Electromagnetic clutch and vehicle

Abstract

The invention discloses an electromagnetic clutch and a vehicle. The electromagnetic clutch comprises a driving wheel; the movable fluted disc is fixed to the driving wheel in the circumferential direction and can be movably arranged in the axis direction of the driving wheel. The driving unit comprises an electromagnetic coil and an elastic piece; the at least two driven wheels are arranged at intervals along the axis direction of the driving wheel; when the electromagnetic coil is powered on, one-way electromagnetic force is generated, the movable fluted disc is driven to move in the first direction in the axial direction, and the movable fluted disc is made to be meshed with the first driven wheel in the at least two driven wheels and separated from the second driven wheel. When the electromagnetic coil is powered off, the elastic piece provides return force opposite to the first direction to drive the movable fluted disc to move in the second direction in the axial direction, so that the movable fluted disc is meshed with the second driven wheel and separated from the first driven wheel. Double-gear switching is controlled through power-on and power-off of a single driving source, the driving and control structure is greatly simplified, control is easy, and the manufacturing cost is low.

Description

Technical Field

[0001] This application belongs to the field of clutch technology, and particularly relates to an electromagnetic clutch and a vehicle. Background Technology

[0002] In the field of mechanical transmission (such as vehicles, machine tools, etc.), clutches are often used to achieve power switching between multiple gears or positions to adapt to different working conditions. Existing dual-gear switching solutions mainly rely on two types of structures: one is the synchronizer shifting mechanism, which requires complex accessories such as shift forks, shift hubs, and shift motors. Not only is the overall axial dimension large, making it difficult to adapt to compact spaces such as wheel-side reducers, but the control logic is also cumbersome and the cost is high. The other type is the multi-coil electromagnetic clutch, which uses at least two coils to control the clutch action of different gears. Although it eliminates the synchronizer accessory, the stacked arrangement of multiple coils still results in a large axial space occupation, and the design of independent power supply and control for dual coils further increases the cost and failure risk. Summary of the Invention

[0003] This application aims to address at least one of the technical problems existing in the prior art. To this end, this application proposes an electromagnetic clutch and a vehicle that controls dual-gear switching by switching on and off with a single drive source, greatly simplifying the drive and control structure, making control simple and manufacturing cost low.

[0004] In a first aspect, this application provides an electromagnetic clutch, comprising: Drive wheel; The movable gear plate is circumferentially fixed to the driving wheel and movable along the axis of the driving wheel; The drive unit includes an electromagnetic coil and an elastic element; At least two driven wheels are arranged at intervals along the axis of the driving wheel; When the electromagnetic coil is energized, it generates a unidirectional electromagnetic force, which drives the movable gear disk to move axially in the first direction, so that the movable gear disk engages with the first driven wheel and disengages from the second driven wheel among at least two driven wheels; when the electromagnetic coil is de-energized, the elastic element provides a return force opposite to the first direction, which drives the movable gear disk to move axially in the second direction, so that the movable gear disk engages with the second driven wheel and disengages from the first driven wheel.

[0005] According to the electromagnetic clutch of this application, a drive unit consisting of a single electromagnetic coil and an elastic element, in conjunction with a circumferentially fixed but axially movable movable gear disc and at least two driven wheels spaced apart along the axial direction, can achieve dual-gear or even multi-gear switching controlled by a single drive source, significantly simplifying the drive structure and control logic, reducing the number of parts, manufacturing costs, and failure risks. Simultaneously, the single electromagnetic coil avoids the problem of excessive axial space occupation caused by multiple coil stacking, resulting in a more compact overall structure. This makes it suitable for scenarios with high installation space requirements, such as wheel-side reducers. Furthermore, power switching is achieved through the meshing of the movable gear disc with different driven wheels, resulting in high transmission efficiency and stable torque transmission, further improving the performance and applicability of the electromagnetic clutch.

[0006] According to one embodiment of this application, the first driven wheel and the second driven wheel are coaxially arranged with the movable gear plate; The first driven wheel is arranged along the axial direction of the movable gear disk on one side of the movable gear disk, and the movable gear disk has a first tooth for meshing with the first driven wheel on the side facing the first driven wheel; The second driven wheel is arranged circumferentially around the movable gear disk, and the circumferential side of the movable gear disk is provided with a second tooth for meshing with the second driven wheel.

[0007] According to one embodiment of this application, the first tooth is a toothed insert that is evenly distributed circumferentially along the end face of the movable toothed disc, and an elastic element is disposed between the first driven wheel and the movable toothed disc, and applies an elastic force away from the first driven wheel to the movable toothed disc.

[0008] According to one embodiment of this application, a first limiting groove is provided on the side of the first driven wheel facing the movable gear plate, and a second limiting groove is provided on the side of the movable gear plate facing the first driven wheel. The second limiting groove is located inside the first tooth portion, and the two ends of the elastic member are respectively located in the first limiting groove and the second limiting groove.

[0009] According to one embodiment of this application, the second tooth is a trapezoidal tooth extending axially along the outer circumferential surface of the movable toothed disc, and the inner circumferential surface of the second driven wheel is provided with an internal meshing tooth that meshes with the trapezoidal tooth, the axial dimension of the internal meshing tooth being larger than the axial dimension of the trapezoidal tooth.

[0010] According to one embodiment of this application, the tips of the first tooth and the second tooth are both provided with chamfers, and the angle of the chamfer is 15°-30°. The corresponding tooth ends of the first driven wheel meshing with the first tooth section, and the corresponding tooth ends of the second driven wheel meshing with the second tooth section, are all provided with matching chamfers.

[0011] According to one embodiment of this application, the radial dimension of the first driven wheel is smaller than that of the second driven wheel, the first driven wheel and the second driven wheel partially overlap in the axial direction, and the second driven wheel is arranged around the first driven wheel.

[0012] According to one embodiment of this application, the electromagnetic coil is fixedly installed on the clutch housing and has a radial clearance between it and the drive wheel. The drive unit also includes a push ring, which is sleeved on the outside of the drive wheel and located between the electromagnetic coil and the movable gear plate. When the electromagnetic coil is energized, it drives the push ring to move axially. The end of the push ring away from the electromagnetic coil abuts against the movable gear plate to push the movable gear plate to move in the first direction.

[0013] According to one embodiment of this application, the push ring has a guide slope at one end near the movable gear plate, and the movable gear plate has a mating slope that matches the guide slope at one end near the push ring.

