power output from the engine can be transmitted to the generator via the transmission 200, and the generator is capable of generating electricity and storing electrical energy in a power battery to charge the power battery.

[0083] Here, when the powertrain 1000 includes a drive motor 100, a transmission 200, an engine, and a generator, the powertrain 1000 is, for example, a hybrid system; when the powertrain 1000 has a drive motor 100 and a transmission 200 but no engine and generator, the powertrain 1000 is, for example, a pure electric system.

[0084] Furthermore, the powertrain 1000 may also include at least one of a motor control unit (MCU), an on-board charger (OBC), a DC-DC converter, a power distribution unit (PDU), and a battery control unit (BCU). The powertrain 1000 may integrate at least one of these components as needed.

[0085] For example, either the drive motor 100 or the generator may include a stator and a rotor, with the stator mounted on the rotor. During operation of the drive motor 100 or the generator, the rotor rotates relative to the stator.

[0086] The rotor of the drive motor 100 or generator contains permanent magnets. In recent years, with the continuous pursuit of high power density and high speed in drive motors 100 or generators, the loss density of the permanent magnets in the rotor has increased dramatically. Excessively high motor temperatures can cause the permanent magnets to demagnetize, affecting the power performance and service life of the drive motor 100 or generator, and reducing vehicle safety. Therefore, it is necessary to cool and dissipate heat from the rotor of the drive motor 100 or generator.

[0087] In some possible implementations, more efficient heat exchange can be achieved in the drive motor 100 or generator by incorporating oil passages inside the rotor. However, these oil passages are typically quite long; for example, the oil passage runs from one end plate of the rotor, through the rotor core, to the other end plate, then turns and runs back through the rotor core to the first end plate, connecting to the outside. This makes it difficult to meet the requirements of high-speed miniaturization and cost control for the drive motor 100 or generator. Moreover, during rotor rotation, a large centrifugal force is generated, which can easily lead to uneven oil distribution at different locations in the aforementioned oil passages, resulting in localized hot spots in the permanent magnets. This restricts further improvements in the power performance and service life of the drive motor 100 or generator, as well as vehicle safety.

[0088] Based on this, some embodiments of this application provide an electric motor and a rotor applied within the motor. This motor can function as the aforementioned drive motor 100 or the aforementioned generator, and can be applied to the aforementioned powertrain 1000 or a vehicle. The motor is, for example, an oil-cooling motor. The following is a schematic description of the motor and rotor provided in some embodiments of this application, with reference to the accompanying drawings.

[0089] In some embodiments, as shown in FIG3, the motor 300 may include a stator 310, a rotor 320, and a housing 330. The housing 330 is sleeved on the stator 310, the stator 310 is sleeved on the rotor 320, and is rotatably connected to the rotating shaft 1 of the rotor 320. The rotating shaft 1 can drively connect to the gearbox 200.

[0090] Furthermore, the stator 310 may include a stator core 3101 and a stator winding 3102. The stator core 3101 is sleeved on the rotor 320, and the stator winding 3102 is wound on the stator core 3101. When the stator winding 3102 is energized, a rotating magnetic field is formed on the inner circumference of the stator 310, which can drive the rotor 320 to rotate relative to the stator 310.

[0091] As shown in Figures 4a, 4b, 5a and 5b, the rotor 320 may include: a shaft 1, a flow guiding structure 2, rotor laminations 3 and a permanent magnet 4.

[0092] In some examples, as shown in Figures 5a and 5b, the rotating shaft 1 can be a hollow shaft with a liquid storage chamber 11 inside. Along the axial direction of the rotating shaft 1, one end of the shaft 1 has an opening that connects to the liquid storage chamber 11, facilitating the introduction of a cooling medium into the liquid storage chamber 11. For example, the cooling medium includes, but is not limited to, cooling oil.

[0093] Referring to Figures 5a, 5b, and 6, a liquid outlet hole 12 is provided on the outer peripheral wall of the rotating shaft 1, which connects to the liquid storage chamber 11. The cooling medium in the liquid storage chamber 11 can flow out of the liquid storage chamber 11 through the liquid outlet hole 12. The liquid outlet hole 12 extends radially along the rotating shaft 1, for example. The diameter of the liquid outlet hole 12 can be selected and set according to the flow rate of the cooling medium flowing out of the liquid storage chamber 11, and this embodiment does not limit this.

[0094] In some examples, referring to Figures 4a, 5a, and 7a, or referring to Figures 4a, 5b, and 7b, the flow guiding structure 2 is annular and fitted onto the rotating shaft 1. The flow guiding structure 2 has an inner circumferential surface and an outer circumferential surface. The inner circumferential surface of the flow guiding structure 2 refers to the side surface that contacts the rotating shaft 1, and the outer circumferential surface refers to the side surface that faces away from the rotating shaft 1. A flow guiding groove 21 is provided on the flow guiding structure 2. Along the axial direction of the rotating shaft 1, the flow guiding groove 21 penetrates the flow guiding structure 2; along the radial direction of the rotating shaft 1, the flow guiding groove 21 can penetrate the inner circumferential surface of the flow guiding structure 2 and extend towards the outer circumferential surface of the flow guiding structure 2.

[0095] In some examples, referring to Figures 4a, 5a, and 8a, or referring to Figures 4a, 5b, and 8b, the rotor laminations 3 are annular and fitted onto the rotating shaft 1. There are multiple rotor laminations 3, located on opposite sides of the flow guide structure 2. Multiple rotor laminations 3 on the same side of the flow guide structure 2 are stacked sequentially, for example, by pressing, bonding, or welding. Along the axial direction of the rotating shaft 1, the number of rotor laminations 3 on both sides of the flow guide structure 2 can be the same or different. For example, in Figures 4a, 5a, and 5b, the number of rotor laminations 3 on both sides of the flow guide structure 2 is the same. The number or thickness of the rotor laminations 3 can be selected according to actual design requirements.

[0096] For example, the rotor lamination 3 can be a silicon steel sheet or a silicon steel sheet, or of course, laminations made of other materials can also be used.

