Suspension system, motor, actuator and vehicle

Abstract

A suspension system, a motor (1), an actuator (10) and a vehicle (1000). The suspension system comprises the motor (1), the motor (1) being adapted to adjust the distance between a vehicle body (100) and a wheel (200); the motor (1) comprises a permanent magnet (122) and a winding assembly (112), one of the permanent magnet (122) and the winding assembly (112) being connected to the vehicle body (100), and the other one thereof being connected to the wheel (200); the permanent magnet (122) and the winding assembly (112) cooperate with each other to drive the motor (1) to operate; the motor (1) is provided with a cooling flow channel (14); the cooling flow channel (14) is configured to control at least one of the temperature or flow rate of a cooling medium in the cooling flow channel (14), such that the motor (1) at least provides required thrust corresponding to the current operating condition, the temperature of the permanent magnet (122) that corresponds to a net heat output generated by operating at least a target duration under the required thrust not exceeding the demagnetization temperature of the permanent magnet (122), and the net heat output being the heat output of the winding assembly (112) at a given current minus the heat taken away by the cooling medium.

Description

Suspension system, motor, actuators and vehicle

[0001] This application claims priority to Chinese patent application No. 202411999096.7, filed on December 31, 2024, the entire contents of which are incorporated herein by reference. Technical Field

[0002] This disclosure relates to the field of vehicle technology, and more particularly to a suspension system, motor, actuator, and vehicle. Background Technology

[0003] The suspension system is a device connecting the vehicle body and wheels. Its main function is to reduce body vibration by generating thrust on the body, thereby improving vehicle comfort and handling. During driving, vehicles typically encounter various road conditions such as jumping over steps, potholes, side tilting, and uneven surfaces. In these situations, the suspension system needs to provide thrust to the body to maintain stability. Summary of the Invention

[0004] This disclosure provides a suspension system, motor, actuator, and vehicle, aimed at solving the problem that the suspension system cannot provide sufficient thrust to the vehicle under harsh conditions and sustain that thrust for the duration required, thus affecting the stability of the vehicle.

[0005] In a first aspect, a suspension system is provided, the suspension system including an electric motor adapted to be connected between the vehicle body and wheels to adjust the distance between the vehicle body and wheels; the electric motor including a permanent magnet and a winding assembly, one of the permanent magnet and the winding assembly being adapted to be connected to the vehicle body, and the other of the permanent magnet and the winding assembly being adapted to be connected to the wheels; the permanent magnet cooperating with the winding assembly to drive the electric motor; the electric motor having a cooling channel configured to cool the winding assembly by controlling at least one of the temperature or flow rate of a cooling medium in the cooling channel, so that the electric motor provides at least the required thrust corresponding to the current operating condition, and the temperature of the permanent magnet corresponding to the net heat generated at least for a target duration under said required thrust does not exceed the demagnetization temperature of the permanent magnet; the net heat generated is the heat generated by the winding assembly at a given current minus the heat carried away by the cooling medium.

[0006] In a second aspect, an electric motor is provided for a suspension system, the motor including a moving component and a fixed component, the moving component and the fixed component being capable of relative movement along the axial direction of a central rod.

[0007] Thirdly, an actuator is provided, which includes a motor and an upper support assembly connected to a fixed assembly.

[0008] Fourthly, a vehicle is provided, the vehicle including a suspension system, a body and wheels, the wheels being located on the underside of the body, and the suspension system being connected between the body and the wheels. Attached Figure Description

[0009] Figure 1 is a structural diagram of a vehicle according to some embodiments;

[0010] Figure 2 is a perspective view of the suspension system in the vehicle shown in Figure 1;

[0011] Figure 3 is a front view of the suspension system shown in Figure 2;

[0012] Figure 4 is a cross-sectional view along line AA in Figure 3;

[0013] Figure 5 is a structural diagram of the motor in the suspension system shown in Figure 2;

[0014] Figure 6 is a cross-sectional view along line BB in Figure 5;

[0015] Figure 7 is a magnified view of the area circled P1 in Figure 6;

[0016] Figure 8 is a structural diagram of the central rod in the motor shown in Figure 6;

[0017] Figure 9 is a half-sectional view of the central rod shown in Figure 8, with the section lines omitted in the figure;

[0018] Figure 10 is a cross-sectional view along line CC in Figure 8;

[0019] Figure 11 is a cross-sectional view along line DD in Figure 8;

[0020] Figure 12 is a graph showing the relationship between the thrust of the motor and the maximum duration of continuous operation of the motor.

[0021] Figure 13 shows the positional relationship between the sensor and the central rod in the motor shown in Figure 5.

[0022] Figure 14 is a magnified view of a portion of circle P2 in Figure 13;

[0023] Figure 15 shows the positional relationship between the central rod and the magnetic strip in the motor shown in Figure 13;

[0024] Figure 16 shows the connection relationship between the magnetic strip and the back plate in the motor shown in Figure 13;

[0025] Figure 17 shows the relationship between the read head and the magnetic strip in the sensor shown in Figure 13;

[0026] Figure 18 is a structural diagram of the guide rod in the motor shown in Figure 6;

[0027] Figure 19 is an exploded view of the guide rod and lower fork arm shown in Figure 18;

[0028] Figure 20 is a front view of the guide rod shown in Figure 18;

[0029] Figure 21 is a cross-sectional view of the motor shown in Figure 5;

[0030] Figure 22 is a magnified view of a portion of circle P3 in Figure 21;

[0031] Figure 23 shows the fit between the bearing assembly and the guide rod in the motor shown in Figure 21;

[0032] Figure 24 is a structural diagram of the guide rod in the motor shown in Figure 21;

[0033] Figure 25 shows the fit between the balls of the bearing assembly in the motor shown in Figure 21 and the guide groove in the guide rod.

[0034] Figure 26 is a diagram of the first structural design of the iron core in the motor shown in Figure 5;

[0035] Figure 27 is a second structural diagram of the iron core in the motor shown in Figure 5;

[0036] Figure 28 is a structural diagram of the yoke section in the iron core shown in Figure 27;

[0037] Figure 29 is a cross-sectional view along line EE in Figure 27;

[0038] Figure 30 is a structural diagram of the support component in the iron core shown in Figure 27;

[0039] Figure 31 shows the third structural diagram of the iron core in the motor shown in Figure 5;

[0040] Figure 32 is a structural diagram of the adjacent support members in the iron core shown in Figure 31 when they are snapped together;

[0041] Figure 33 is a magnified view of the area circled P4 in Figure 32;

[0042] Figure 34 is a structural diagram of the yoke section of the iron core shown in Figure 31 when it is a split structure;

[0043] Figure 35 is a magnified view of a portion of circle P5 in Figure 34;

[0044] Figure 36 is a diagram of the fourth structure of the iron core in the motor shown in Figure 5;

[0045] Figure 37 is an exploded view of the iron core shown in Figure 36 from the first perspective.

[0046] Figure 38 is an exploded view of the iron core shown in Figure 36 from a second perspective.

[0047] Figure 39 is an exploded view of another structure of the iron core shown in Figure 36 from a first-view perspective.

[0048] Figure 40 is an exploded view of another structure of the iron core shown in Figure 36 from a second perspective.

[0049] Figure 41 is an exploded view of another structure of the iron core shown in Figure 36 from a first-view perspective.

[0050] Figure 42 is an exploded view of another structure of the iron core shown in Figure 36 from a second perspective.

[0051] Figure 43 is an exploded view of another structure of the iron core shown in Figure 36 from a first perspective.

[0052] Figure 44 is an exploded view of another structure of the iron core shown in Figure 36 from a second perspective.

[0053] Figure 45 is a structural diagram of the iron core shown in Figure 36 when it is equipped with connecting ribs and connecting grooves;

[0054] Figure 46 is another structural diagram of the iron core shown in Figure 36 when it is equipped with connecting ribs and connecting grooves;

[0055] Figure 47 shows the fifth structural diagram of the iron core in the motor shown in Figure 5;

[0056] Figure 48 is a structural diagram of the teeth of the iron core shown in Figure 47;

[0057] Figure 49 is a magnified view of a portion of circle P6 in Figure 47;

[0058] Figure 50 is a structural diagram of the first barrier groove of the iron core shown in Figure 47, which extends to the outer edge of the tooth and to the inner edge of the tooth.

[0059] Figure 51 is another structural diagram of the toothed part in the iron core shown in Figure 47;

[0060] Figure 52 is a structural diagram of the second barrier groove of the iron core shown in Figure 47, which extends to the inner edge of the yoke and to the outer edge of the yoke.