[0014] Secondly, this application provides a vehicle that includes an electromagnetic clutch as described in any of the technical solutions in the first aspect.

[0015] The beneficial effects of the vehicle provided in the second aspect of this application are the same as those of the electromagnetic clutch provided in the first aspect, and will not be repeated here.

[0016] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0017] The above and / or additional aspects and advantages of this application will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which: Figure 1 This is an exploded structural diagram of the electromagnetic clutch provided in an embodiment of this application; Figure 2 This is a cross-sectional view of the electromagnetic clutch provided in an embodiment of this application; Figure 3 This is another cross-sectional view of the electromagnetic clutch provided in an embodiment of this application.

[0018] Figure label: 100. Electromagnetic clutch; 110. Driving wheel; 120. Movable gear disc; 121. First tooth; 122. Second tooth; 123. Second receiving groove; 130. Drive unit; 131. Electromagnetic coil; 132. Push ring; 133. Elastic element; 140. First driven wheel; 141. First receiving groove; 150. Second driven wheel; 151. Internal meshing tooth. Detailed Implementation

[0019] The embodiments of this application are described in detail below. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this application, and should not be construed as limiting this application.

[0020] The following is for reference. Figures 1-3 An electromagnetic clutch according to an embodiment of this application is described.

[0021] Please see Figure 1 , Figure 2 and Figure 3 This application provides an electromagnetic clutch 100, which includes: a driving wheel 110, a movable gear 120, a drive unit 130, and at least two driven wheels.

[0022] The drive wheel 110 is the starting component for power transmission in the electromagnetic clutch 100. It can be designed as a disc, cylinder, or pulley, depending on actual transmission requirements. Its outer surface or end face can be provided with structures for cooperation with other components, such as splines, keyways, or bosses for circumferential fixation with the movable gear disc 120. The center of the drive wheel 110 can have a mounting hole for connection to the power input shaft. The inner wall of the mounting hole can be machined with a keyway or spline to achieve circumferential fixation between the drive wheel 110 and the power input shaft, ensuring stable power transmission to the drive wheel 110; alternatively, the drive wheel 110 can be integrally formed with the input shaft.

[0023] The movable gear 120 and the driving wheel 110 are circumferentially fixed and movable along the axis of the driving wheel 110.

[0024] The movable gear 120 and the driving wheel 110 are circumferentially fixed and movable along the axis of the driving wheel 110. Here, circumferentially fixed means that the movable gear 120 and the driving wheel 110 cannot rotate relative to each other in the circumferential direction, so as to ensure that the power of the driving wheel 110 can be synchronously transmitted to the movable gear 120.

[0025] There are several ways to achieve circumferential fixation. For example, an axially extending spline can be provided on the end face of the drive wheel 110, and a spline hole matching the spline can be provided at the corresponding position of the movable gear disk 120. The movable gear disk 120 can be sleeved on the spline of the drive wheel 110 through the spline hole, which achieves both circumferential fixation and allows the movable gear disk 120 to move smoothly along the extension direction of the spline (i.e., the axial direction of the drive wheel 110). Alternatively, a guide key can be provided between the drive wheel 110 and the movable gear disk 120. A keyway can be provided on the drive wheel 110, and the guide key can be fixed in the keyway. A long groove that mates with the guide key can be provided on the movable gear disk 120, and the guide key can slide in the long groove, thereby achieving axial movement and circumferential fixation of the movable gear disk 120.

[0026] The movable gear 120 can be provided with teeth for meshing with the driven wheel. The shape, number and distribution of the teeth can be determined according to the transmission accuracy and torque requirements. For example, involute tooth shape or rectangular tooth shape can be used. The number of teeth can be 10, 12, 15, etc., as long as it can meet the meshing transmission with different driven wheels.

[0027] The drive unit 130 includes an electromagnetic coil 131 and an elastic element 133.

[0028] The electromagnetic coil 131 is the core component that generates driving force. It can be fixedly mounted on the fixed housing or bracket of the electromagnetic clutch 100. The winding method and number of turns of the coil can be designed according to the required electromagnetic force. The unidirectional electromagnetic force generated after the coil is energized can act directly or indirectly on the movable gear 120, pushing the movable gear 120 to move axially.

[0029] The elastic element 133 is used to provide a return force to the movable gear 120 when the electromagnetic coil 131 is de-energized. The type of elastic element 133 can be a spring, such as a cylindrical helical spring, a disc spring, or a wave spring. The installation position of the elastic element 133 can be determined according to the structural layout. For example, the elastic element 133 can be sleeved on the outside of the driving wheel 110, with one end abutting against the stepped surface of the driving wheel 110 and the other end abutting against one side of the movable gear 120. When the movable gear 120 moves in the first direction, the elastic element 133 is compressed or stretched and stores elastic potential energy. When the electromagnetic coil 131 is de-energized, the elastic element 133 releases the elastic potential energy and pushes the movable gear 120 back to the second direction. Alternatively, the elastic element 133 can be set on the side of the movable gear 120 away from the first driven wheel 140, with one end connected to the fixed component and the other end connected to the movable gear 120, which can also achieve the return function.

[0030] At least two driven wheels are arranged at intervals along the axis of the driving wheel 110.

[0031] The number of driven wheels is not specifically limited; there can be two, three, four, or more. When there are two driven wheels, they are the first driven wheel 140 and the second driven wheel 150, which are arranged sequentially along the axis of the driving wheel 110 and coaxially with it. A certain interval is maintained between the two driven wheels. This interval must be sufficient to allow the movable gear 120 to engage or disengage with at least two driven wheels when it moves axially, avoiding simultaneous engagement or disengagement. When there are three driven wheels, they are arranged sequentially and spaced apart along the axial direction. In this case, the movable gear 120 can engage with different driven wheels under the action of the electromagnetic coil 131 and the elastic element 133, achieving more gear switching.

[0032] Each driven wheel may be provided with a mounting structure for connecting to the power output shaft, such as an internal spline, keyway, or set screw hole. The driven wheel is provided with teeth that match the teeth of the movable gear 120 to ensure that the torque can be stably transmitted when the two mesh. The driven wheel is usually mounted on a fixed shaft or housing by bearings, so that it can rotate freely and does not move with the axial movement of the driving wheel 110 or the movable gear 120.