[0097] Referring again to Figures 4a, 8a, and 8b, each rotor lamination 3 has a magnetic slot 31 extending through it along the axial direction of the shaft 1. The magnetic slot 31 accommodates the permanent magnet 4; specifically, as shown in Figures 4a, 9a, and 9b, the permanent magnet 4 is located within the magnetic slot 31. Different rotor laminations 3 can have the same structure. For example, multiple rotor laminations 3 may overlap along the axial direction of the shaft 1; or, as shown in Figures 4a and 4b, two adjacent rotor laminations located on the same side of the flow guide structure 2 are rotated outwards at a certain angle. In both arrangements, along the axial direction of the shaft 1, in two adjacent rotor laminations located on the same side of the flow guide structure 2, the magnetic slots 31 overlap or are rotated outwards at a certain angle and are connected; the permanent magnets 4 located within the magnetic slots 31 overlap or are rotated outwards at a certain angle and are in contact.

[0098] As shown in Figures 4a, 9a, and 9b, along the axial direction of the rotating shaft 1, the area of ​​the permanent magnet 4 is smaller than the area of ​​the magnetic steel groove 31, and there is a gap between the permanent magnet 4 and the inner wall of the magnetic steel groove 31, that is, the permanent magnet 4 does not completely occupy the space inside the magnetic steel groove 31. A cooling gap 32 is formed between the permanent magnet 4 and the inner wall of the magnetic steel groove 31. Along the axial direction of the rotating shaft 1, in two adjacent rotor laminations 3 located on the same side of the guide structure 2, the cooling gaps 32 coincide or are rotated out at a certain angle and are connected. Further, as shown in Figures 5a and 5b, the cooling gaps 32 on multiple rotor laminations 3 located on the same side of the guide structure 2 are connected in sequence to form the first cooling channel D1. For example, in Figures 5a and 5b, multiple interconnected cooling gaps 32 in the multiple rotor laminations 3 located on the left side of the flow guide structure 2 constitute a first cooling channel D1; in the multiple rotor laminations 3 located on the right side of the flow guide structure 2, multiple interconnected cooling gaps 32 constitute a first cooling channel D1.

[0099] In some examples, as shown in Figures 5a and 5b, each first cooling channel D1 is connected to the guide groove 21 in the guide structure 2. Referring to Figures 10a and 10b, this guide groove 21 is also connected to the liquid outlet 12 in the rotating shaft 1. The guide groove 21 can serve as a radial flow channel, allowing the cooling medium to enter radially. The first cooling channel D1 can also serve as an axial flow channel.

[0100] Accordingly, as shown in Figures 5a and 5b, during the operation of the rotor 320 or the motor 300, the cooling medium in the liquid storage chamber 11 of the rotating shaft 1 can flow out from the liquid outlet 12 and flow radially into the guide groove 21. The cooling medium in the guide groove 21 can flow axially along the rotating shaft 1 towards the left side of the guide structure 2 and into the first cooling channel D1 on the left side of the guide structure 2; simultaneously, the cooling medium in the guide groove 21 can also flow axially along the rotating shaft 1 towards the right side of the guide structure 2 and into the first cooling channel D1 on the right side of the guide structure 2. After flowing through the first cooling channel D1, the cooling medium can be discharged from the rotor 320. Here, as shown in Figures 5a and 5b, under the action of centrifugal force, the direction in which the cooling medium is discharged from the rotor 320 can have a certain angle with the axial or radial direction of the rotating shaft 1. In this way, the cooling medium can be sprayed onto the stator 310 to cool the stator 310. The cooling medium can be recycled through a circulation loop. Specifically, it can flow into the liquid storage chamber 11 of the rotating shaft 1 for recycling.

[0101] In this way, the rotor 320 can be cooled down, reducing the temperature of the rotor laminations 3 and permanent magnets 4 in the rotor 320.

[0102] Understandably, since the first cooling channel D1 is composed of multiple interconnected cooling gaps 32, and these gaps 32 are formed between the inner wall of the magnetic steel groove 31 and the permanent magnet 4, the cooling medium flowing into the first cooling channel D1 can fill the space between the inner wall of the magnetic steel groove 31 and the permanent magnet 4, directly contacting the permanent magnet 4 and the rotor laminations 3. In this way, the cooling medium can directly cool and dissipate heat from the permanent magnet 4 and the rotor laminations 3, greatly enhancing the heat dissipation effect on the permanent magnet 4 and the rotor laminations 3. This effectively improves the problem of overheating of the permanent magnet 4 during the rotation of the rotor 320, and facilitates the elimination of local hot spots in the permanent magnet 4, effectively improving the power performance and service life of the motor 300 used in the rotor 320, as well as the safety of the vehicle.

[0103] Furthermore, the first cooling channels D1 located on both sides of the flow guide structure 2 and connected to the same flow guide groove 21 can form parallel cooling channels (also known as oil circuits). The structure of each first cooling channel D1 is basically the same, and it only passes through multiple rotor laminations 3 located on the same side of the flow guide structure 2. The cooling medium in the flow guide groove 21 can flow synchronously through the first cooling channels D1 on both sides of the flow guide structure 2, and the flow distribution of the cooling medium is relatively even. In this way, not only can the length of the first cooling channel D1 be greatly reduced, which is beneficial to meeting the high-speed miniaturization and cost requirements of the motor 300 used in the rotor 320; it can also improve the uniformity of the flow distribution of the cooling medium at different positions in each first cooling channel D1, effectively improve the problem of local hot spots in the permanent magnet 4, and effectively improve the power performance and service life of the motor 300 used in the rotor 320, as well as the safety of the vehicle.

[0104] Furthermore, in this embodiment of the application, the gap between the inner wall of the magnet slot 31 in each rotor lamination 3 and the permanent magnet 4 located in the magnet slot 31 is reused as a cooling gap 32 that can accommodate the cooling medium, thereby forming the first cooling channel D1. There is no need to set up an additional cooling channel. This not only avoids affecting the structural strength of the rotor lamination 3, but also reduces mold costs and production costs.

[0105] In the aforementioned rotating shaft 1 and flow guiding structure 2, there can be multiple liquid outlet holes 12, which are arranged at intervals along the circumference of the rotating shaft 1, for example. Similarly, there can be multiple flow guiding channels 21, which are also arranged at intervals along the circumference of the rotating shaft 1. The number of liquid outlet holes 12 and flow guiding channels 21 can be the same, and they are connected in a one-to-one correspondence. For example, Figures 10a and 10b show six liquid outlet holes 12 and six flow guiding channels 21, respectively, which are connected in a one-to-one correspondence.

[0106] The positional relationship between the liquid outlet 12 and the connected guide channel 21 can be varied and can be flexibly set according to actual needs.