[0061] Figure 53 shows the sixth structural diagram of the iron core in the motor shown in Figure 5;

[0062] Figure 54 is a structural diagram of the iron core shown in Figure 53 from a relative perspective;

[0063] Figure 55 is a structural diagram of the iron core shown in Figure 53 when it has a third rib groove;

[0064] Figure 56 is a structural diagram of the iron core shown in Figure 55 from a relative perspective;

[0065] Figure 57 is a magnified view of a portion of circle P7 in Figure 55;

[0066] Figure 58 is a magnified view of a portion of circle P8 in Figure 56;

[0067] Figure 59 is a structural diagram of the load-bearing component in the iron core shown in Figure 53;

[0068] Figure 60 is a structural diagram of the stressed component shown in Figure 59 from a relative perspective;

[0069] Figure 61 is a diagram showing the arrangement of the iron core in the winding assembly of the motor shown in Figure 5;

[0070] Figure 62 is a front view of the iron core shown in Figure 61;

[0071] Figure 63 is a structural diagram of the first end core in the core shown in Figure 61;

[0072] Figure 64 is a structural diagram of the second end core in the core shown in Figure 61;

[0073] Figure 65 is a cross-sectional view of the first end core shown in Figure 63;

[0074] Figure 66 is a cross-sectional view of the second end core shown in Figure 64;

[0075] Figure 67 shows the relationship between the iron core and the central rod in the motor shown in Figure 5.

[0076] Figure 68 is a structural diagram of the central rod shown in Figure 67;

[0077] Figure 69 is a cross-sectional view of the central rod shown in Figure 68;

[0078] Figure 70 shows the sealing relationship between the central rod, the housing seal, and the guide rod in the motor shown in Figure 5.

[0079] Figure 71 is one of the partial structural diagrams of the motor shown in Figure 70;

[0080] Figure 72 is a structural diagram of the first seal in the motor shown in Figure 70;

[0081] Figure 73 is a front view of the first seal shown in Figure 72;

[0082] Figure 74 is a cross-sectional view along line FF in Figure 73;

[0083] Figure 75 is a perspective view of the sealing bracket in the motor shown in Figure 70;

[0084] Figure 76 is one of the positional relationships between the sealing bracket and the first sealing element in the motor shown in Figure 70;

[0085] Figure 77 is the second diagram showing the positional relationship between the sealing bracket and the first sealing element in the motor shown in Figure 70.

[0086] Figure 78 is a partial structural diagram of the motor shown in Figure 71;

[0087] Figure 79 shows the connection relationship between the motor and the buffer in the suspension system shown in Figure 2.

[0088] Figure 80 shows the connection relationship between the upper support assembly and the buffer body in the suspension system shown in Figure 79.

[0089] Figure 81 is a cross-sectional view of the upper support assembly and buffer body in Figure 80;

[0090] Figure 82 is a magnified view of a portion of P9 circled in Figure 79;

[0091] Figure 83 is a magnified view of the area circled P10 in Figure 4;

[0092] Figure 84 is a magnified view of the area circled P11 in Figure 4;

[0093] Figure 85 shows the fit between the center rod and the winding assembly in the motor shown in Figure 5.

[0094] Reference numerals: 1000, Vehicle; 100, Body; 200, Wheel; 300, Suspension system; 10, Actuator; 1, Motor; 11, Fixing assembly; 111, Center rod; 111A, First rod segment; 111B, Second rod segment; 111C, Mounting slot; 111D, Guide hole; 111E, Cable outlet channel; 111F, Radial hole; 111G, Axial hole; 111M, Second oil reservoir; 111N, Insertion hole; 111H, First positioning part; 111K, Anti-rotation rod; 112, Winding assembly; 1121, Core; 1121A, Yoke; 1121B, Tooth; 1121C, First mounting hole; 1121D, Support member; 1121E, Snap-fit ​​groove; 1121F, Protrusion; 1121G, First snap-fit ​​notch; 1121H, First snap-fit ​​protrusion; 1121K, Arc-shaped segment; 1121M, First surface; 1121N, Second surface; 112A, First tooth; 112B, Second tooth; 112C, First support member; 112D, Second support member; 112E, First yoke; 112F, Second yoke; 112G, First annular portion; 112H, First rib; 112K, Second annular portion; 112L, Second rib; 112M, Connecting rib; 112N, Connecting groove; 112P, Second positioning portion; 1122, Coil; 1122A, Wire connecting segment; 1123, Receiving groove; 1124, Barrier Groove; 1124A, First Barrier Groove; 1122B, Outlet Terminal; 1124B, Second Barrier Groove; 1125, Rib Groove; 1125A, First Rib Groove; 1125B, Second Rib Groove; 1125C, Third Rib Groove; 1125D, First Inner Wall Surface; 1125E, Second Inner Wall Surface; 1125F, Third Inner Wall Surface; 1125G, Fourth Inner Wall Surface; 1125H, Fourth Rib Groove; 1125K, Load-Bearing Component; 1125M, First Recess; 1125N, Second Recess; 1126A, First End Core; 1126B, Second End Core; 1126C, Middle Core; 1126D, First Magnetic Isolation Groove; 1126E, Second magnetic isolation groove; 1126F, First limiting protrusion; 1126G, Second limiting protrusion; 1126H, First tooth crown; 1126M, First inclined surface; 1126N, Second inclined surface; 1127A, Wire passage groove; 1127B, Wire passage channel; 113, Bearing assembly; 1131, Bearing housing; 1132, Ball; 114, Second linear bearing; 115, Third seal; 116, Connector; 117, Sixth seal; 12, Motion assembly; 121, Housing; 1211, Second mounting hole; 1212, Oil injection hole; 122, Permanent magnet; 123, Guide rod; 1231, Rod body; 1232, Base; 1233, Guide groove; 124, First linear bearing; 125, First seal; 1251, Annular seal; 1251A, First sealing end;1251B, Second sealing end; 1252, Support part; 126, Second sealing element; 127, Sealing element; 128, Sealing bracket; 1281, Main body part; 1282, Connecting part; 13, Lower fork arm; 14, Cooling channel; 141, Water inlet channel; 142, Water outlet channel; 143, Merging channel; 15, Sensor; 151, Reading head; 152, Magnetic strip; 1521, First magnetic pole; 1522, Second magnetic pole; 153, Back plate; 1531, Main body part; 1532, First mating part; 1533, Second mating part; 2, Upper support assembly; 21, Upper support member; 22, Outer bracket; 221, Installation space; 222, First clearance hole; 23, Connecting assembly; 231, Inner bushing; 232, Fixing member; 233, Cover plate; 234, Fourth sealing element; 3. Buffer body; 4. Fifth seal; 5. Dustproof sleeve. Detailed Implementation

[0095] The technical solutions of the embodiments of this disclosure will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this disclosure, and not all embodiments. Based on the embodiments of this disclosure, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this disclosure.

[0096] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this disclosure, unless otherwise stated, "a plurality of" means two or more.

[0097] In the description of this specification, specific features, structures, materials, or characteristics may be combined in any suitable manner in one or more embodiments or examples.

[0098] In related technologies, the suspension system overheats quickly, and the large thrust it provides to the vehicle body is sustained for a short period of time. This results in a limited function of the suspension system, which cannot perform its original performance under adverse conditions. Consequently, the vehicle cannot provide sufficient thrust to the vehicle and sustain that thrust for the required duration under adverse conditions such as going over potholes or rolling, thus affecting the vehicle's driving stability.

[0099] To address the aforementioned technical problems, this disclosure provides a vehicle 1000 in some embodiments. The vehicle 1000 can be a pure electric vehicle, a hybrid electric vehicle, a plug-in hybrid electric vehicle, a range-extended electric vehicle, a gasoline-powered vehicle, etc. The vehicle 1000 can also be a sedan, truck, bus, lorry, trailer, etc.

[0100] Please refer to Figure 1. The vehicle 1000 includes a body 100 and wheels 200. The body 100 is used for passengers to ride in and for carrying goods. The wheels 200 are mounted under the body 100, configured to support the body 100, and are able to roll on the road surface to enable the vehicle 1000 to move.

[0101] The vehicle 1000 also includes a suspension system 300. The suspension system 300 is located between the body 100 and the wheels 200 and is configured to transmit force and torque between the body 100 and the wheels 200, and to cushion the impact forces on the body 100 during the driving of the vehicle 1000, so as to improve the comfort of riding or driving.

[0102] The suspension system 300 can be a non-independent suspension system, an independent suspension system, or an active suspension system.

[0103] In some embodiments, the suspension system 300 is an active suspension system. The stiffness and damping characteristics of the active suspension system are dynamically and adaptively adjusted according to the driving conditions of the vehicle 1000 (such as the motion state of the vehicle 1000 and the road conditions) to ensure that the suspension system 300 is always in an optimal damping state. Referring to Figure 2, the suspension system 300 may include an actuator 10. The actuator 10 can adjust the distance between the vehicle body 100 and the wheels 200 to make the vehicle 1000 more stable during operation. Furthermore, the actuator 10 can also cushion the vehicle body 100 to improve the driving comfort of the vehicle 1000.

[0104] In some embodiments, referring to Figures 3 and 4, the actuator 10 includes a motor 1 and an upper support assembly 2. The motor 1 includes a fixed assembly 11, a moving assembly 12, and a lower fork arm 13. The moving assembly 12 and the fixed assembly 11 are capable of relative movement along a first direction (direction X shown in Figure 4). The first direction may be the height direction of the vehicle 1000.

[0105] The upper support assembly 2 is connected to the fixed assembly 11, and the lower fork arm 13 is connected to the moving assembly 12. One of the upper support assembly 2 and the lower fork arm 13 is connected to the vehicle body 100, and the other is connected to the wheel 200. The connection of the support assembly 2 to the vehicle body 100 and the lower fork arm 13 to the wheel 200 are exemplarily described in this disclosure.