[0033] When the electromagnetic coil 131 is energized, it generates a unidirectional electromagnetic force, driving the movable gear 120 to move axially in the first direction, so that the movable gear 120 engages with the first driven wheel 140 and disengages from the second driven wheel 150 among at least two driven wheels; when the electromagnetic coil 131 is de-energized, the elastic element 133 provides a return force opposite to the first direction, driving the movable gear 120 to move axially in the second direction, so that the movable gear 120 engages with the second driven wheel 150 and disengages from the first driven wheel 140.

[0034] In actual implementation, please refer to Figure 2 When switching to the first gear, the electromagnetic coil 131 is energized, generating a unidirectional electromagnetic force. This force acts on the movable gear 120, overcoming the force of the elastic element 133, and drives the movable gear 120 to move in the first direction along the axis of the driving wheel 110. As the movable gear 120 moves, the teeth on one side closer to the first driven wheel 140 gradually engage with the teeth of the first driven wheel 140, while the teeth on the other side gradually disengage from the teeth of the second driven wheel 150. At this time, the power of the driving wheel 110 is transmitted sequentially through the movable gear 120 to the first driven wheel 140, and then from the first driven wheel 140 to the corresponding power output shaft, realizing the power output of the first gear. Please refer to [link to relevant documentation]. Figure 3 When it is necessary to switch to the second gear, the power supply of the electromagnetic coil 131 is disconnected, the electromagnetic force disappears, and the elastic element 133 releases the stored elastic potential energy, generating a return force opposite to the first direction. The return force drives the movable gear 120 to move axially in the second direction. The teeth of the movable gear 120 near the second driven wheel 150 gradually mesh with the teeth of the second driven wheel 150, while separating from the teeth of the first driven wheel 140. The power of the driving wheel 110 is then transmitted to the second driven wheel 150 through the movable gear 120, and then transmitted from the second driven wheel 150 to the corresponding power output shaft, realizing the power output of the second gear.

[0035] According to the electromagnetic clutch 100 provided in this application embodiment, the drive unit 130 consisting of a "single electromagnetic coil 131 + elastic element 133," in conjunction with a circumferentially fixed and axially movable movable gear disc 120 and at least two driven wheels spaced apart along the axial direction, can achieve dual-gear or even multi-gear switching under single-drive-source power-on / off control. This significantly simplifies the drive structure and control logic, reduces the number of parts, and lowers manufacturing costs and failure risks. Simultaneously, the single electromagnetic coil 131 avoids the problem of excessive axial space occupation caused by multiple coil stacking, resulting in a more compact overall structure. This makes it suitable for scenarios with high installation space requirements, such as wheel-side reducers. Furthermore, power switching is achieved through the meshing of the movable gear disc 120 with different driven wheels, resulting in high transmission efficiency and stable torque transmission, further improving the performance and applicability of the electromagnetic clutch 100.

[0036] Please see Figure 1 , Figure 2 and Figure 3 According to some embodiments of this application, the first driven wheel 140 and the second driven wheel 150 can be coaxially arranged with the movable gear disk 120; the first driven wheel 140 is arranged along the axial direction of the movable gear disk 120 on one side of the movable gear disk 120, and the movable gear disk 120 is provided with a first tooth 121 for meshing with the first driven wheel 140 on the side facing the first driven wheel 140; the second driven wheel 150 is arranged circumferentially around the movable gear disk 120, and the circumferential side of the movable gear disk 120 is provided with a second tooth 122 for meshing with the second driven wheel 150.

[0037] The first driven wheel 140 is arranged along the axial direction of the movable gear 120 on one side of the movable gear 120. Specifically, it can be arranged on the side of the movable gear 120 close to the electromagnetic coil 131 or away from the electromagnetic coil 131. Its arrangement position needs to be adapted to the first movement direction of the movable gear 120 when the electromagnetic coil 131 is energized, so as to ensure that the electromagnetic force can drive the movable gear 120 to move towards the first driven wheel 140 and achieve meshing. The movable gear 120 has a first tooth section 121 on the side facing the first driven wheel 140. The first tooth section 121 is a tooth structure with teeth evenly distributed along the circumference of the end face of the movable gear 120. The tooth shape can be involute, rectangular, or trapezoidal, etc. The module and number of teeth of the teeth must match the teeth on the end face of the first driven wheel 140 to achieve precise meshing. For example, when the diameter of the end face of the movable gear 120 is 80mm, the first tooth section 121 can be provided with 16 involute teeth with a module of 5. The corresponding teeth on the end face of the first driven wheel 140 are also provided with the same parameters to ensure a stable transmission ratio during meshing. The function of the first tooth section 121 is to mesh with the teeth of the first driven wheel 140 when the movable gear 120 moves in the first direction, so as to transmit the power from the driving wheel 110 to the movable gear 120 to the first driven wheel 140, thereby realizing the power output of the first gear.

[0038] The second driven wheel 150 is arranged circumferentially around the movable gear disk 120, that is, the second driven wheel 150 has a ring-shaped structure, with its inner ring surface facing the outer ring surface of the movable gear disk 120, and a certain gap is maintained between them. This gap must ensure that the movable gear disk 120 does not rub against the inner ring surface of the second driven wheel 150 when it moves axially, and at the same time ensure that the second teeth 122 can accurately mesh with the second driven wheel 150 when the movable gear disk 120 moves in the second direction. The second driven wheel 150 can be fixed by connecting it to the housing or fixed bracket, and mounting it on a fixed structure through bearings, so that it can rotate freely around the axis of the movable gear disk 120 and does not move with the axial movement of the movable gear disk 120. The movable gear disk 120 has a second tooth 122 on its circumference. The second tooth 122 is a tooth structure that extends axially along the outer circumferential surface of the movable gear disk 120. The extension length of the tooth must be adapted to the axial movement stroke of the movable gear disk 120 to ensure that when the movable gear disk 120 moves to the designated position in the second direction, the second tooth 122 can fully mesh with the inner ring tooth of the second driven wheel 150. The tooth profile of the second tooth 122 can also adopt an involute tooth profile or a rectangular tooth profile. Its module and number of teeth must be consistent with the tooth parameters of the inner ring of the second driven wheel 150. For example, when the outer circumferential diameter of the movable gear disk 120 is 60mm, the second tooth 122 can be provided with 12 rectangular teeth with a module of 5. The inner ring of the second driven wheel 150 is provided with 12 teeth of the same tooth profile to ensure the stability of the meshing transmission.