[0107] In some embodiments, as shown in Figures 5a, 5b, and 6, the outlet hole 12 is located at the center of the rotating shaft 1. A guide channel 21 covers the outlet hole 12 along its axial direction. For example, referring to Figures 5a and 10a, or Figures 5b and 10b, the guide channel 21 has an inlet 211. Along the axial direction of the outlet hole 12, the area of ​​the inlet 211 is larger than the area of ​​the outlet hole 12, and the outlet hole 12 is located within the area enclosed by the inlet 211. In this case, the location of the outlet hole 12 coincides with the location of the guide structure 2.

[0108] In this way, the cooling medium flowing out of the liquid outlet 12 can directly flow into the corresponding guide channel 21.

[0109] By adopting the above configuration, the flow path of the cooling medium from the outlet hole 12 to the corresponding guide groove 21 can be shortened, and the resistance encountered by the cooling medium when flowing between the outlet hole 12 and the guide groove 21 can be reduced.

[0110] In some embodiments, as shown in Figures 11 and 12, the position of the liquid outlet 12 is offset from the center of the rotating shaft 1. Along the axial direction of the rotating shaft 1, the liquid outlet 12 and the flow guide structure 2 are offset, with a certain distance between them. Correspondingly, the liquid outlet 12 is offset relative to the flow guide structure 2. For example, as shown in Figure 11, along the axial direction of the rotating shaft 1, the liquid outlet 12 can be located on the right side of the flow guide structure 2; of course, the liquid outlet 12 can also be located on the left side of the flow guide structure 2.

[0111] Based on this, the area occupied by the liquid outlet 12 is covered by multiple rotor laminations 3. Referring to Figures 11 and 13, along the axial direction of the rotating shaft 1, a groove 33 is formed on the inner circumferential surface of the rotor laminations 3 located between the liquid outlet 12 and the flow guiding structure 2. This groove 33 connects the flow guiding groove 21 and the liquid outlet 12. The number of rotor laminations 3 located between the liquid outlet 12 and the flow guiding structure 2 can be selected and set according to actual needs.

[0112] For example, when the outlet hole 12 is located on the contact surface between two adjacent rotor laminations 3, the groove 33 extends through each rotor lamination 3 located between the outlet hole 12 and the flow guide structure 2 along the axial direction of the shaft 1. Alternatively, when the outlet hole 12 is covered by a rotor lamination 3, the groove 33 extends through the portion of the rotor lamination 3 located between the outlet hole 12 and the flow guide structure 2; furthermore, it can extend through other rotor laminations 3 located between the rotor lamination 3 and the flow guide structure 2.

[0113] Referring again to Figure 11, a connecting channel is formed between the groove 33 and the outer peripheral wall of the rotating shaft 1, connecting the guide groove 21 and the liquid outlet 12. After the cooling medium flows out of the liquid outlet 12, it can flow into the connecting channel, then into the guide groove 21, and then into the first cooling channel D1 connected to it.

[0114] By adopting the above-mentioned arrangement, the liquid outlet 12 is flexibly arranged in the axial direction of the rotating shaft 1, which enhances the flexibility of the rotor 320 and the motor 300 used therein.

[0115] In the aforementioned flow guiding structure 2 and multiple rotor laminations 3, there are various ways to arrange the flow guiding groove 21 and the cooling gap 32, which can be selected according to actual needs.

[0116] In some embodiments, as shown in Figures 8a-9b, each rotor lamination 3 has multiple magnet slots 31, which are spaced apart circumferentially along the rotor lamination 3. For example, each magnet slot 31 contains a permanent magnet 4, and correspondingly, the multiple magnet slots 31 in each rotor lamination 3 form multiple cooling gaps 32. Multiple first cooling channels D1 are formed in the multiple rotor laminations 3 located on the same side of the flow guiding structure 2, and these multiple first cooling channels D1 correspond one-to-one with the multiple magnet slots 31 in the same rotor lamination 3.

[0117] Furthermore, the flow guiding structure 2 is provided with a plurality of flow guiding grooves 21, which are distributed at intervals along the circumference of the flow guiding structure 2. As shown in Figures 10a and 10b, along the axial direction of the rotating shaft 1, in adjacent flow guiding structures 2 and rotor laminations 3, each flow guiding groove 21 overlaps with at least one cooling gap 32. That is, each flow guiding groove 21 covers at least a portion of each of the at least one cooling gap 32 and communicates with it. Correspondingly, each flow guiding groove 21 communicates with at least one first cooling channel D1 located on the same side of the flow guiding structure 2.

[0118] For example, along the axial direction of the rotating shaft 1, multiple guide grooves 21 and multiple cooling gaps 32 can be arranged one-to-one in adjacent guide structures 2 and rotor laminations 3. That is, each guide groove 21 is connected to a first cooling channel D1 located on the same side of the guide structure 2.

[0119] For example, as shown in Figures 10a and 10b, in adjacent flow guiding structures 2 and rotor laminations 3, each flow guiding groove 21 covers at least a portion of each of at least two cooling gaps 32. That is, each flow guiding groove 21 is connected to at least two first cooling channels D1 located on the same side of the flow guiding structure 2. The number of flow guiding grooves 21 is less than the number of magnet grooves 31 (or cooling gaps 32, first cooling channels D1).

[0120] In this way, after the cooling medium enters the guide groove 21, it can directly contact the end face of the rotor lamination 3 and flow smoothly into the cooling gap 32 formed in the rotor lamination 3, reducing the resistance encountered by the cooling medium when flowing inside the rotor 320. Here, the end face of the rotor lamination 3 refers to the side end face of the rotor lamination 3 adjacent to the guide structure 2 that is used to contact the guide structure 2.

[0121] Furthermore, in adjacent flow guiding structures 2 and rotor laminations 3, when each flow guiding groove 21 overlaps with at least two cooling gaps 32, the number of flow guiding grooves 21 in the flow guiding structure 2 can be reduced. This avoids affecting the structural strength of the flow guiding structure 2 and allows the flow guiding grooves 21 to have a larger size. This is beneficial for reducing the resistance encountered by the cooling medium when flowing in the flow guiding grooves 21, and also for increasing the contact area between the cooling medium and the end face of the rotor laminations 3, thereby improving the heat dissipation effect on the rotor laminations 3 and the rotor 320.