[0106] In this way, the relative movement of the moving component 12 and the fixed component 11 can drive the relative movement of the upper support component 2 and the lower fork arm 13, thereby adjusting the distance between the vehicle body 100 and the wheel 200, so that the vehicle body 100 can maintain stability when driving on rough roads, thereby improving the driving comfort of the vehicle body 1000.

[0107] In some examples, the upper support assembly 2 includes an upper support member 21. The actuator 10 also includes a lower support 30A and an elastic element 3A. The lower support 30A is connected to the motion assembly 12. The elastic element 3A is disposed between the upper support member 21 and the lower support 30A. For example, the elastic element 3A is disposed between the upper support member 21 and the lower support 30A. The upper support member 21 and the lower support 30A are configured to support the elastic element 3A.

[0108] By moving the fixed component 11 and the moving component 12 relative to each other, the deformation of the elastic element 3A can be changed accordingly, thereby adjusting the deformation of the elastic element 3A to adjust the buffering performance of the elastic element 3A, so that the buffering performance of the elastic element 3A matches the needs of the vehicle 1000, improving the buffering effect on the vehicle 1000 and improving the experience of the driver and passengers.

[0109] In some examples, the elastic element 3A can be a spring, a rubber cylinder, a rubber column, etc.

[0110] In some embodiments, referring to Figures 5 and 6, the fixed assembly 11 of the motor 1 includes a central rod 111 and a winding assembly 112. The winding assembly 112 is connected to the peripheral wall surface of the central rod 111. The moving assembly 12 includes a housing 121 and a permanent magnet 122. The central rod 111 is slidably connected to the housing 121. For example, the housing 121 is provided with a second mounting hole 1211. The second mounting hole 1211 communicates with the internal space of the housing 121, and the central rod 111 passes through the second mounting hole 1211. The lower fork arm 13 is connected to the outside of the housing 121. The upper support assembly 2 is connected to the central rod 111 and is located outside the housing 121.

[0111] The winding assembly 112 is located inside the housing 121. The permanent magnet 122 is connected to the inner wall of the housing 121 and is arranged around the winding assembly 112. In this way, when the winding assembly 112 is energized, a magnetic field will be generated near the winding assembly 112, and a magnetic field will also be generated near the permanent magnet 122.

[0112] The magnetic field generated by the winding assembly 112 interacts with the magnetic field generated by the permanent magnet 122, generating an axial force on the housing 121 along the central rod 111. This forces the central rod 111 and the housing 121 to move relative to each other along the central rod 111, thereby causing the moving assembly 12 and the fixed assembly 11 to move relative to each other along the central rod 111. Furthermore, the direction of the interaction force between the central rod 111 and the housing 121 can be controlled by changing the direction of the current flow in the winding assembly 112, thus adjusting the direction of relative movement between the fixed assembly 11 and the moving assembly 12.

[0113] It should be noted that the axial direction of the center rod 111 is consistent with the first direction. That is, the axial direction of the center rod 111 is consistent with the height direction of the vehicle 1000. The direction of relative movement between the fixed assembly 11 and the moving assembly 12 is along the axial direction of the center rod 111.

[0114] In some examples, referring to Figure 7, the winding assembly 112 includes a plurality of iron cores 1121 and coils 1122. The plurality of iron cores 1121 are arranged axially along the center rod 111, and a receiving groove 1123 is formed between two adjacent iron cores 1121. The coils 1122 are received within the receiving grooves 1123.

[0115] When coil 1122 is energized, it generates a magnetic field, which is the magnetic field of winding assembly 112. Iron core 1121 is configured to support coil 1122 and conduct magnetic lines of force of the magnetic field generated by coil 1122, thereby enhancing the strength of the magnetic field.

[0116] In some examples, there are multiple coils 1122. Multiple iron cores 1121 can form multiple receiving slots 1123. The multiple receiving slots 1123 are spaced apart along the axial direction of the central rod 111, and one coil 1122 is disposed in one receiving slot 1123.

[0117] In some examples, multiple coils 1122 can be divided into multiple groups, each group of coils 1122 having three coils 1122, and the wires of the three coils 1122 in each group of coils 1122 can carry alternating current of different phases. That is, the coils 1122 include three-phase wires.

[0118] The interaction between coil 1122 and permanent magnet 122 causes the suspension system 300 to exert thrust on the vehicle body 100 to adjust the distance between the vehicle body 100 and the wheels 200. During this process, coil 1122 continuously generates heat, which accumulates within housing 121, causing the temperature of permanent magnet 122 to rise continuously. If the temperature of permanent magnet 122 exceeds its demagnetization temperature, coil 1122 and permanent magnet 122 will be unable to exert thrust on the vehicle body 100, thus affecting the performance of suspension system 300.

[0119] Furthermore, vehicle 1000 encounters common driving conditions during daily operation, such as going over speed bumps, manhole covers, cornering, mountain S-curves, and undulating roads. Under these conditions, including but not limited to, the suspension system 300 needs to apply different amounts of thrust to the vehicle body 100 to ensure stability. For example, when traversing uneven surfaces with minor amplitude, the suspension system 300 only needs to apply a small amount of thrust to maintain stability. When going over speed bumps or mountain S-curves, vehicle 1000 may experience greater swaying, requiring the suspension system 300 to apply a larger amount of thrust to maintain stability.

[0120] The greater the thrust applied by the suspension system 300 to the vehicle body 100, the greater the current flowing into the coil 1122, the faster the coil 1122 heats up, and the faster the permanent magnet 122 heats up. This may cause the permanent magnet 122 to reach its demagnetization temperature in a very short time. If the permanent magnet 122 demagnetizes, the electromagnetic performance of the motor will degrade, resulting in insufficient electromagnetic thrust from the suspension system 300 under a given current. Furthermore, during the time between the suspension system 300 applying thrust to the vehicle body 100 and the suspension system 300 losing thrust, the vehicle 1000 may not have yet left the current driving condition, thus failing to guarantee that the vehicle body 100 remains in the expected stable state, thereby affecting the vehicle's stability, comfort, and handling.

[0121] If the suspension system 300 lacks a cooling mechanism, the maximum thrust applied by the suspension system 300 to the vehicle body 100 will reach 2000N, causing the temperature of the permanent magnet 122 to approach its demagnetization temperature. If the maximum thrust applied by the suspension system 300 to the vehicle body 100 exceeds 2000N, the temperature of the permanent magnet 122 will rise rapidly and demagnetize, causing the thrust applied by the suspension system 300 to the vehicle body 100 to become unsustainable. This process typically does not exceed 0.3 seconds.

[0122] In other words, if the suspension system 300 lacks a cooling mechanism, the maximum thrust applied by the suspension system 300 to the vehicle body 100 will be insufficient to support harsh operating conditions (i.e., conditions requiring high thrust, such as those exceeding 2000N). Furthermore, if a thrust exceeding 2000N is applied to the vehicle body under harsh operating conditions, it will be insufficient to sustain the current operating conditions and will still affect the stability, comfort, and handling of the vehicle 1000. Therefore, to continuously ensure the stability of the vehicle 1000, it is necessary to ensure that the thrust applied by the suspension to the vehicle body 100 is sufficiently large and can be maintained at the current thrust for the required duration.

[0123] The suspension system 300 in the related technology is unable to provide high thrust to the vehicle body 100 due to the severe overheating of the winding assembly 112, or is unable to maintain high thrust for a sustained period of time. This can cause the vehicle 1000 to fail to maintain the stability of the vehicle body 100 under some harsh or extreme working conditions, thus affecting the functionality of the suspension system 300.

[0124] Based on this, in some embodiments, the motor 1 is provided with a cooling channel 14, which is configured to cool the winding assembly 112 by controlling at least one of the temperature or flow rate of the cooling medium in the cooling channel 14, so that the temperature of the permanent magnet 122 corresponding to the net heat generated by the motor 1 under different vehicle operating conditions does not exceed the demagnetization temperature of the permanent magnet 122. The net heat generated is the heat generated by the winding assembly 112 at a given current minus the heat carried away by the cooling medium.

[0125] By providing cooling channels 14, during the continuous operation of the motor 1 under different thrusts, the cooling medium flowing within the cooling channels 14 can exchange heat with the winding assembly 112, thereby removing the heat generated during the operation of the winding assembly 112 and the heat generated by the operation of other components of the motor 1 (such as the heat generated by friction when the fixed assembly 11 and the moving assembly 12 move relative to each other). That is, the cooling medium flowing within the cooling channels 14 can remove some heat, while another portion of heat (i.e., net generated heat) still accumulates within the housing 121. However, during the continuous operation of the motor 1, the temperature of the permanent magnet 122 under this other portion of heat (i.e., net generated heat) will not exceed the demagnetization temperature of the permanent magnet 122.