[0039] In actual operation, when the electromagnetic coil 131 is energized, the generated unidirectional electromagnetic force drives the movable gear 120 to move axially in the first direction (i.e., towards the first driven wheel 140). The first tooth 121 on the end face of the movable gear 120 gradually approaches and meshes with the teeth on the end face of the first driven wheel 140. At the same time, the second tooth 122 on the periphery of the movable gear 120 gradually moves away from the inner ring teeth of the second driven wheel 150 as the movable gear 120 moves, eventually separating from the second driven wheel 150. At this time, the power is transmitted through the driving wheel 110, the movable gear 120, and the first driven wheel 140. 40 transmits power to complete the first gear shift; when the electromagnetic coil 131 is de-energized, the return force of the elastic element 133 drives the movable gear 120 to move axially in the second direction (i.e., away from the first driven wheel 140 and closer to the inner ring of the second driven wheel 150). The first tooth 121 on the end face of the movable gear 120 gradually separates from the first driven wheel 140, while the second tooth 122 on the periphery of the movable gear 120 gradually enters the inner ring of the second driven wheel 150 and meshes with it. At this time, the power is transmitted through the driving wheel 110, the movable gear 120, and the second driven wheel 150 to complete the second gear shift.

[0040] This axial arrangement of the first driven wheel 140 and its circumferential surrounding of the second driven wheel 150 further optimizes the axial spatial layout of the electromagnetic clutch 100, avoiding the overall length increase caused by the axial stacking of the two driven wheels, and is more suitable for compact installation scenarios.

[0041] Please see Figure 1 , Figure 2 and Figure 3 According to some embodiments of this application, the first tooth 121 can be a toothed insert that is evenly distributed circumferentially along the end face of the movable toothed disc 120, and the elastic member 133 is disposed between the first driven wheel 140 and the movable toothed disc 120, and applies an elastic force away from the first driven wheel 140 to the movable toothed disc 120.

[0042] The first tooth section 121 consists of evenly distributed teeth along the circumference of the end face of the movable gear 120. A toothed engagement tooth is a tooth structure that transmits power through tooth-to-tooth engagement. Its tooth surface is typically straight or inclined. Compared to ordinary involute teeth, toothed engagement teeth have a larger meshing area, stronger torque transmission capability, and can achieve rapid tooth engagement during meshing, reducing shifting impact. The number of toothed engagement teeth can be determined according to the size of the movable gear 120 and the torque transmission requirements; for example, 8, 10, or 12 teeth can be set. The tooth groove width between adjacent toothed engagement teeth matches the tooth width to ensure precise engagement with the toothed engagement teeth on the end face of the first driven wheel 140. The height of the toothed engagement teeth must meet the meshing depth requirements and can be 3mm-8mm, ensuring sufficient meshing strength while avoiding excessively long meshing strokes due to excessive tooth height. This toothed gear structure makes the meshing of the movable gear 120 with the first driven wheel 140 more reliable, and is especially suitable for high torque transmission scenarios, such as the wheel-side reducer transmission of a vehicle.

[0043] The specific type of elastic element 133 can be a cylindrical helical compression spring, a disc spring, or a wave spring, etc. Considering the installation space and the stability of the return force, a cylindrical helical compression spring or a disc spring is preferred. The elastic element 133 can be installed by setting a spring seat between the movable gear 120 and the first driven wheel 140. The spring seat fits against both the movable gear 120 and the first driven wheel 140, and the elastic element 133 is sleeved on the guide post of the spring seat, achieving the positioning and installation of the elastic element 133. The number of elastic elements 133 can be set to one or more according to the return force requirement, such as two, four, or six, etc. Multiple elastic elements 133 are evenly distributed along the circumference of the movable gear 120 to ensure that the return force on the movable gear 120 is uniform, avoiding tilting or jamming of the movable gear 120 due to uneven force.

[0044] The elastic force applied by the elastic element 133 to the movable gear 120 away from the first driven wheel 140 must be matched with the electromagnetic force generated when the electromagnetic coil 131 is energized. This ensures that the electromagnetic force can overcome the elastic force to drive the movable gear 120 to move towards the first driven wheel 140 and achieve engagement, and that after the electromagnetic coil 131 is de-energized, the movable gear 120 can be quickly pushed back to its original position by sufficient elastic force to engage with the second driven wheel 150.

[0045] Please see Figure 1 , Figure 2 and Figure 3 According to some embodiments of this application, a first limiting groove may be provided on the side of the first driven wheel 140 facing the movable gear 120, and a second limiting groove may be provided on the side of the movable gear 120 facing the first driven wheel 140. The second limiting groove is located inside the first tooth 121, and the two ends of the elastic member 133 are respectively located in the first limiting groove and the second limiting groove.

[0046] The first limiting groove is located on the side of the first driven wheel 140 facing the movable gear disk 120, i.e., the end face of the first driven wheel 140. Its shape matches the shape of the end of the elastic element 133. If the elastic element 133 is a cylindrical helical compression spring, the first limiting groove is designed as a circular groove, and the circular groove is coaxially arranged with the first driven wheel 140 to facilitate relative rotation between the elastic element 133 and the first driven wheel 140. The diameter of the groove is slightly larger than the outer diameter of the spring end to ensure that the spring end can be smoothly inserted without wobbling. The depth of the first limiting groove needs to be determined according to the compression stroke of the elastic element 133, and can be 1 / 5 to 1 / 3 of the free length of the elastic element 133. This ensures that the end of the elastic element 133 has sufficient insertion depth for positioning, while avoiding the elastic element 133 not being able to fully extend when compressed due to excessive groove depth.

[0047] The second limiting groove is located on the side of the movable gear 120 facing the first driven wheel 140, i.e., the end face of the movable gear 120, and inside the first tooth 121. Here, "inner side" refers to the side close to the central axis of the movable gear 120. It forms an inner-outer distribution structure with the first tooth 121 along the radial direction of the movable gear 120. This layout can avoid spatial interference between the second limiting groove and the first tooth 121, while making full use of the inner space of the end face of the movable gear 120, without affecting the meshing of the first tooth 121 and the first driven wheel 140. The shape and size of the second limiting groove are consistent with the first limiting groove. For example, when the elastic element 133 is a cylindrical helical compression spring, the second limiting groove is also a circular groove with the same diameter and depth as the first limiting groove, ensuring that the elastic element 133 is subjected to uniform force at both ends.