[0122] In some examples, as shown in Figures 8a and 8b, the multiple magnet slots 31 in the rotor lamination 3 can be divided into multiple magnet slot units 31a, each magnet slot unit 31a including at least two magnet slots 31. Optionally, the number of magnet slot units 31a includes, but is not limited to, three, four, five, six, seven, etc., and the number of magnet slots 31 included in each magnet slot unit 31a can be two, three, four, etc., which can be selected and set according to actual design needs. For example, if the number of magnet slots 31 included in each magnet slot unit 31a is even, then at least two magnet slots 31 in the magnet slot unit 31a can be symmetrically arranged about the direct axis (also known as the d-axis).

[0123] Furthermore, the plurality of magnet slot units 31a in the rotor lamination 3 are distributed at intervals along the circumference of the rotor lamination 3. For example, these plurality of magnet slot units 31a are periodically and uniformly distributed along the circumference of the rotor lamination 3. Exemplarily, the rotor lamination 3 may have an axisymmetric structure, with the extension direction of the axis of symmetry perpendicular to the axial direction of the rotating shaft 1. Alternatively, the rotor lamination 3 may also have a rotationally symmetric structure, with the center of rotation being the axis of the rotating shaft 1, and the minimum rotation angle being, for example, 360° / N, where N is the number of magnet slot units 31a.

[0124] Referring to Figures 8a and 10a, or Figures 8b and 10b, along the axial direction of the rotating shaft 1, in adjacent guide structures 2 and rotor laminations 3, each guide groove 21 overlaps with at least two cooling gaps 32 in the magnet slot unit 31a. Each guide groove 21 may correspond to one or more magnet slot units 31a, and each guide groove 21 overlaps with the cooling gaps 32 in its corresponding magnet slot unit 31a. Each guide groove 21 is connected to the first cooling channel D1 formed by its corresponding magnet slot unit 31a. For example, the number of magnet slot units 31a corresponding to each guide groove 21 is the same.

[0125] For example, as shown in Figures 10a and 10b, the guide channel 21 is strip-shaped, and each guide channel 21 is correspondingly arranged with one magnetic steel channel unit 31a. The magnetic steel channels 31 of the same pole are connected through the guide channel 21. As another example, the guide channel 21 is Y-shaped, and each guide channel 21 is correspondingly arranged with two magnetic steel channel units 31a.

[0126] This helps to improve the uniformity of the flow distribution of the cooling medium in each guide channel 21 and its connected first cooling channel D1, helps to improve the problem of local hot spots in the permanent magnet 4, and improves the power performance and service life of the drive motor 300 or generator used in the rotor 320, as well as the safety of the vehicle.

[0127] In some examples, as shown in Figures 8a and 8b, in the magnet slot unit 31a, two magnet slots 31 symmetrical about the direct axis form a V-groove structure 31b. Along the direction from the inner circumferential surface of the rotor lamination 3 to the outer circumferential surface, the spacing between the two magnet slots 31 in the V-groove structure 31b gradually increases in the circumferential direction of the rotating shaft 1. Referring further to Figures 10a and 10b, in adjacent flow guiding structures 2 and rotor laminations 3, along the circumferential direction of the rotating shaft 1, the dimension S2 of the flow guiding groove 21 is greater than the minimum spacing S1 between the two magnet slots 31 in the V-groove structure 31b.

[0128] For example, the magnet slot unit 31a may include one V-groove structure 31b, or it may include multiple V-groove structures 31b, which are arranged sequentially along the radial direction of the rotating shaft 1. Each magnet slot unit 31a may include the same number of V-groove structures 31b. For example, Figure 8b shows that each magnet slot unit 31a includes two V-groove structures 31b.

[0129] When the magnet groove unit 31a includes multiple V-groove structures 31b, the dimension S2 of the position where the guide groove 21 and each V-groove structure 31b overlap in the circumferential direction of the rotation axis is greater than the minimum spacing S1 of the two magnet grooves 31 in the V-groove structure 31b in the circumferential direction of the rotation axis.

[0130] At this point, the adjacent ends of the two magnetic grooves 31 in each V-groove structure 31b can overlap with the guide groove 21, so that the guide groove 21 and the cooling gap 32 formed by each magnetic groove 31 in the V-groove structure 31b are connected, realizing the connection of cooling paths between different layers of magnetic grooves 31, and enhancing the heat dissipation and temperature uniformity. Based on this, the circumferential dimensions of the guide groove 21 on the rotating shaft 1 can be adjusted to ensure the structural strength of the guide structure 2 and meet the flow distribution requirements of the cooling medium.

[0131] In some examples, as shown in Figures 7a and 7b, multiple guide channels 21 in the guide structure 2 are uniformly distributed along the circumference of the rotation axis 1. Alternatively, the multiple guide channels 21 in the guide structure 2 may have the same shape and size. Furthermore, the multiple guide channels 21 in the guide structure 2 can form a rotationally symmetric structure, with the rotation center of this rotational symmetry being the axis of the rotation axis 1. That is, these multiple guide channels 21 are rotationally symmetric about the axis of the rotation axis 1. The minimum rotation angle is, for example, 360° / N, where N is the number of guide channels 21.

[0132] In this way, on the one hand, it helps to reduce the processing difficulty of the flow guiding structure 2; on the other hand, it can improve the uniformity of the flow distribution of the cooling medium in different flow guiding grooves 21, and uniformly cool and dissipate heat to the permanent magnet 4 at different locations, effectively improving the local hot spot problem of the permanent magnet 4.

[0133] Here, the shape of the guide channel 21 can be adjusted according to the correspondence between the guide channel 21 and the magnet channel 31, and the fit between the guide channel 21 and the rotating shaft 1. For example, the shape of the guide channel 21 includes, but is not limited to, strip, Y-shaped, T-shaped, etc.

[0134] In the rotor lamination 3 mentioned above, there are multiple ways to set the cooling gap 32, which can be selected according to actual needs.

[0135] In some embodiments, as shown in Figures 8a and 8b, the magnetic steel groove 31 includes a magnetic steel receiving section 311 and a magnetic isolation section 312 that are connected to each other. The number of magnetic isolation sections 312 can be one or two. For example, one magnetic isolation section 312 may be connected to the end of the magnetic steel receiving section 311 near the rotating shaft 1, or it may be connected to the end of the magnetic steel receiving section 311 away from the rotating shaft 1. Optionally, all magnetic isolation sections 312 may be connected to the end of the magnetic steel receiving section 311 near the rotating shaft 1. As shown in Figures 8a and 8b, two magnetic isolation sections 312 may be connected to the two ends of the magnetic steel receiving section 311, respectively.