[0126] This design prevents the permanent magnet 122 from overheating, allowing it to engage with the winding assembly 112 for an extended period. This ensures that the motor 1 provides at least the required thrust for the current operating condition and operates at that thrust for at least the target duration. This enhances the functionality of the suspension system 300, enabling it to consistently provide sufficient thrust to the vehicle body 1000 under various operating conditions, and sustain that thrust for a sufficient duration, thus improving the vehicle's stability. Furthermore, the motor 1 can stop operating after a sufficient duration under different thrust conditions, preventing overheating and potential damage.

[0127] It should be noted that the thrust generated by motor 1 on vehicle body 100 is a linear thrust. Since the direction of relative motion between fixed component 11 and moving component 12 is the axis of center rod 111, the direction of thrust generated by motor 1 on vehicle body 100 is also along the axis of center rod 111, that is, the height direction of vehicle 1000.

[0128] In some embodiments, referring to Figures 6 and 8, the central rod 111 includes a first rod segment 111A and a second rod segment 111B. The second rod segment 111B is located inside the housing 121, and the first rod segment 111A passes through a second mounting hole 1211 on the housing 121 and is slidable within the second mounting hole 1211. A portion of the first rod segment 111A is located outside the housing 121, and the upper support assembly 2 is connected to the first rod segment 111A. The winding assembly 112 is connected to the second rod segment 111B and is disposed around the second rod segment 111B.

[0129] Referring to Figures 6 and 9, the cooling channel 14 is located within the center rod 111. At least a portion of the cooling channel 14 overlaps with the winding assembly 112 along the radial direction of the center rod 111.

[0130] By setting a cooling channel 14 inside the center rod 111, the cooling medium flows in the cooling channel 14 and exchanges heat with the winding assembly 112 during the continuous operation of the motor 1 under different thrusts, thereby removing the heat generated by the winding assembly 112 during operation. This prevents the permanent magnet 122 from heating up too quickly and ensures that the temperature of the permanent magnet 122 does not exceed the demagnetization temperature during the continuous operation of the motor 1, thus ensuring that the motor 1 can continue to operate under different thrusts for a longer period of time and increasing the functionality of the suspension system 300.

[0131] In some embodiments, the projection of the cooling channel 14 radially onto the central rod 111 is a first projection, and the length of the first projection along the axial direction of the central rod 111 is not less than the length of the winding assembly 112. This results in a longer cooling channel 14, allowing the cooling medium to flow a longer path and for a longer time within the channel, thereby facilitating sufficient heat exchange with the winding assembly 112 and improving the heat dissipation effect on the winding assembly 112. This ensures that the motor 1 can provide greater thrust and sustain this thrust for a longer duration under different thrust levels.

[0132] In some examples, the cooling channel 14 extends axially along the central rod 111. In other examples, the cooling channel 14 is arranged in a spiral shape around the central rod 111. In still other examples, the cooling channel 14 may also be arranged in a wavy shape.

[0133] In some embodiments, the projection of the winding assembly 112 in the radial direction of the central rod 111 is a second projection. The overlap of the first projection and the second projection in the radial direction of the central rod 111, along the axial direction of the central rod 111, is the overlap length. The overlap length is equal to the axial length of the second projection in the central rod 111. That is, the two ends of the first projection in the axial direction of the central rod 111 are respectively located on both sides of the winding assembly 112 in the axial direction of the central rod 111.

[0134] In this way, the cooling medium can exchange heat with the entire winding assembly 112 during the flow of the cooling channel 14 along the axial direction of the central rod 111, thereby increasing the heat exchange area between the cooling medium and the central rod 111, improving the heat dissipation effect on the winding assembly 112, ensuring that the motor 1 can provide a larger thrust and can maintain it for a longer period of time under different thrusts.

[0135] In some embodiments, the maximum duration of continuous operation of motor 1 decreases as the overlap length decreases. That is, the less the first projection of cooling channel 14 overlaps with the second projection of winding assembly 112 along the radial direction of center rod 111, the smaller the heat exchange area between cooling medium and winding assembly 112, and the lower the heat exchange efficiency, which leads to a shorter maximum duration of continuous operation of motor 1.

[0136] Conversely, the more the first projection of the cooling channel 14 overlaps with the second projection of the winding assembly 112 along the radial direction of the central rod 111, the larger the heat exchange area between the cooling medium and the winding assembly 112, and the higher the heat exchange efficiency, which in turn leads to a longer maximum continuous operating time of the motor 1.

[0137] Therefore, the overlap length of the first projection and the second projection in the radial direction of the central rod 111 can be set according to actual needs so that the heat exchange capacity between the cooling medium and the winding assembly 112 meets the thrust requirements of the motor 1.

[0138] In some embodiments, referring to Figures 9, 10, and 11, the cooling channel 14 includes an inlet channel 141, an outlet channel 142, and a confluence channel 143. The inlet channel 141 extends from the side surface of the first rod segment 111A opposite to the second rod segment 111B to the end of the second rod segment 111B opposite to the first rod segment 111A. The outlet channel 142 extends from the side surface of the first rod segment 111A opposite to the second rod segment 111B to the end of the second rod segment 111B opposite to the first rod segment 111A. The confluence channel 143 is located at the end of the second rod segment 111B opposite to the first rod segment 111A and connects the inlet channel 141 and the outlet channel 142.

[0139] In this way, the cooling medium enters the confluence channel 143 from the inlet channel 141, then enters the outlet channel 142 from the confluence channel 143, and finally flows out from the outlet channel 142. Since the winding assembly 112 is located on the second rod segment 111B, the cooling medium can exchange heat with the entire winding assembly 112 during its flow in the inlet channel 141 and the outlet channel 142 along the axial direction of the central rod 111, thereby improving the heat exchange efficiency between the cooling medium and the winding assembly 112.

[0140] In some embodiments, there are multiple water inlet channels 141. These multiple water inlet channels 141 are spaced apart circumferentially along the central rod 111. This allows the cooling medium within the multiple water inlet channels 141 to exchange heat with the winding assembly 112, thereby increasing the heat exchange area between the cooling medium and the winding assembly 112 and improving heat exchange efficiency.

[0141] In some embodiments, the number of water outlet channels 142 is also multiple. Multiple water outlet channels 142 are arranged at circumferential intervals along the central rod 111. In this way, the cooling medium within the multiple water outlet channels 142 can exchange heat with the winding assembly 112, thereby increasing the heat exchange area between the cooling medium and the winding assembly 112 and improving heat exchange efficiency.

[0142] In some embodiments, referring to FIG11, the confluence channel 143 extends circumferentially along the central rod 111. This facilitates the convergence of cooling media within the multiple inlet channels 141 within the confluence channel 143 before flowing out into the outlet channel 142. It also facilitates the dispersion of the cooling media within the confluence channel 143 into the multiple outlet channels 142 for further flow.

[0143] In some embodiments, under different operating conditions of the vehicle 1000, the thrust provided by the motor 1 to the vehicle body 100 is not less than the required thrust corresponding to the current operating condition, and under the required thrust corresponding to the current operating condition, the maximum duration for which the motor 1 continues to work is not less than the target duration. The target duration is the shortest duration for which the motor 1 continues to work with the required thrust corresponding to the current operating condition to complete the current operating condition. The maximum duration for which the motor 1 continues to work is the maximum duration for which the temperature of the permanent magnet 122 corresponding to the net heat generated by the motor 1 continuing to work under the required thrust corresponding to the current operating condition is maintained at no more than the demagnetization temperature of the permanent magnet 122. The thrust provided by the motor 1 to the vehicle body 100 increases with the increase of the impact degree of the road surface on the vehicle body 100.

[0144] The thrust provided by motor 1 to vehicle body 100 is not less than the thrust required for the current working condition, and the maximum duration of continuous operation of motor 1 under the required thrust for the current working condition is not less than the target duration. In other words, the thrust provided by motor 1 to vehicle body 100 can meet the thrust required for the current working condition. Furthermore, during the process of vehicle 1000 completing the current working condition, the temperature of permanent magnet 122 corresponding to the net heat generated by motor 1 is always lower than the demagnetization temperature of permanent magnet 122. Therefore, permanent magnet 122 will not demagnetize, thereby enabling motor 1 to continuously maintain the thrust until the vehicle completes the current working condition.

[0145] Furthermore, under the current operating conditions, the thrust provided by motor 1 to the vehicle body 100 increases with the increase in the impact of the road surface on the vehicle body 100. In other words, as the impact force of the road surface on the vehicle body increases, the thrust provided by motor 1 to the vehicle body also increases accordingly to meet the thrust requirements of the vehicle body under the corresponding impact force, thus ensuring the vehicle body remains stable under the corresponding impact force. Moreover, since the maximum continuous operating time of motor 1 is not less than the target time, the thrust provided by motor 1 to the vehicle body is also sufficient to ensure that the corresponding impact force on the vehicle body disappears. This ensures that motor 1 can continuously maintain vehicle body stability even when the impact force of the road surface on the vehicle body 100 is constantly changing, improving the driving experience.

[0146] In some embodiments, when the vehicle is in a first operating condition, the thrust of the motor is not less than a first threshold F1, and the duration of continuous operation of the motor is not less than T1. The first threshold F1 and T1 are configured to reduce the impact on the vehicle when it is in the first operating condition, which includes the condition of the vehicle passing through an undulating road surface.