[0048] The two ends of the elastic member 133 are located in the first limiting groove and the second limiting groove, respectively. That is, one end of the elastic member 133 is embedded in the first limiting groove of the first driven wheel 140, and the other end is embedded in the second limiting groove of the movable gear 120. Through the combined action of the two limiting grooves, the elastic member 133 is limited in the axial extension direction. This installation method effectively prevents the elastic element 133 from radially shifting during compression or extension. For example, when the electromagnetic coil 131 is energized and drives the movable gear 120 to move toward the first driven wheel 140, the elastic element 133 is compressed. At this time, the first and second limiting grooves can limit the radial displacement of the end of the elastic element 133, ensuring that the elastic element 133 deforms only along the axial direction. When the electromagnetic coil 131 is de-energized and the elastic element 133 extends to push the movable gear 120 back to its original position, the two limiting grooves can also ensure that the elastic element 133 applies force along the axial direction, preventing the movable gear 120 from tilting due to the offset of the elastic element 133, ensuring that the movable gear 120 can move smoothly along the axial direction, thereby ensuring precise meshing with the first driven wheel 140 and the second driven wheel 150.

[0049] Please see Figure 1 , Figure 2 and Figure 3 According to some embodiments of this application, the second tooth 122 can be a trapezoidal tooth extending axially along the outer circumferential surface of the movable toothed disc 120, and the inner circumferential surface of the second driven wheel 150 is provided with an internal meshing tooth 151 that meshes with the trapezoidal tooth, and the axial dimension of the internal meshing tooth 151 is greater than the axial dimension of the trapezoidal tooth.

[0050] The second tooth 122 is a trapezoidal tooth extending axially along the outer circumferential surface of the movable gear disk 120. The tooth profile of the trapezoidal tooth is characterized by the tooth tip and tooth root being parallel planes, and the tooth surfaces on both sides being inclined surfaces. Compared with rectangular teeth, the tooth surface of the trapezoidal tooth has a certain taper, resulting in better meshing guidance. When the movable gear disk 120 moves axially in the second direction, the inclined tooth surface of the trapezoidal tooth can form a natural guiding fit with the internal meshing tooth 151 of the second driven wheel 150. Even if there is a slight circumferential misalignment between the two teeth, the inclined tooth surface can automatically align itself through sliding, reducing meshing jamming or tooth impact, improving shifting smoothness, and having a larger tooth surface contact area. The inclined tooth surface of the trapezoidal tooth increases the contact area with the internal meshing tooth 151, which can transmit torque more evenly, reduce the force per unit area of ​​the tooth surface, reduce tooth surface wear, and extend the service life of the second tooth 122 and the internal meshing tooth 151.

[0051] The tooth height and pitch of the trapezoidal teeth need to be determined according to the outer diameter of the movable gear 120 and the torque transmission requirements. For example, when the outer diameter of the movable gear 120 is 60mm, the tooth pitch of the trapezoidal teeth can be set to 15mm and the tooth height (radial distance from the tooth root to the tooth tip) can be set to 5mm. This ensures the strength of the teeth and avoids excessive tooth height causing interference with the inner ring surface of the second driven wheel 150.

[0052] The inner circumferential surface of the second driven wheel 150 is provided with internal meshing teeth 151 that mesh with trapezoidal teeth. The internal meshing teeth 151 are tooth-shaped structures extending axially along the inner circumferential surface of the second driven wheel 150. Their tooth profile parameters are completely matched with those of the trapezoidal teeth. That is, the tooth pitch, tooth tip width, tooth root width, and inclination angle of the two sides of the internal meshing teeth 151 are all consistent with those of the trapezoidal teeth, ensuring that the two can achieve precise meshing. The internal meshing teeth 151 are arranged to be continuously distributed along the inner circumferential surface of the second driven wheel 150, forming a complete internal gear ring structure. The number of teeth on the gear ring is the same as the number of teeth on the trapezoidal teeth on the movable gear disk 120. For example, when there are 12 trapezoidal teeth, there are also 12 internal meshing teeth 151, ensuring that each trapezoidal tooth can form a stable mesh with the corresponding internal meshing teeth 151, avoiding transmission fluctuations caused by mismatch in the number of teeth. In addition, the surface hardness of the internal meshing tooth 151 needs to be compatible with the hardness of the trapezoidal tooth. The surface hardness can be increased to HRC58-62 through processes such as surface hardening to ensure that the two are not prone to surface wear or plastic deformation during long-term meshing transmission.

[0053] The axial dimension of the internal meshing tooth 151 is larger than that of the trapezoidal tooth. Here, "axial dimension" refers to the length of the tooth profile along the axis of the electromagnetic clutch 100. This dimension design provides sufficient meshing tolerance for the axial movement of the movable gear disc 120. Specifically, it can compensate for installation errors. During actual assembly, the axial travel of the movable gear disc 120 may have slight deviations due to factors such as the machining accuracy of parts and assembly clearances. The longer axial dimension of the internal meshing tooth 151 can cover these deviations, ensuring that even if the return position of the movable gear disc 120 is slightly offset, the trapezoidal tooth can be fully engaged in the tooth groove of the internal meshing tooth 151, achieving reliable meshing. The specific dimensional difference can be determined according to the actual working conditions. For example, when the axial dimension of the trapezoidal tooth is 12mm, the axial dimension of the internal meshing tooth 151 can be set to 15mm-18mm, with the difference controlled within 3mm-6mm. This satisfies the tolerance requirements without causing the overall axial dimension of the second driven wheel 150 to be too large due to the excessive length of the internal meshing tooth 151, thus affecting the structural compactness.

[0054] Please see Figure 1 , Figure 2 and Figure 3 According to some embodiments of this application, the tooth ends of the first tooth 121 and the second tooth 122 can both be provided with chamfer angles, the chamfer angles being 15°-30°; the corresponding tooth ends of the first driven wheel 140 meshing with the first tooth 121 and the corresponding tooth ends of the second driven wheel 150 meshing with the second tooth 122 are all provided with matching chamfer angles.