[0136] The aforementioned magnet accommodating section 311 is used to accommodate the permanent magnet 4. Accordingly, referring to Figures 8a and 9a, or Figures 8b and 9b, the permanent magnet 4 is located within the magnet accommodating section 311. The magnetic shielding section 312 is empty, and no permanent magnet 4 is disposed inside it. In this case, the cooling gap 32 may include the magnetic shielding section 312.

[0137] As shown in Figures 10a and 10b, along the axial direction of the rotating shaft 1, in adjacent flow guiding structures 2 and rotor laminations 3, each flow guiding groove 21 can, for example, cover at least one magnetic shielding section 312 of a magnet groove 31, and correspondingly communicate with this at least one magnetic shielding section 312 of the magnet groove 31. In this way, each flow guiding groove 21 can be connected to the corresponding cooling gap 32 through the magnetic shielding section 312 it covers, and further connected to the corresponding first cooling channel D1.

[0138] For example, each magnetic steel groove 31 includes two magnetic shielding sections 312, each guide groove 21 covers two adjacent magnetic shielding sections 312 in the same V-shaped groove structure 31b, and is connected to the corresponding cooling gap 32 and the first cooling channel D1 through these two magnetic shielding sections 312.

[0139] By reusing the magnetic isolation section 312 included in the magnet slot 31 itself as the cooling gap 32, it is not necessary to open additional cooling channels in the rotor lamination 3, thus avoiding significant changes to the structure of the rotor lamination 3. In this way, on the one hand, the original structural strength and magnetic conductivity of the rotor lamination 3 can be guaranteed; on the other hand, it can avoid increasing mold costs and production costs, and enhance universality.

[0140] In some examples, in the aforementioned magnet groove 31, the permanent magnet 4 can be fixed within the magnet groove 311 by means of bonding with potting compound. Alternatively, the magnet groove 311 and the permanent magnet 4 can be spaced apart, allowing the permanent magnet 4 to be fixed within the magnet groove 311 by other methods.

[0141] For example, as shown in Figure 14(b), a plurality of spring-loaded protrusions 3111 are provided on the inner wall of the magnet receiving section 311, and these protrusions 3111 are spaced apart. For example, these protrusions 3111 can be formed on the inner wall of the magnet receiving section 311 using a spring-loaded process. After the permanent magnet 4 is installed in the magnet receiving section 311, the protrusions 3111 can undergo elastic deformation, thereby fixing the permanent magnet 4 in the magnet receiving section 311. In addition, these protrusions 3111 can also separate the inner wall of the magnet receiving section 311 and the permanent magnet 4 to form a gap 3112 between the inner wall of the magnet receiving section 311 and the permanent magnet 4. Figure 14(b) is a partially enlarged structural view of the magnet groove 31 located in region Q of the rotor lamination 3 shown in Figure 14(a).

[0142] Furthermore, as shown in Figure 14(a), the aforementioned gap 3112 and the magnetic shielding section 312 are connected, and the cooling gap 32 may also include the gap 3112. That is, the cooling gap 32 can be composed of the gap 3112 and the magnetic shielding section 312. For example, as shown in Figure 14(a), any position on the inner wall of the magnetic steel groove 31 is basically not in direct contact with the permanent magnet 4, the cooling gap 32 surrounds the permanent magnet 4, and the first cooling channel D1 formed by connecting multiple cooling gaps 32 in sequence surrounds the corresponding multiple permanent magnets 4.

[0143] In this way, the cooling medium flowing into the cooling gap 32 or the first cooling channel D1 can basically surround the permanent magnet 4 and directly contact various positions of the permanent magnet 4 and the inner wall of the magnetic steel groove 31, directly cooling and dissipating heat at different positions of the permanent magnet 4 and the magnetic steel groove 31. That is to say, by setting the spring-loaded protrusion 3111, the contact area between the permanent magnet 4 and the magnetic steel groove 31 can be reduced, and the contact area between the cooling medium and the permanent magnet 4 and the rotor lamination 3 can be increased, which greatly improves the heat dissipation effect on the permanent magnet 4 and the rotor lamination 3, greatly improves the problem of overheating of the permanent magnet 4 during the rotation of the rotor 320, and can effectively improve and eliminate the problem of local hot spots in the permanent magnet 4, effectively improving the power performance and service life of the drive motor 300 or generator used in the rotor 320, as well as the safety of the vehicle.

[0144] For example, the aforementioned multiple spring-loaded protrusions 3111 are arranged in an array and are relatively evenly distributed on the inner wall of the magnet accommodating section 311. For instance, in Figure 14(b), the multiple spring-loaded protrusions 3111 on each inner wall of the magnet accommodating section 311 are arranged in two rows and multiple columns. The number, size, etc. of the spring-loaded protrusions 3111 can be selected and set according to actual needs.

[0145] This helps to improve the uniformity of the pressure borne by the permanent magnet 4 at different positions, and improve the uniformity of the distance (i.e. the size of the gap 3112) between the permanent magnet 4 and the inner wall of the magnet housing section 311, so that the resistance encountered by the cooling medium when flowing at different positions of the gap 3112 is more uniform, thereby improving the heat dissipation effect.

[0146] Optionally, when a spring-loaded protrusion 3111 is provided on the inner wall of the magnet accommodating section 311, as shown in FIG10b, along the axial direction of the rotating shaft 1, in adjacent flow guiding structures 2 and rotor laminations 3, each flow guiding groove 21 can, for example, cover the magnetic shielding section 312 of at least one magnet groove 31 and be offset from the gap 3112 in this at least one magnet groove 31. In this case, each flow guiding groove 21 can be connected to the gap 3112 through the magnetic shielding section 312 it covers, realizing the connection between the flow guiding groove 21 and the cooling gap 32, and thus realizing the connection between the flow guiding groove 21 and the first cooling channel D1.

[0147] This reduces the size of the guide groove 21 around the rotating shaft 1, ensuring the structural strength of the guide structure 2.

[0148] Other structures can also be provided in the rotor lamination 3 described above, which will be illustrated below with reference to the accompanying drawings.

[0149] In some embodiments, as shown in FIG14(a), a first de-weighting hole 34 is provided on the rotor lamination 3, and the first de-weighting hole 34 penetrates the rotor lamination 3 along the axial direction of the rotating shaft 1. The first de-weighting hole 34 is spaced apart from the inner circumferential surface of the rotor lamination 3 and from the magnet slot 31. The number of first de-weighting holes 34 can be one or more. When there are multiple first de-weighting holes 34, the multiple first de-weighting holes 34 can be distributed at intervals along the circumference of the rotating shaft 1. The multiple first de-weighting holes 34 can be arranged in one layer along the circumference of the rotating shaft 1, or, as shown in FIG14(a), can be arranged in two layers. Of course, they can also be arranged in more layers.