[0147] When the vehicle is in the second operating condition, the thrust of the motor is not less than the second threshold F2, and the duration of continuous operation of the motor is not less than T2. ​​The second threshold F2 and T2 are configured to reduce the degree of body roll of the vehicle when it is in the second operating condition, which includes the condition of the vehicle turning.

[0148] When the vehicle is in the third operating condition, the thrust of the motor is not less than the third threshold F3, and the duration of continuous operation of the motor is not less than T3. The third threshold F3 and T3 are configured to reduce the pitch of the vehicle along the X direction when the vehicle is in the third operating condition. The third operating condition includes the vehicle start-stop condition.

[0149] Among them, F1 > F2 > F3, and T1 < T2 < T3.

[0150] For example, when vehicle 1000 is in the first operating condition, the thrust of motor 1 is not less than the first threshold F1, and the duration of continuous operation of motor 1 is not less than T1. When vehicle 1000 is in the second operating condition, the thrust of motor 1 is not less than the second threshold F2, and the duration of continuous operation of motor 1 is not less than T2. ​​When vehicle 1000 is in the third operating condition, the thrust of motor 1 is not less than the third threshold F3, and the duration of continuous operation of motor 1 is not less than T3. When vehicle 1000 is in the fourth operating condition, the thrust of motor 1 is not less than the fourth threshold F4, and the duration of continuous operation of motor 1 is not less than T4; the road conditions in the fourth operating condition are better than those in the third operating condition. Wherein, F1 > F2 > F3 > F4, and T1 < T2 < T3 < T4.

[0151] It should be noted that the road conditions in the first working condition have a greater impact on the wheels, mainly manifested in the Z-axis effect on the vehicle body 100, such as the step-like road impacts caused by speed bumps and manhole covers. In this case, the suspension motor 1 needs to apply a significant active thrust to the vehicle body 100 to overcome the step-like acceleration tendency of the unsprung mass caused by the impact of this condition. Furthermore, the duration of the continuous thrust generated by motor 1 on the vehicle body 100 each time it operates is relatively short compared to other working conditions. For example, F1 = 6000N, T1 = 5s. That is to say, in the first working condition, the thrust generated by motor 1 on the vehicle body 100 is no less than 6000N, and this thrust value increases significantly with the increase of the amplitude of the step-like road obstacle and the increase of vehicle speed.

[0152] For example, when vehicle 1000 travels at 20 km / h over speed bumps with heights of 3cm, 4cm, 5cm, and 6cm, the required active thrust will increase with the increase in speed bump height. For example, the thrust could be 6000N, 6100N, 6200N, 6300N, 6400N, or 6500N. If encountering consecutive speed bumps, motor 1 will maintain thrust F1 for at least 5 seconds, for example, 5s, 6s, 7s, 8s, 9s, or 10s, until vehicle 1000 leaves the current area.

[0153] The road conditions in the second operating condition have a smaller impact on the wheels, mainly affecting the Y-axis of the vehicle body, such as turning at intersections in urban areas or S-curves on mountain roads in national highways. When vehicle 1000 is traveling in the second operating condition, without active control, vehicle body 100 will experience significant body roll. At this time, motor 1 of suspension system 300 needs to generate thrust on vehicle body 100 to suppress body roll and control the body roll angle of vehicle body 100 within the target range under this operating condition, ensuring the stability of vehicle body 100. At this time, motor 1 needs to provide a large thrust to vehicle 1000 to ensure the stability of vehicle body 100. The specific thrust needs to be determined based on the total mass of the vehicle, the turning radius under this operating condition, the current driving speed, and the target value for body roll angle control.

[0154] For example, under the conditions of a vehicle with a total mass of approximately 3000 kg, a turning radius of 20 meters, and a speed of 60 km / h, when vehicle 1000 makes a fixed-circle turn, F2 = 4000 N. T2 = 5 min. That is to say, under the second operating condition, the thrust generated by motor 1 on vehicle body 100 is no less than 4000 N, and this thrust value will increase significantly as the turning radius decreases and the vehicle speed increases. For example, the thrust can be 4000 N, 4100 N, 4200 N, 4300 N, 4400 N, 4500 N, 5000 N, etc. Furthermore, the duration of motor 1 under thrust F2 is no less than 5 min, for example, the duration can be 5 min, 6 min, 7 min, 8 min, 9 min, 10 min, etc. For example, F2 < 6000 N.

[0155] The road conditions in the third operating condition have a smaller impact on the wheels, mainly affecting the Z-axis of the vehicle body. Examples include undulating surfaces on expressways or national highways, and the pitching of vehicle 1000 during startup or braking. When vehicle 1000 is traveling in the third operating condition, without active control, the vehicle body 100 will experience significant vertical bouncing. At this time, the motor 1 of the suspension system 300 needs to generate thrust on the vehicle body 100 to reduce its sway and maintain stability. Compared to the first and second operating conditions, the swaying amplitude of the vehicle body 100 is smaller in this condition, and the required thrust is also relatively smaller. The winding assembly 112 generates relatively less heat, and the duration of the thrust is also shorter.

[0156] For example, F3 = 1500N. T3 = 15min. That is, under the third operating condition, the thrust generated by motor 1 on the vehicle body 100 is no less than 1500N, for example, the thrust can be 1500N, 1600N, 1700N, 1800N, 1900N, 2000N, etc. Furthermore, the duration of motor 1 under thrust F3 is no less than 15min, for example, the duration can be 15min, 16min, 17min, 18min, 19min, 20min, etc. For example, F3 < 4000N.

[0157] The road conditions in the fourth operating condition have minimal impact on the wheels, primarily affecting the Z-axis of the vehicle body. This applies to relatively flat sections of urban roads, expressways, national highways, and expressways. This condition constitutes the majority of the vehicle 1000's driving conditions. When the vehicle 1000 is in the fourth operating condition, without active control, the vertical bouncing of the vehicle body 100 in the Z-axis direction is minimal. The road surface undulation height in the fourth operating condition is less than in the third operating condition. The amplitude of the vehicle 1000's swaying during driving is also less than that in the third operating condition. Therefore, the thrust required by the vehicle body 100 is less. The winding assembly 112 generates less heat, and the temperature of the permanent magnet 122 generally does not exceed the demagnetization temperature, allowing the motor 1 to operate continuously.

[0158] For example, F4 = 0N, T4 = 30min. This means that under the condition of suppressing body roll 100, the thrust generated by motor 1 on body 100 is not less than 0N. For example, the thrust can be 10N, 50N, 100N, 200N, 300N, 400N, etc. Furthermore, the duration of motor 1 under thrust F4 is not less than 30min. For example, the duration can be 35min, 36min, 37min, 38min, 39min, 40min, etc. For example, F4 < 1500N. Motor 1 can operate continuously.

[0159] In some embodiments, the relationship between the net heat generation of motor 1, the heat generation of motor 1, and the heat carried away by the cooling medium is as follows:

[0160] in, E is the net heat generated by motor 1. g q represents the heat generated by motor 1. c ρ is the heat carried away by the cooling medium, v is the volume of the cooling channel 14, c is the specific heat capacity of the cooling medium, T is the temperature of motor 1, and t is the cooling time. ∞ R is the temperature of the cooling medium, and R is the thermal resistance of motor 1.

[0161] The above formula shows the relationship between the temperature of motor 1 and cooling time when different cooling media are used, given a fixed volume of cooling channel 14. Therefore, at least one of the flow rate or temperature of the cooling medium can be controlled based on this relationship to ensure that the cooling rate of the cooling medium is greater than the heating rate of motor 1. This minimizes the net heat generation of motor 1, preventing the temperature of permanent magnet 122 from exceeding its demagnetization temperature, and ensuring that motor 1 can maintain a large thrust for a longer period under different thrust conditions.

[0162] In some embodiments, referring to Figure 12, the relationship between the thrust of motor 1 and the maximum duration of continuous operation of motor 1 is: y = kx n

[0163] Where y is the maximum duration of continuous operation of motor 1, x is the thrust of motor 1, k and n are constants, with k being a positive number and n being a negative number.

[0164] In other words, the maximum continuous operating time of motor 1 has a negative exponential relationship with the thrust of motor 1. The greater the thrust, the shorter the maximum continuous operating time of motor 1. In this way, motor 1 can have different upper limits for continuous operating time under different thrusts, so that motor 1 stops working when the upper limit is reached, thus avoiding overheating due to prolonged continuous operation and preventing damage to motor 1.

[0165] Furthermore, the duration of continuous operation of motor 1 under different thrusts also has a lower limit. If the duration of continuous operation of motor 1 under different thrusts exceeds the lower limit, motor 1 can meet the needs of vehicle 1000 under different operating conditions. This allows motor 1 to handle multiple operating conditions without being damaged due to overheating.

[0166] In some embodiments, the projection of the cooling channel 14 along the radial direction of the central rod 111 is a first projection, and the projection of the winding assembly 112 is a second projection. The overlap of the first and second projections in the radial direction of the central rod 111 has a length along the axial direction of the central rod 111 called the overlap length. k decreases as the overlap length decreases, and n decreases as the overlap length decreases. Conversely, k increases as the overlap length increases, and n increases as the overlap length increases.