[0055] Both the first tooth portion 121 and the second tooth portion 122 have chamfered ends. Here, "tooth end" refers to the end of the tooth portion in the meshing direction. For the first tooth portion 121, the tooth end is the tip of the tooth facing the first driven wheel 140; for the second tooth portion 122, the tooth end is the tip of the tooth facing the meshing direction of the second driven wheel 150. The chamfer is an inclined surface formed by cutting or grinding at the edge of the tooth end. This inclined surface forms a certain angle with the meshing end face or tooth surface of the tooth portion, and the angle range is limited to 15°-30°. The reason for choosing this angle range is that if the angle is less than 15°, the guide slope of the chamfer is too gentle and it is difficult to effectively guide the tooth portion into meshing, and tooth end collision is still likely to occur; if the angle is greater than 30°, the guide slope of the chamfer is too steep, which will excessively weaken the structural strength of the tooth end, causing the tooth end to be prone to deformation or breakage during long-term meshing stress. An angle range of 15°-30° can ensure sufficient guiding effect while taking into account the strength of the tooth tip. For example, 15°, 20°, 25° or 30° can be selected according to the tooth size. For example, when the first tooth 121 is a module 5 toothed clutch, a 20° chamfer angle is selected. This can guide the tooth to accurately embed into the tooth groove of the first driven wheel 140 through the chamfer, without significantly reducing the meshing strength of the toothed clutch.

[0056] The corresponding tooth ends of the first driven wheel 140 meshing with the first tooth 121, and the corresponding tooth ends of the second driven wheel 150 meshing with the second tooth 122, are all provided with matching chamfers. "Matching" means that the angle and inclination direction of the chamfer of the driven wheel tooth end are completely consistent with the chamfer of the corresponding tooth, ensuring that when the two mesh, the chamfered surface of the tooth can completely fit with the chamfered surface of the driven wheel tooth end, forming a smooth guiding fit. Taking the first driven wheel 140 as an example, if the tooth end of the first tooth 121 has a 20° chamfer and the inclination direction is towards the inside of the tooth groove, then the tooth ends of the first driven wheel 140 meshing with the first tooth 121 also need to be provided with a 20° chamfer, and the inclination direction is also towards the inside of the tooth groove, so that the chamfered surfaces of the two form a "surface contact" guide during meshing, rather than a "point contact" collision.

[0057] Please see Figure 1 , Figure 2 and Figure 3 According to some embodiments of this application, the radial dimension of the first driven wheel 140 may be smaller than that of the second driven wheel 150, the first driven wheel 140 and the second driven wheel 150 may partially overlap in the axial direction, and the second driven wheel 150 is arranged around the first driven wheel 140.

[0058] The radial dimension of the first driven wheel 140 is smaller than that of the second driven wheel 150. Here, "radial dimension" mainly refers to the outer diameter of both. Specifically, if the first driven wheel 140 has an end-face meshing structure, it can be understood as the maximum radial radius of its meshing teeth; if the second driven wheel 150 has an internal meshing structure, it can be understood as the maximum radial radius of its internal meshing teeth 151. The specific dimensional difference needs to be determined according to the power transmission requirements and spatial layout. For example, the maximum outer diameter of the meshing teeth of the first driven wheel 140 can be set to 50mm, and the maximum outer diameter of the internal meshing teeth 151 of the second driven wheel 150 can be set to 80mm, or the radial radius of the meshing teeth of the first driven wheel 140 can be 25mm, and the radial radius of the internal meshing teeth 151 of the second driven wheel 150 can be 40mm, ensuring that the first driven wheel 140 can be completely accommodated within the radial range of the second driven wheel 150, providing a spatial basis for the radial nesting layout of the two. This radial dimension difference design does not affect the power transmission function of the two driven wheels, and can reduce the waste of overall radial space through radial nesting.

[0059] The first driven wheel 140 and the second driven wheel 150 partially overlap in the axial direction. "Partial axial overlap" means that there is a partial overlapping area of ​​the two driven wheels in the axial direction of the electromagnetic clutch 100, rather than that they are completely arranged back and forth along the axial direction. The axial length of the overlapping area needs to be determined according to the structural dimensions of the two driven wheels and the axial travel of the movable gear 120, to ensure that the total axial length occupied by the two driven wheels is minimized while ensuring that the movable gear 120 can mesh with the two driven wheels respectively.

[0060] Throughout the power switching process, the radial nested layout of the two driven wheels ensures that the overall axial length of the electromagnetic clutch 100 only needs to cover the axial travel of the movable gear 120 and the maximum axial length of a single driven wheel. Compared with the traditional axially parallel arrangement, the axial dimension is significantly reduced, making it particularly suitable for scenarios where installation space is limited, such as vehicle wheel-side reducers and small machine tools. At the same time, this layout does not require additional parts, improving space utilization without increasing manufacturing costs or failure risks.

[0061] Please see Figure 1 , Figure 2 and Figure 3 According to some embodiments of this application, the electromagnetic coil 131 is fixedly installed on the clutch housing and has a radial gap between it and the drive wheel 110. The drive unit 130 also includes a push ring 132, which is sleeved on the outside of the drive wheel 110 and located between the electromagnetic coil 131 and the movable gear 120. When the electromagnetic coil 131 is energized, it drives the push ring 132 to move axially. The end of the push ring 132 away from the electromagnetic coil 131 abuts against the movable gear 120 to push the movable gear 120 to move in the first direction.

[0062] The electromagnetic coil 131 is fixedly mounted on the clutch housing, which is the fixed base component of the electromagnetic clutch 100. It is typically made of metal (such as aluminum alloy or cast iron) and possesses sufficient structural strength to support all components. The electromagnetic coil 131 can be fixed using bolts, snap-fit ​​fasteners, or interference fits. For example, an annular mounting groove can be formed on the inner wall of the clutch housing, with the outer circumferential surface of the electromagnetic coil 131 fitting against the inner wall of the groove. Bolts are used to connect the coil mounting base to the housing, ensuring that the electromagnetic coil 131 does not undergo axial or radial displacement during operation. A radial clearance is provided between the electromagnetic coil 131 and the drive wheel 110. This radial clearance refers to the space maintained radially between the inner circumferential surface of the electromagnetic coil 131 and the outer circumferential surface of the drive wheel 110. This clearance prevents frictional interference between the drive wheel 110 and the electromagnetic coil 131 during rotation, while providing sufficient space for the drive wheel 110 to rotate, ensuring that the drive wheel 110 can freely transmit power.