[0150] For example, referring to Figures 8b and 14(a), one or more first de-weighting holes 34 can be provided between two adjacent magnetic steel slot units 31a. For example, the first de-weighting hole 34 can be a straight through hole or a spiral opening. Along the axial direction of the rotating shaft 1, the cross-sectional shape of the first de-weighting hole 34 can be any shape and combination of shapes, such as a circular hole, an elliptical hole, a rhomboid hole, or an oblong hole.

[0151] By setting the first weight-reduction hole 34, on the one hand, the weight of the rotor lamination 3 can be reduced, the moment of inertia of the rotor 320 during rotation can be reduced, the influence of inertia on the rotor 320 can be reduced, and the stability of the rotor 320 during deceleration can be improved; on the other hand, it is beneficial to reduce the stress at the location of the first weight-reduction hole 34.

[0152] The positional relationship between the first deweighting hole 34 and the guide groove 21 can be varied. In some examples, as shown in Figure 15, the first deweighting hole 34 and the guide groove 21 are staggered. Along the axial direction of the rotating shaft 1, the guide structure 2 covers the first deweighting hole 34 on the adjacent rotor lamination 3. There is no connection between the first deweighting hole 34 and the guide groove 21.

[0153] This prevents the cooling medium from accidentally flowing into the first weight removal hole 34, which could have an adverse effect on the rotation of the rotor 320.

[0154] In other examples, as shown in Figure 16, the first de-weighting holes 34 on multiple rotor laminations 3 located on the same side of the flow guide structure 2 are sequentially connected to form a second cooling channel D2. In the axial direction of the rotating shaft 1, the sequentially connected first de-weighting holes 34 overlap or intersect.

[0155] For example, when multiple first de-weighting holes 34 are provided on the rotor lamination 3, the multiple first de-weighting holes 34 are connected one-to-one in two adjacent rotor laminations 3 located on the same side of the flow guiding structure 2. In this case, in Figure 16, multiple second cooling channels D2 can be formed in the multiple rotor laminations 3 located on the left side of the flow guiding structure 2; multiple second cooling channels D2 can also be formed in the multiple rotor laminations 3 located on the right side of the flow guiding structure 2.

[0156] Referring to Figures 16 and 17, the guide channel 21 is also connected to the second cooling channel D2. When multiple second cooling channels D2 are provided on the same side of the guide structure 2, each guide channel 21 can be connected to one, two, or even more second cooling channels D2. For example, each guide channel 21 is connected to two second cooling channels D2 located on the same side of the guide structure 2.

[0157] During the operation of the rotor 320 or motor 300, the cooling medium in the guide groove 21 flows not only into the first cooling channel D1, but also into the second cooling channels D2 located on both sides of the guide groove 21. The second cooling channels D2 located on both sides of the guide structure 2 and connected to the same guide groove 21 can form parallel cooling channels; the second cooling channel D2 and the first cooling channel D1 located on the same side of the guide structure 2 and connected to the same guide groove 21 can also form parallel cooling channels. Each second cooling channel D2 only penetrates multiple rotor laminations 3 located on the same side of the guide structure 2, and the length of the second cooling channel D2 on the same side of the guide structure 2 is basically the same as the length of the first cooling channel D1. The flow distribution of the cooling medium at different positions in the rotor 320 is relatively even.

[0158] By reusing the multiple first de-weighting holes 34 connected in sequence as the second cooling channel D2, on the one hand, the contact area between the cooling medium and the rotor lamination 3 can be increased, greatly improving the heat dissipation effect on the rotor lamination 3, and thus improving the heat dissipation effect on the rotor 320; on the other hand, it can avoid changing the structure of the rotor lamination 3, ensure the structural strength of the rotor lamination 3, avoid increasing mold costs and production costs, and enhance universality.

[0159] In some examples, as shown in Figure 17, along the axial direction of the shaft 1, in adjacent guide structures 2 and rotor laminations 3, each guide groove 21 overlaps with at least one first de-weighting hole 34. For example, each guide groove 21 covers at least one adjacent first de-weighting hole 34 to achieve communication.

[0160] In this way, the cooling medium in the guide groove 21 can directly contact the end face of the rotor lamination 3 and flow into the first weight-removing hole 34 formed in the rotor lamination 3 more smoothly, reducing the resistance encountered by the cooling medium when it flows inside the rotor 320.

[0161] Furthermore, when each guide groove 21 overlaps with at least two first de-weighting holes 34, the number of guide grooves 21 in the guide structure 2 can be reduced. This avoids affecting the structural strength of the guide structure 2 and allows the guide grooves 21 to have a larger size. This is beneficial for reducing the resistance encountered by the cooling medium when it flows in the guide groove 21, and also for increasing the contact area between the cooling medium and the end face of the rotor lamination 3, thereby improving the heat dissipation effect on the rotor lamination 3 and the rotor 320.

[0162] Optionally, along the circumference of the rotating shaft 1, adjacent magnetic steel groove units 31a and the first weight removal hole 34 can be connected to the same guide groove 21. This helps to further reduce the number of guide grooves 21, ensure the structural strength of the guide structure 2, and reduce the resistance encountered by the cooling medium when it flows in the guide groove 21.

[0163] There are several ways to set up the above-mentioned flow guiding structure 2, which are illustrated below with reference to the attached drawings.

[0164] In some embodiments, as shown in Figures 15 and 17, a second deweighting hole 22 is provided in the flow guiding structure 2, and the second deweighting hole 22 penetrates the flow guiding structure 2 along the axial direction of the rotating shaft 1. The second deweighting hole 22 and the flow guiding groove 21 are spaced apart, that is, there is no communication between the second deweighting hole 22 and the flow guiding groove 21. Furthermore, the second deweighting hole 22 and the inner circumferential surface of the flow guiding structure 2 can also be spaced apart.

[0165] For example, the second de-weighting hole 22 can be a straight through hole or a spiral opening. Along the axial direction of the rotating shaft 1, the cross-sectional shape of the second de-weighting hole 22 can be any shape or combination of shapes, such as a round hole, an elliptical hole, a rhomboid hole, or an oblong hole.