[0167] It should be noted that different thrusts provided by motor 1 to the vehicle body 100 correspond to different amounts of heat generation. That is, the thrust of motor 1 is directly related to the heat generation of motor 1 and the current in the winding assembly 112. For example: F = KI, Q = I * IRT. Where F is the thrust, I is the current, K is the current constant; Q is the heat generation, R is the thermal resistance of motor 1, and T is the temperature of motor 1. It is evident that the thrust of motor 1 is positively correlated with the current, and the heat generation is also positively correlated with the current; that is, the greater the thrust of motor 1, the greater the current required, and the greater the heat generation of motor 1.

[0168] As the overlap length decreases, the heat exchange area between the cooling medium and the winding assembly 112 decreases, resulting in a reduction in heat exchange efficiency. Therefore, by decreasing both k and n as the overlap length decreases, a more reasonable maximum duration of continuous operation of the motor 1 under different thrusts can be achieved, preventing the motor 1 from being damaged due to prolonged continuous operation under high heat generation.

[0169] In some embodiments, to reduce the heat generation of the winding assembly 112, the coil 1122 may include three-phase conductors, each with a cross-sectional area greater than or equal to 2.5 square millimeters and less than or equal to 3.5 square millimeters. For example, the cross-sectional area of ​​each phase conductor may be 2.5 square millimeters, 2.8 square millimeters, 3.0 square millimeters, 3.2 square millimeters, 3.4 square millimeters, 3.5 square millimeters, etc., and the cross-section is a section perpendicular to the length direction of the conductor.

[0170] The length of each phase conductor shall not be less than the first length, which is greater than or equal to 28 meters and less than or equal to 42 meters. For example, the length of each phase conductor can be 28 meters, 30 meters, 32 meters, 34 meters, 36 meters, 38 meters, 40 meters, 42 meters, etc.

[0171] By controlling the cross-sectional area and length of each phase conductor of coil 1122 within the above range, the thickness and length of the conductor can be within a suitable range to ensure that the winding assembly 112 can work normally and generate relatively little heat, thereby improving the heat dissipation efficiency of motor 1 and avoiding the permanent magnet 122 from heating up too quickly, so that motor 1 can provide greater thrust and can continue for a longer period of time under different thrust.

[0172] In some embodiments, the resistance of each phase conductor is no greater than 0.5 ohms. For example, the resistance of each phase conductor can be 0.2 ohms, 0.25 ohms, 0.3 ohms, 0.35 ohms, 0.4 ohms, 0.45 ohms, 0.5 ohms, etc.

[0173] The resistance of each phase conductor is no more than 0.5 ohms, which can reduce the resistance of each phase conductor, thereby reducing the heat generated by the winding assembly 112, so that the motor 1 can provide greater thrust and can continue for a longer period of time under different thrust.

[0174] In some embodiments, the motor 1 serves as both a power element and an actuating element. That is, the motor 1 is configured to both power the suspension system 300 and adjust the distance between the vehicle body 100 and the wheels 200.

[0175] In some embodiments, the motion component 12 is formed as an actuating element, and the motion component 12 and the fixed component 11 cooperate to form a power element.

[0176] In some examples, the housing 121 and the lower wishbone 13 are formed as actuating elements, and the permanent magnet 122 and the winding assembly 112 are formed as power elements. That is, the permanent magnet 122 and the winding assembly 112 cooperate to provide power to the housing 121 and the lower wishbone 13, thereby providing power to the suspension system 300 so that the housing 121 and the lower wishbone 13, as actuating elements of the suspension system 300, push the vehicle body 100 relative to the wheel 200, thereby adjusting the distance between the vehicle body 100 and the wheel 200.

[0177] In this way, the housing 121 and the lower wishbone 13 serve both as components supporting the permanent magnet 122 and the fixed assembly 11 in the motor 1, and as components configured in the suspension system 300 to adjust the distance between the wheel 200 and the vehicle body 100, thus reducing the number of components in the suspension system 300. Compared to a suspension system 300 that adjusts the distance between the wheel 200 and the vehicle body 100 through primary and secondary transmissions, by having the motor 1 act as both a power element and an actuator, the thrust transmission path can be reduced, and energy loss due to intermediate transmission efficiency can be minimized, enabling the motor 1 to provide greater thrust.

[0178] Furthermore, the suspension system 300 has fewer parts, which means it occupies less space, thus reducing unsprung mass, unnecessary work, thrust loss, and thrust control precision.

[0179] It should be noted that the traditional first and second stage transmission suspension system 300 usually transmits power from the motor 1 to the suspension arm through the linkage structure, then to the spring, and finally to the body 100. This results in a long power transmission path for the motor 1, which can easily cause a large thrust loss.

[0180] In other examples, the motor 1 provided in some embodiments of this disclosure can also be used in suspension systems 300 such as MacPherson strut suspension, double wishbone suspension, and five-link suspension.

[0181] In some embodiments, the mating gap between the moving component 12 and the stationary component 11 is formed as an electromagnetic gap. For example, a permanent magnet 122 is disposed around the winding component 112, and there is a gap between the permanent magnet 122 and the winding component 112, which is an electromagnetic gap. By providing an electromagnetic gap, the magnetic field of the permanent magnet 122 can interact better with the magnetic field of the winding component 112, so that the motor 1 can generate sufficient thrust on the vehicle body 100.

[0182] In some embodiments, to detect the relative displacement between the fixed component 11 and the moving component 12 for precise adjustment of the distance between the vehicle body 100 and the wheel 200, referring to Figures 13 and 14, the motor 1 also includes a sensor 15. The sensor 15 is configured to detect the relative displacement between the fixed component 11 and the moving component 12. The sensor 15 includes a read head 151 and a magnetic strip 152. One of the read head 151 and the magnetic strip 152 is disposed on the moving component 12, and the other is disposed on the fixed component 11. The read head 151 is capable of sensing the magnetic field signal of the magnetic strip 152 to detect the relative displacement between the fixed component 11 and the moving component 12.

[0183] Some embodiments of this disclosure are illustrated by way of example, with a reader 151 disposed on the motion assembly 12 and a magnetic strip 152 disposed on the fixed assembly 11.

[0184] In some embodiments, the read head 151 is connected to the housing 121. For example, the read head 151 can be connected to the surface of the housing 121 that mates with the center rod 111. That is, the read head 151 is connected to the outer surface of the top wall of the housing 121, which is the side wall of the housing 121 facing away from the wheel 200. Since the winding assembly 112 and other components of the motor 1 generate heat during operation, and this heat accumulates inside the housing 121, connecting the read head 151 to the surface of the housing 121 that mates with the center rod 111 avoids exposing the read head 151 to a high-temperature environment, thus preventing the read head 151 from overheating and affecting its performance. Furthermore, the read head 151 being located on the surface of the housing 121 that mates with the center rod 111 allows for natural heat dissipation through the flow of outside air, further reducing the temperature of the read head 151.

[0185] In some embodiments, the magnetic strip 152 is connected to the central rod 111. For example, the magnetic strip 152 is disposed on the first segment 111A of the central rod 111. The sensing surface of the reading head 151 faces the magnetic strip 152. By reading the magnetic field signals at different positions on the magnetic strip 152 through the sensing surface of the reading head 151, the relative displacement between the fixed component 11 and the moving component 12 can be detected.

[0186] In some examples, please refer to Figure 15, the center rod 111 has a mounting groove 111C, and the magnetic strip 152 is disposed in the mounting groove 111C. For example, the mounting groove 111C is disposed on the outer peripheral surface of the first rod segment 111A of the center rod 111.

[0187] In this way, the magnetic strip 152 can be limited by the mounting slot 111C to prevent the magnetic strip 152 from shifting downward or falling off under its own weight. This makes the connection of the magnetic strip 152 on the central rod 111 more stable, thereby improving the stability of the cooperation between the reading head 151 and the magnetic strip 152, and thus improving the detection accuracy of the sensor 15.

[0188] In some examples, sensor 15 also includes a back plate 153. The back plate 153 is disposed within a mounting groove 111C, and a magnetic strip 152 is disposed on the surface of the back plate 153 facing the read head 151. That is, both the back plate 153 and the magnetic strip 152 are disposed within the mounting groove 111C. The mounting groove 111C limits the back plate 153, thereby limiting the magnetic strip 152. The back plate 153 also supports and fixes the magnetic strip 152, improving the stability of the magnetic strip 152 on the central rod 111, thereby improving the detection accuracy of sensor 15.

[0189] In some examples, the magnetic strip 152 may be adhesively attached to the back plate 153. In other examples, the magnetic strip 152 is detachably connected to the back plate 153. For example, the magnetic strip 152 may be snap-fitted to the back plate 153 or connected by bolts. This facilitates the removal of the magnetic strip 152 from the back plate 153 for replacement or repair.

[0190] In some examples, the back plate 153 can be connected to the center rod 111 by means of adhesive bonding, snap-fitting, screwing, etc.

[0191] In other examples, at least a portion of the back plate 153 is interference-fitted with the inner wall of the mounting groove 111C. That is, the back plate 153 may be integrally interference-fitted with the inner wall of the mounting groove 111C, or it may be partially interference-fitted with the inner wall of the mounting groove 111C.