[0063] The drive unit 130 also includes a push ring 132, which is a power transmission component connecting the electromagnetic coil 131 and the movable gear disk 120. Its material must possess certain magnetic permeability and structural strength; low-carbon steel, electrical pure iron, or other magnetically permeable materials can be selected to ensure that the electromagnetic coil 131 can effectively attract the push ring 132 and drive its movement when energized. The push ring 132 is sleeved on the outside of the drive wheel 110, meaning it has a ring-shaped structure. Its inner hole is adapted to the outer circumferential surface of the drive wheel 110, and a sliding fit structure can be provided between them (e.g., a guide groove is opened in the inner hole of the push ring 132, and a guide rib extending axially is provided on the outer circumferential surface of the drive wheel 110, with the guide rib engaging with the guide groove), ensuring that the push ring 132 can move smoothly along the axial direction of the drive wheel 110. The push ring 132 is located between the electromagnetic coil 131 and the movable gear disk 120. Its axial position must meet the following requirements: when the electromagnetic coil 131 is de-energized, the push ring 132 maintains a small gap (such as 0.1mm-0.3mm) or slight contact with the movable gear disk 120 to avoid the push ring 132 obstructing the return of the movable gear disk 120; when the electromagnetic coil 131 is energized, the push ring 132 can move towards the movable gear disk 120 under the action of electromagnetic force and reliably abut against the movable gear disk 120 to realize power transmission.

[0064] When the electromagnetic coil 131 is energized, it drives the push ring 132 to move axially. The end of the push ring 132 away from the electromagnetic coil 131 abuts against the movable gear disk 120, thereby pushing the movable gear disk 120 to move in the first direction. The end face area of ​​the push ring 132 needs to be matched with the force-bearing surface area of ​​the movable gear disk 120 to ensure that the electromagnetic force transmitted by the push ring 132 can be evenly applied to the movable gear disk 120, and to prevent the movable gear disk 120 from tilting due to uneven force. For example, the end face diameter of the push ring 132 can be set to be the same as the force-bearing end face diameter of the movable gear disk 120, or the end face of the push ring 132 can be provided with an annular protrusion that matches the annular groove on the movable gear disk 120, further improving the stability of force transmission.

[0065] According to some embodiments of this application, the end of the push ring 132 near the movable gear disk 120 may be provided with a guide slope, and the end of the movable gear disk 120 near the push ring 132 is provided with a mating slope adapted to the guide slope.

[0066] The push ring 132 has a guide slope at one end near the movable gear disk 120. The guide slope is an inclined surface machined into the edge of the end face of the push ring 132 facing the movable gear disk 120, and its inclination direction forms a certain angle with the axial and radial directions of the push ring 132. The specific structure of the guide slope needs to be designed in conjunction with the overall shape of the push ring 132. If the push ring 132 is a ring structure, the guide slope can be set on the inner edge or the outer edge of the end face of the push ring 132. It is preferred to set it on the inner edge (the side closer to the drive wheel 110) or the outer edge in the full circumference to form a ring slope, so as to ensure that the slope can be uniformly stressed in the full circumference when the push ring 132 contacts the movable gear disk 120. The inclination angle of the guide ramp needs to balance the guiding effect and structural strength. It can be set to 10°-25°, such as 15° or 20°. If the angle is too small, the guiding effect of the ramp will not be obvious and it will be difficult to correct the coaxiality deviation. If the angle is too large, it will excessively weaken the effective contact area of ​​the push ring 132 end face, resulting in excessive local pressure and aggravating wear.

[0067] The movable gear plate 120 has a mating inclined surface at one end near the push ring 132 that is adapted to the guide inclined surface. "Adapted" means that the inclination angle and inclination direction of the mating inclined surface are completely consistent with the guide inclined surface, and the position of the mating inclined surface corresponds one-to-one with the position of the guide inclined surface. This ensures that when the push ring 132 abuts against the movable gear plate 120, the guide inclined surface can fully fit with the mating inclined surface, forming a surface contact rather than a point contact or line contact. When the electromagnetic coil 131 is energized, and the push ring 132 moves towards the movable gear disk 120 under the action of electromagnetic force, if there is a slight coaxiality deviation between the push ring 132 and the movable gear disk 120, the guide slope of the push ring 132 will first partially contact the mating slope of the movable gear disk 120. Due to the inclined structure of the slope, the radial component force generated by the contact will push the push ring 132 or the movable gear disk 120 to automatically adjust its position and correct the coaxiality deviation until the guide slope and the mating slope are fully circumferentially fitted. After fitting, the electromagnetic force is evenly transmitted to the movable gear disk 120 through the entire slope, avoiding the local force concentration caused by deviation during traditional planar contact, and reducing the wear of the end faces of the push ring 132 and the movable gear disk 120. During the movement of the movable gear disk 120 in the first direction, the guide slope and the mating slope always remain in a fitted state, continuously providing stable guidance for the axial movement of the movable gear disk 120, ensuring that the movable gear disk 120 can move smoothly towards the first driven wheel 140 and accurately achieve meshing.

[0068] This inclined surface mating structure is particularly suitable for working conditions with frequent gear shifting over long periods. It can effectively reduce the contact wear between the push ring 132 and the movable gear 120, extend their service life, improve the anti-deviation capability of the drive unit 130, reduce the stringent requirements on the coaxiality of the push ring 132 and the movable gear 120, indirectly simplify the assembly process, and improve production efficiency.

[0069] This application also provides a vehicle that includes an electromagnetic clutch 100 as described in any of the above technical solutions.

[0070] Since the vehicle provided in this application embodiment includes the electromagnetic clutch 100 of any of the above technical solutions, it has the technical features and effects of the electromagnetic clutch 100 of any of the above technical solutions, which will not be repeated here.

[0071] The installation location of the electromagnetic clutch 100 in a vehicle can be determined according to the vehicle's power transmission requirements. Typical application scenarios include key power transmission components such as wheel-side reducers, gearboxes, or transfer cases. Taking a wheel-side reducer as an example, the wheel-side reducer of a vehicle needs to achieve power reduction and torque increase and gear switching within a limited wheel hub space to adapt to different working conditions such as low-speed climbing and high-speed cruising. The electromagnetic clutch 100 provided in this application embodiment has a compact overall structure and can adapt to the compact installation space of the wheel-side reducer. At this time, the driving wheel 110 of the electromagnetic clutch 100 is connected to the half-shaft of the vehicle drive axle and is circumferentially fixed by spline or key connection to ensure that the power of the half-shaft can be stably transmitted to the driving wheel 110. The first driven wheel 140 and the second driven wheel 150 of the electromagnetic clutch 100 are respectively connected to different reduction gear sets of the wheel-side reducer. Through the difference in the transmission ratio of different reduction gear sets, the dual gear switching of the vehicle wheel-side is realized. For example, the first driven wheel 140 is connected to the high-speed gear set (small transmission ratio, suitable for high-speed cruising of the vehicle), and the second driven wheel 150 is connected to the low-speed gear set (large transmission ratio, suitable for low-speed climbing or heavy-load start of the vehicle).