[0166] By setting the second de-weighting hole 22, on the one hand, the weight of the flow guiding structure 2 can be reduced, the moment of inertia of the rotor 320 during rotation can be reduced, the influence of inertia on the rotor 320 can be reduced, and the stability of the rotor 320 during deceleration can be improved; on the other hand, it is beneficial to reduce the stress at the location of the second de-weighting hole 22.

[0167] The number of the aforementioned second de-weighting holes 22 can be one or more. As shown in Figures 15 and 17, when multiple guide grooves 21 and multiple second de-weighting holes 22 are provided on the flow guiding structure 2, the guide grooves 21 and the second de-weighting holes 22 are alternately arranged along the circumference of the rotating shaft 1.

[0168] For example, the number of guide grooves 21 and the number of second de-weight holes 22 are the same. Along the circumference of the rotating shaft 1, there is a second de-weight hole 22 between every two adjacent guide grooves 21, and there is a guide groove 21 between every two adjacent second de-weight holes 22.

[0169] This balances the structural strength at different locations of the flow guide structure 2, thereby reducing its weight and ensuring good structural stability.

[0170] For example, the multiple second de-weighting holes 22 can have the same shape and size. For instance, as shown in Figures 15 and 17, the multiple second de-weighting holes 22 can form a rotationally symmetric structure, with the rotation center of this structure being the axis of the rotating shaft 1. That is, the multiple second de-weighting holes 22 are distributed rotationally symmetrically about the axis of the rotating shaft 1. The minimum rotation angle is, for example, 360° / N, where N is the number of second de-weighting holes 22. Furthermore, the flow guiding structure 2 as a whole can form a rotationally symmetric structure, with the rotation center of this structure being the axis of the rotating shaft 1.

[0171] This can further balance the structural strength of the flow guide structure 2 at different locations, and ensure that the flow guide structure 2 has good structural stability while reducing its weight.

[0172] In some embodiments, the material of the flow guiding structure 2 includes, but is not limited to, plastic, non-magnetic metal, or magnetic metal.

[0173] In some examples, the material of the flow guiding structure 2 includes plastic or non-magnetic metal. In this case, the flow guiding structure 2 can have a large thickness, and the flow guiding structure 2 can also be called a flow guide plate.

[0174] This helps to simplify the structure of rotor 320 and reduce its cost.

[0175] In other examples, the material of the flow guiding structure 2 includes magnetically conductive metals, etc. In this case, as shown in Figure 18, the flow guiding structure 2 may include flow guiding blades 2a, which may be silicon steel sheets, silicon steel sheets, etc. The thickness of the flow guiding blades 2a is relatively small. To ensure the flow guiding effect of the flow guiding structure 2 on the cooling medium, the flow guiding structure 2 may include multiple flow guiding blades 2a, which may be stacked along the axial direction of the rotating shaft 1.

[0176] This helps to ensure the magnetic conductivity of the flow guiding structure 2, increase the structural strength of the flow guiding structure 2, and avoid affecting the normal operation of the rotor 320.

[0177] For example, when the flow guiding structure 2 includes multiple flow guiding tabs 2a, the structures of these multiple flow guiding tabs 2a may be the same or different.

[0178] Optionally, the aforementioned multiple guide vanes 2a have identical structures. In this case, these multiple guide vanes 2a overlap along the axial direction of the rotating shaft 1. Further, guide vanes 2a are provided with guide sub-grooves 21a, which penetrate through the guide vanes 2a along the axial direction of the rotating shaft 1, and the guide sub-grooves 21a on adjacent guide vanes 2a overlap. The multiple guide sub-grooves 21a connected sequentially in the multiple guide vanes 2a constitute a guide groove 21.

[0179] This can reduce mold and production costs, and also avoid increasing the resistance encountered by the cooling medium when it flows in the guide channel 21.

[0180] Optionally, the structures of the aforementioned multiple guide laminations 2a may differ. In this case, as shown in Figure 18, a guide sub-groove 21a is formed on the guide lamination 2a, and the guide sub-groove 21a extends through the guide lamination 2a along the axial direction of the rotating shaft 1. Specifically, along the stacking direction of the guide structure 2 and the rotor lamination 3, the maximum distance between the guide sub-groove 21a on at least two adjacent guide laminations 2a and the rotating shaft 1 gradually increases.

[0181] For example, as shown in Figure 18, the flow guiding structure 2 includes five flow guiding plates (2a-1, 2a-2, 2a-3, 2a-4, and 2a-5, respectively), which are stacked sequentially along the axial direction of the rotating shaft 1. Among them, the maximum distance between the flow guiding sub-groove 21a of flow guiding plate 2a-3 and the rotating shaft 1 is the smallest. Along the direction from flow guiding plate 2a-3 to flow guiding plate 2a-1, the maximum distance between the flow guiding sub-groove 21a of flow guiding plates 2a-3, 2a-2, and 2a-1 and the rotating shaft 1 gradually increases; along the direction from flow guiding plate 2a-3 to flow guiding plate 2a-5, the maximum distance between the flow guiding sub-groove 21a of flow guiding plates 2a-3, 2a-4, and 2a-5 and the rotating shaft 1 gradually increases. Multiple guide sub-grooves 21a connected in sequence in multiple guide laminations 2a constitute a stepped distribution of guide grooves 21.

[0182] In some examples, as shown in Figures 7a and 7b, a mounting key 23 is provided on the inner circumferential surface of the flow guide structure 2. This mounting key 23 is used to fix the flow guide structure 2 to the rotating shaft 1. Further, as shown in Figure 10b, a mounting groove 13 is also provided on the outer circumferential wall of the rotating shaft 1. The mounting groove 13 is recessed from the outer circumferential wall of the rotating shaft 1 into the interior of the rotating shaft 1 and does not connect to the liquid storage chamber 11. The mounting key 23 extends into the mounting groove 13 to achieve the fixation between the flow guide structure 2 and the rotating shaft 1.

[0183] For example, there can be multiple mounting keys 23, and correspondingly, there can be multiple mounting slots 13, the same number as the number of mounting keys 23. For example, in Figure 10b, there are two mounting keys 23 and two mounting slots 13.

[0184] Referring to Figures 7a and 7b, the mounting key 23 and the guide groove 21 in the flow guiding structure 2 are spaced apart and are not connected.

[0185] This avoids affecting the transmission of the cooling medium and the normal operation of the rotor 320 and motor 300.