[0192] For example, a portion of the back plate 153 is interference-fitted with the inner wall of the mounting groove 111C. This reduces the force required to install the back plate 153 into the mounting groove 111C, facilitating its installation. Furthermore, after installation, only a portion of the back plate 153 is subjected to pressure from the inner wall of the groove, reducing the overall pressure and preventing deformation or damage. This improves the support provided by the back plate 153 to the magnetic strip 152, thereby enhancing the detection accuracy of the sensor 15.

[0193] For example, the two sides of the back plate 153 along the direction perpendicular to the axial direction of the housing 121 respectively abut against the two inner wall surfaces of the mounting groove 111C in the direction perpendicular to the axial direction of the central rod 111, and the two sides of the back plate 153 along the axial direction of the housing 121 are spaced apart from the two inner wall surfaces of the mounting groove 111C along the axial direction of the central rod 111.

[0194] For example, referring to Figure 16, the back plate 153 includes a body portion 1531, a first mating portion 1532, and a second mating portion 1533. A magnetic strip 152 is connected to the body portion 1531. The first mating portion 1532 and the second mating portion 1533 are respectively connected to the two ends of the body portion 1531 in a second direction. Both the first mating portion 1532 and the inner wall surface of the mounting groove 111C, and the second mating portion 1533 and the inner wall surface of the mounting groove 111C, are interference-fitted. The second direction is perpendicular to the arrangement direction of the back plate 153 and the magnetic strip 152. For example, the second direction can be the radial direction of the center rod 111.

[0195] By setting a first mating part 1532 and a second mating part 1533, and making the first mating part 1532 and the inner wall surface of the mounting groove 111C interference fit, and making the second mating part 1533 and the inner wall surface of the mounting groove 111C interference fit, the back plate 153 is partially interference fit with the center rod 111, which facilitates the installation of the back plate 153 and the center rod 111.

[0196] The first mating part 1532 and the second mating part 1533 can be located at the end of the main body 1531 facing the vehicle body 100, or at the end of the main body 1531 facing away from the vehicle body 100. The location of the first mating part 1532 and the second mating part 1533 is not limited here.

[0197] In some examples, the first mating portion 1532 may be a protrusion protruding from the body portion 1531. The second mating portion 1533 may also be a protrusion protruding from the body portion 1531.

[0198] In some examples, the magnetic strip 152 can be a magnetic grating ruler, and the reading head 151 can be a magnetic head. The magnetic grating ruler and the magnetic head form a magnetic induction sensor 15. For example, referring to Figure 17, the magnetic grating ruler includes a plurality of first magnetic poles 1521 and a plurality of second magnetic poles 1522. It should be noted that the polarities of the first magnetic poles 1521 and the second magnetic poles 1522 are different. For example, if the first magnetic pole 1521 is the N pole, then the second magnetic pole 1522 is the S pole; if the first magnetic pole 1521 is the S pole, then the second magnetic pole 1522 is the N pole.

[0199] For example, the first magnetic pole 1521 can be a current-carrying coil 1122, an electromagnet, a magnet, a permanent magnet, etc. The second magnetic pole 1522 can be a current-carrying coil 1122, an electromagnet, a magnet, a permanent magnet, etc.

[0200] Multiple first magnetic poles 1521 and multiple second magnetic poles 1522 are alternately arranged along the axial direction of the central rod 111. That is, a second magnetic pole 1522 is arranged between any two adjacent first magnetic poles 1521, and a first magnetic pole 1521 is arranged between any two adjacent second magnetic poles 1522. Along the axial direction of the central rod 111, the dimensions of the first magnetic poles 1521 and the second magnetic poles 1522 are the same.

[0201] When the central rod 111 moves relative to the housing 121, the magnetic scale and the magnetic head also move relative to each other. The magnetic head can detect the magnetic field strength at different positions on the magnetic scale and process the magnetic field strength to obtain a displacement signal, thereby detecting the relative displacement between the moving component 12 and the fixed component 11.

[0202] In some embodiments, in order to ensure that the motor 1 can provide sufficient thrust to the vehicle body 100, the resistance of the suspension system 300 can be less than 150N. For example, the resistance of the suspension system 300 can be 145N, 140N, 135N, 130N, 125N, 120N, 100N, 90N, 80N, etc.

[0203] By controlling the resistance of the suspension system 300 within a small range, the energy loss caused by the system resistance during the operation of the motor 1 can be reduced, so that the motor 1 can use more energy to provide thrust to the vehicle body 100, thus ensuring that the motor 1 can provide sufficient thrust to the vehicle body 100.

[0204] In some embodiments, referring further to FIG6, the motion assembly 12 also includes a guide rod 123. The center rod 111 and the guide rod 123 are nested together to form a guide assembly. For example, the center rod 111 has a guide hole 111D extending axially along the center rod 111, and at least a portion of the guide rod 123 is located within the guide hole 111D. During relative movement between the fixed assembly 11 and the motion assembly 12, the guide rod 123 can slide relative to the center rod 111 within the guide hole 111D to guide the fixed assembly 11 and the motion assembly 12. The axial direction of the guide rod 123 is aligned with the axial direction of the center rod 111.

[0205] The guiding stiffness of the guide assembly shall not be less than 7767 N / mm. For example, the guiding stiffness of the guide assembly can be 7767 N / mm, 7780 N / mm, 7800 N / mm, 7900 N / mm, 8000 N / mm, 8200 N / mm, 8500 N / mm, etc.

[0206] It should be noted that during the relative movement of the fixed component 11 and the moving component 12, the magnetic field of the permanent magnet 122 and the magnetic field of the winding component 112 will generate magnetic bias force on the fixed component 11 and the moving component 12. That is, the moving component 12 will be offset radially along the central rod 111 under the action of the magnetic bias force, which will cause the guide rod 123 and the central rod 111 to be relatively eccentric, that is, the axes do not coincide.

[0207] The air gap tolerance between the fixed component 11 and the moving component 12 is typically 1-0.083 mm. The resulting basic eccentricity (i.e., the eccentricity caused by the machining errors of the guide rod 123 and the center rod 111) is 0.097 mm. The eccentricity of the motor 1 during operation is typically required to be within ±0.2 mm; therefore, the stiffness deformation of the guide component must be less than or equal to 0.103 mm (i.e., 0.2 mm - 0.097 mm). Given that the magnetic force corresponding to an eccentricity of 0.2 mm is 800 N, the guiding stiffness of the guide component must be greater than or equal to 7767 N / mm (i.e., 800 N divided by 0.103 mm).

[0208] With the guiding stiffness of the guide component within the above range, it can be ensured that the guide component has a large stiffness. During the relative movement of the fixed component 11 and the moving component 12, the guide component is not easy to deform, thereby reducing the system resistance caused by the deformation of the guide component and reducing the energy loss caused by the system resistance.

[0209] In some embodiments, the guide diameter of the guide rod 123 is not less than 23 mm. For example, the diameter of the guide rod 123 can be 23 mm, 24 mm, 25 mm, 26 mm, 27 mm, 28 mm, 29 mm, 30 mm, etc. By keeping the guide diameter of the guide rod 123 within the above range, the rigidity of the guide rod 123 can be avoided due to its excessive thinness, thereby preventing deformation of the guide rod 123 and reducing system resistance.

[0210] In some embodiments, the elastic modulus of both the guide rod 123 and the center rod 111 is not less than 200 GPa. For example, the elastic modulus of the guide rod 123 can be 200 GPa, 210 GPa, 220 GPa, 230 GPa, 240 GPa, 250 GPa, 260 GPa, 270 GPa, 280 GPa, etc. The elastic modulus of the center rod 111 can be 200 GPa, 210 GPa, 220 GPa, 230 GPa, 240 GPa, 250 GPa, 260 GPa, 270 GPa, 280 GPa, etc.

[0211] By setting the elastic modulus of both the guide rod 123 and the center rod 111 within the aforementioned range, the stiffness of the guide rod 123 and the center rod 111 can be enhanced, thereby reducing the deformation of the guide rod 123 and the center rod 111 and reducing the system resistance.

[0212] In some embodiments, referring to Figures 6, 18, and 19, the guide rod 123 includes a rod body 1231 and a base 1232. The first end of the rod body 1231 is nested with the center rod 111, and the base 1232 is connected to the second end of the rod body 1231 and detachably connected to the lower fork arm 13. For example, the base 1232 and the lower fork arm 13 can be connected by snap-fit, screw connection, or other methods.

[0213] Referring to Figure 20, the thickness of the base 1232 (thickness H1 as shown in Figure 20) along the axial direction of the rod 1231 is not less than 3 mm. For example, the thickness of the base 1232 can be 3 mm, 3.2 mm, 3.5 mm, 3.8 mm, 4 mm, 4.2 mm, 4.5 mm, 4.8 mm, 5 mm, etc. The thickness of the base 1232 refers to the maximum dimension of the base 1232 along the axial direction of the central rod 111.