[0072] If the electromagnetic clutch 100 is applied to a vehicle transmission, it can replace the synchronizer shifting mechanism or multi-coil electromagnetic clutch 100 in a traditional transmission, simplifying the internal structure of the transmission. In this case, the driving wheel 110 of the electromagnetic clutch 100 is connected to the input shaft of the transmission, and the first driven wheel 140 and the second driven wheel 150 are respectively connected to gears with different transmission ratios within the transmission. The engagement of the movable gear plate 120 with different driven wheels is controlled by the on / off state of the electromagnetic coil 131, thus achieving gear shifting. Compared to a traditional synchronizer shifting mechanism, this electromagnetic clutch 100 eliminates the need for complex accessories such as shift forks, shift drums, and shift motors. This not only reduces the number of transmission parts, lowers manufacturing costs and reduces the risk of failure, but also simplifies the shifting control logic. Gear shifting can be completed simply by controlling the on / off state of the electromagnetic coil 131, improving shifting response speed and enhancing the driving experience.

[0073] The terms "first," "second," etc., used in the specification and claims of this application are used to distinguish similar objects and not to describe a specific order or sequence. It should be understood that such use of data can be interchanged where appropriate so that embodiments of this application can be implemented in orders other than those illustrated or described herein, and the objects distinguished by "first," "second," etc., are generally of the same class and the number of objects is not limited; for example, a first object can be one or more. Furthermore, in the specification and claims, "and / or" indicates at least one of the connected objects, and the character " / " generally indicates that the preceding and following objects are in an "or" relationship.

[0074] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0075] In the description of this application, "first feature" and "second feature" may include one or more of the features.

[0076] In the description of this application, "multiple" means two or more.

[0077] In the description of this application, the first feature being "above" or "below" the second feature may include the first and second features being in direct contact, or the first and second features being in contact through another feature between them.

[0078] In the description of this application, the terms "above," "over," and "on top" for the first feature and the second feature include the first feature being directly above or diagonally above the second feature, or simply indicate that the first feature is at a higher horizontal level than the second feature.

[0079] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0080] Although embodiments of this application have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of this application, the scope of which is defined by the claims and their equivalents.

Claims

1. An electromagnetic clutch, characterized in that, include: Drive wheel; The movable gear plate is circumferentially fixed to the driving wheel and movably disposed along the axial direction of the driving wheel; The drive unit includes an electromagnetic coil and an elastic element; At least two driven wheels are arranged at intervals along the axial direction of the driving wheel; When the electromagnetic coil is energized, it generates a unidirectional electromagnetic force, driving the movable gear disk to move axially in a first direction, causing the movable gear disk to engage with the first driven wheel and disengage from the second driven wheel among the at least two driven wheels; when the electromagnetic coil is de-energized, the elastic element provides a return force opposite to the first direction, driving the movable gear disk to move axially in a second direction, causing the movable gear disk to engage with the second driven wheel and disengage from the first driven wheel.

2. The electromagnetic clutch according to claim 1, characterized in that, The first driven wheel and the second driven wheel are coaxially arranged with the movable gear plate; The first driven wheel is arranged along the axial direction of the movable gear disk on one side of the movable gear disk, and the movable gear disk has a first tooth for meshing with the first driven wheel on the side facing the first driven wheel; The second driven wheel is arranged circumferentially around the movable gear disk, and the circumferential side of the movable gear disk is provided with a second tooth for meshing with the second driven wheel.

3. The electromagnetic clutch according to claim 2, characterized in that, The first tooth is a toothed insert that is evenly distributed around the end face of the movable toothed disc. The elastic element is disposed between the first driven wheel and the movable toothed disc and applies an elastic force away from the first driven wheel to the movable toothed disc.

4. The electromagnetic clutch according to claim 3, characterized in that, The first driven wheel has a first limiting groove on the side facing the movable gear plate, and the movable gear plate has a second limiting groove on the side facing the first driven wheel. The second limiting groove is located inside the first tooth, and the two ends of the elastic member are respectively located in the first limiting groove and the second limiting groove.

5. The electromagnetic clutch according to claim 2, characterized in that, The second tooth is a trapezoidal tooth extending axially along the outer circumferential surface of the movable toothed disc. The inner circumferential surface of the second driven wheel is provided with an internal meshing tooth that meshes with the trapezoidal tooth. The axial dimension of the internal meshing tooth is greater than the axial dimension of the trapezoidal tooth.

6. The electromagnetic clutch according to any one of claims 2-5, characterized in that, Both the first and second teeth have chamfered ends, and the chamfered angle is 15°-30°. The corresponding tooth ends of the first driven wheel that mesh with the first tooth section and the corresponding tooth ends of the second driven wheel that mesh with the second tooth section are both provided with matching chamfers.

7. The electromagnetic clutch according to any one of claims 2-5, characterized in that, The radial dimension of the first driven wheel is smaller than that of the second driven wheel. The first driven wheel and the second driven wheel partially overlap in the axial direction, and the second driven wheel is arranged around the first driven wheel.

8. The electromagnetic clutch according to any one of claims 1-5, characterized in that, The electromagnetic coil is fixedly installed on the clutch housing and has a radial gap between it and the drive wheel. The drive unit also includes a push ring, which is sleeved on the outside of the drive wheel and located between the electromagnetic coil and the movable gear plate. When the electromagnetic coil is energized, it drives the push ring to move axially. The end of the push ring away from the electromagnetic coil abuts against the movable gear plate to push the movable gear plate to move in the first direction.

9. The electromagnetic clutch according to claim 8, characterized in that, The push ring has a guide slope at one end near the movable gear plate, and the movable gear plate has a mating slope that matches the guide slope at one end near the push ring.

10. A vehicle, characterized in that, Including the electromagnetic clutch as described in any one of claims 1-9.

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