[0186] In some embodiments, the rotor 320 may also include other structures. As shown in Figures 11 and 16, the rotor 320 may also include end plates 5, with the flow guiding structure 2 and a plurality of rotor laminations 3 located between the two end plates 5. As shown in Figure 11, flow channels are provided in the end plates 5, and the cooling medium flowing out from the first cooling channel D1 and / or the second cooling channel D2 can flow into the flow channels and then exit the rotor 320.

[0187] Since the first cooling channel D1 is formed by a plurality of sequentially connected cooling gaps 32, and the cooling gaps 32 are formed within the magnet slot 31, the first cooling channel D1 extends substantially along the axial direction of the rotating shaft 1. Since the second cooling channel D2 is formed by a plurality of sequentially connected first weight-removing holes 34, the second cooling channel D2 also extends substantially along the axial direction of the rotating shaft 1. That is, the first cooling channel D1 and the second cooling channel D2 do not need to rotate. Accordingly, as shown in Figures 5a and 5b, the rotor 320 in this embodiment can also omit the end plate, and the cooling medium flows through the first cooling channel D1 and / or the second cooling channel D2 before being directly discharged from the rotor 320. This simplifies the structure of the rotor 320 and reduces the cost of the rotor 320 and the motor 300 used in it.

[0188] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions conceived by those skilled in the art within the scope of the technology disclosed herein should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A rotor, characterized in that, The rotor includes: A rotating shaft has a liquid storage cavity; an outlet hole communicating with the liquid storage cavity is provided on the outer peripheral wall of the rotating shaft; A flow guiding structure is sleeved on the rotating shaft; the flow guiding structure has a flow guiding groove, which is connected to the liquid outlet hole; Multiple rotor laminations are sleeved on the rotating shaft and located on both sides of the flow guiding structure; each rotor lamination has a magnetic groove. A permanent magnet is located inside the magnetic steel groove; a cooling gap is formed between the permanent magnet and the inner wall of the magnetic steel groove, and the cooling gaps on multiple rotor laminations located on the same side of the flow guiding structure are connected in sequence to form a first cooling channel; the first cooling channel is connected to the flow guiding groove.

2. The rotor according to claim 1, characterized in that, Each rotor lamination has multiple magnet slots, which are spaced apart along the circumference of the rotor lamination. The flow guiding structure has multiple flow guiding grooves, which are distributed at intervals along the circumference of the flow guiding structure. Along the axial direction of the shaft, in adjacent flow guide structures and rotor laminations, each flow guide groove overlaps with at least one cooling gap.

3. The rotor according to claim 2, characterized in that, The plurality of magnetic slots are divided into a plurality of magnetic slot units, which are distributed circumferentially along the rotor laminations. Each magnetic slot unit includes at least two magnetic slots that are symmetrical about a direct axis. Along the axial direction of the rotating shaft, in adjacent flow guiding structures and rotor laminations, each flow guiding groove overlaps with at least two cooling gaps in the magnet slot unit.

4. The rotor according to claim 3, characterized in that, The two magnetic grooves, symmetrical about the right axis, form a V-shaped groove structure; Along the circumference of the rotating shaft, the size of the guide groove is greater than the minimum distance between the two magnetic grooves in the V-groove structure.

5. The rotor according to any one of claims 2-4, characterized in that, The multiple guide channels form a rotationally symmetric structure, and the rotation center of the rotationally symmetric structure is the axis of the rotating shaft.

6. The rotor according to any one of claims 1-5, characterized in that, The magnetic steel groove includes a magnetic steel receiving section and a magnetic isolation section that are connected to each other, and the permanent magnet is located in the magnetic steel receiving section; The cooling gap includes the magnetic shielding section.

7. The rotor according to claim 6, characterized in that, The inner wall of the magnet receiving section is provided with multiple spring-loaded protrusions, which separate the inner wall of the magnet receiving section from the permanent magnet to form a gap between the inner wall of the magnet receiving section and the permanent magnet. The gap is connected to the magnetic isolation section. The cooling gap also includes the slit.

8. The rotor according to any one of claims 1-7, characterized in that, The rotor lamination is provided with a first de-weighting hole; Along the axial direction of the rotating shaft, the flow guiding structure covers the first de-weighting hole on the adjacent rotor lamination.

9. The rotor according to any one of claims 1-7, characterized in that, The rotor lamination has a first de-weighting hole, and the first de-weighting holes on multiple rotor laminations located on the same side of the flow guiding structure are connected in sequence to form a second cooling channel. The guide channel is also connected to the second cooling channel.

10. The rotor according to claim 9, characterized in that, Along the axial direction of the rotating shaft, in adjacent flow guiding structures and rotor laminations, each flow guiding groove overlaps with at least one of the first weight-removing holes.

11. The rotor according to any one of claims 1-10, characterized in that, Along the axial direction of the liquid outlet, the guide groove covers the liquid outlet.

12. The rotor according to any one of claims 1-10, characterized in that, Along the axial direction of the rotating shaft, the liquid outlet and the flow guiding structure are staggered. A groove is formed on the inner circumferential surface of the rotor lamination located between the liquid outlet and the flow guiding structure. The groove connects the flow guiding groove and the liquid outlet.

13. The rotor according to any one of claims 1-12, characterized in that, The flow guiding structure is a flow guide plate; or, The flow guiding structure includes multiple flow guiding blades, which are stacked along the axial direction of the rotating shaft.

14. The rotor according to any one of claims 1-13, characterized in that, The flow guiding structure has a second de-weighting hole, and the second de-weighting hole and the flow guiding groove are spaced apart.

15. The rotor according to claim 14, characterized in that, The flow guiding structure is provided with a plurality of flow guiding grooves and a plurality of second de-weighting holes, and the flow guiding grooves and second de-weighting holes are alternately arranged along the circumference of the rotating shaft.

16. The rotor according to any one of claims 1-15, characterized in that, An installation groove is provided on the outer peripheral wall of the rotating shaft, and an installation key is provided on the inner peripheral surface of the flow guiding structure, the installation key extending into the installation groove; The installation key and the flow guide groove are spaced apart.

17. An electric motor, characterized in that, The motor includes: The rotor as described in any one of claims 1-16; A stator is mounted on the rotor; the rotor is capable of rotating relative to the stator.

18. A powertrain, characterized in that, The powertrain includes: The motor as described in claim 17; The transmission is connected to the motor.

19. A vehicle, characterized in that, The vehicles include: The powertrain as described in claim 18; The transmission mechanism is connected to the powertrain; The wheels are connected to the transmission mechanism; the powertrain drives the wheels through the transmission structure.

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