[0214] By setting the thickness of the base 1232 within the aforementioned range, the base 1232 can provide better support for the rod 1231 of the guide rod 123, thereby preventing the guide rod 123 from deforming due to insufficient support strength of the base 1232 for the rod 1231, and thus avoiding excessive system resistance.

[0215] Furthermore, the detachable connection between the base 1232 and the lower fork arm 13 facilitates the disassembly and installation of the guide rod 123. Moreover, the base 1232 and the lower fork arm 13 are separate structures, allowing the guide rod 123 and the lower fork arm 13 to be made of different materials. For example, the guide rod 123 can be made of a material with higher structural strength, while the lower fork arm 13 can be made of a material with relatively lower structural strength. This ensures the structural strength of the guide rod 123 while reducing the weight of the motor 1.

[0216] In some examples, the guide rod 123 is made of a first material, and the lower fork arm 13 is made of a second material. The density of the first material is not less than the density of the second material. That is, the guide rod 123 and the lower fork arm 13 can be made of the same material or different materials.

[0217] For example, both the guide rod 123 and the lower fork arm 13 are made of aluminum alloy. Alternatively, the guide rod 123 may be made of carburized steel, and the lower fork arm 13 may be made of aluminum alloy. The guide rod 123 and the lower fork arm 13 may also be made of other materials that meet the structural strength requirements of the motor 1, which will not be specifically described here.

[0218] In some embodiments, referring to Figures 21 and 22, the motion assembly 12 further includes a bearing assembly 113. The bearing assembly 113 is disposed within the guide hole 111D and is located between the inner wall surface of the guide hole 111D and the guide rod 123.

[0219] Referring to Figures 22 and 23, the bearing assembly 113 includes a cylindrical bearing housing 1131 and a plurality of balls 1132. The bearing housing 1131 is disposed within a guide hole 111D and fixed to a central rod 111. The plurality of balls 1132 are embedded in the bearing housing 1131 and are rotatable relative to the bearing housing 1131. A guide rod 123 passes through the bearing housing 1131 and rolls with the plurality of balls 1132.

[0220] With the arrangement of multiple balls 1132, during the relative movement of the guide rod 123 and the center rod 111, the multiple balls 1132 of the bearing assembly 113 can roll relative to the guide rod 123 on the circumferential surface of the guide rod 123. In this way, compared with sliding friction, the frictional force between the guide rod 123 and the balls 1132 is relatively small, thereby reducing the system resistance when the motor 1 is working, and thus reducing the energy loss caused by resistance.

[0221] In some embodiments, referring to Figures 24 and 25, the guide rod 123 is provided with a guide groove 1233. The guide groove 1233 is recessed from the peripheral wall surface of the guide rod 123 toward the axis of the guide rod 123 and extends along the axial direction of the guide rod 123. A portion of the ball bearing 1132 is located within the guide groove 1233 and rolls into contact with the guide groove 1233.

[0222] By providing a guide groove 1233 on the guide rod 123, during the relative movement of the guide rod 123 and the center rod 111, the balls 1132 of the bearing assembly 113 can roll within the guide groove 1233 to guide the balls 1132. This ensures that the guide rod 123 and the center rod 111 can move relative to each other along the axial direction of the center rod 111, thus avoiding deviation during the relative movement of the guide rod 123 and the center rod 111, which would increase the system resistance and reduce energy loss caused by resistance.

[0223] In some embodiments, the cross-section of the guide groove 1233 is arc-shaped, and the arc shape matches the ball 1132. The cross-section of the guide groove 1233 is perpendicular to the axial direction of the guide rod 123.

[0224] By setting the cross-section of the guide groove 1233 to an arc shape that matches the ball 1132, the ball 1132 can make line contact with the inner wall surface of the guide groove 1233. This reduces the contact stress between the ball 1132 and the inner wall surface of the guide groove 1233, thereby reducing the friction between the ball 1132 and the guide rod 123. Furthermore, reducing the contact stress between the ball 1132 and the inner wall surface of the guide groove 1233 also reduces wear between the ball 1132 and the guide rod 123, thus improving service life.

[0225] In some embodiments, the coefficient of friction of the inner wall surface of the guide groove 1233 is less than or equal to 0.05. For example, the coefficient of friction of the inner wall surface of the guide groove 1233 can be 0.02, 0.025, 0.03, 0.035, 0.04, 0.045, 0.05, etc. This results in a lower coefficient of friction on the inner wall surface of the guide groove 1233, which reduces the friction between the ball 1132 and the guide rod 123, thereby reducing system resistance.

[0226] In some embodiments, referring to FIG25, the plurality of balls 1132 includes multiple groups of balls 1132. That is, the plurality of balls 1132 can be divided into multiple groups. The multiple groups of balls 1132 are arranged at intervals along the circumference of the guide rod 123. For example, the multiple groups of balls 1132 can be a first group of balls 1132, a second group of balls 1132, a third group of balls 1132, ..., an Nth group of balls 1132, where N is greater than or equal to 2. The first group of balls 1132, the second group of balls 1132, the third group of balls 1132, ..., the Nth group of balls 1132 are arranged at intervals along the circumference of the guide rod 123.

[0227] For example, the number of balls 1132 in each group can be one or more. When the number of balls 1132 in each group is more than one, the balls 1132 in each group are arranged along the axial direction of the guide rod 123.

[0228] The guide rod 123 is provided with multiple guide grooves 1233, which are arranged at intervals along the circumference of the guide rod 123. A set of balls 1132 roll in cooperation with one guide groove 1233.

[0229] By arranging multiple sets of balls 1132 along the axial direction of the guide rod 123, and having multiple sets of balls 1132 rollingly engaging with a guide groove 1233, the multiple sets of balls 1132 can rollly engage with the guide rod 123 from multiple positions in the circumferential direction of the guide rod 123, thereby improving the stability of the multiple balls 1132 engaging with the guide rod 123 and reducing system resistance.

[0230] In some embodiments, referring to FIG26, the core 1121 includes a yoke 1121A and a toothed portion 1121B. The yoke 1121A has a first mounting hole 1121C, through which the center rod 111 passes. The toothed portion 1121B is connected to the yoke 1121A and is disposed around the first mounting hole 1121C.

[0231] The teeth 1121B of two adjacent iron cores 1121 define a receiving groove 1123. The coil 1122 is disposed within the receiving groove 1123. The teeth 1121B are configured to support the coil 1122. Both the teeth 1121B and the yoke 1121A are configured as magnetic lines of force to conduct the magnetic field of the coil 1122.

[0232] The core 1121 is made of a magnetically conductive material. For example, the core 1121 may be made of ferrite, ferrosilicon, or silicon steel.

[0233] In some embodiments, referring to FIG27, the toothed portion 1121B may include a plurality of separately arranged support members 1121D. The plurality of support members 1121D are arranged circumferentially along the yoke portion 1121A and connected to the yoke portion 1121A. The circumferential direction of the yoke portion 1121A coincides with the circumferential direction of the first mounting hole 1121C. For example, the support members 1121D and the yoke portion 1121A can be connected by snap-fit, welding, screwing, bonding, or other methods.

[0234] By setting the toothed portion 1121B as multiple separately arranged support members 1121D, and then connecting the multiple support members 1121D through the yoke portion 1121A, the structure of the iron core 1121 can be made simpler, and easier to process and assemble.

[0235] For example, the support member 1121D can be a plate-like structure, a sheet-like structure, a block-like structure, etc. The yoke 1121A can be a ring-like structure, a cylindrical structure, etc.

[0236] In some embodiments, the tooth 1121B further includes an insulating element. An insulating element is provided between any two adjacent support members 1121D.

[0237] In some examples, the insulating element can be an insulating coating. For example, the sides of any two adjacent support members 1121D facing each other are respectively the first side and the second side. The insulating coating is provided on at least one of the first side and the second side. For example, the insulating coating is provided on the first side. Or, the insulating coating is provided on the second side. Or, both the first side and the second side are provided with insulating coatings. For example, the insulating coating can be an insulating varnish coating, an insulating adhesive coating, etc.

[0238] In other examples, the insulating element can also be an insulating sheet. For example, the insulating element can be a plastic sheet, a rubber sheet, a silicone sheet, etc.

[0239] By setting an insulator between any two adjacent support members 1121D, when the magnetic field lines of the coil 1122 are conducted on the multiple support members 1121D on the iron core 1121, the insulator can break the eddy currents generated by the magnetic field lines. This can break the large eddy currents generated by the magnetic field lines into smaller eddy currents, thereby reducing the eddy current loss of the iron core 1121 and improving the working performance of the motor 1 so that the motor 1 can generate sufficient thrust to the vehicle body 100.

[0240] It should be noted that the magnetic field lines generated by the coil 1122 after it is energized will be conducted within the iron core 1121 to enhance the strength of the induced magnetic field. However, the conduction of magnetic field lines within the iron core 1121 will generate large eddy currents, resulting in significant eddy current losses in the iron core 1121, which in turn will affect the working performance of the direct current generator 1.

[0241] It should be noted that the thickness of the insulating component should be as thin as possible to avoid the insulating component occupying too much space between two adjacent support components 1121D, which would result in an excessive reduction in the magnetic permeability of the iron core 1121 and affect the performance of the motor 1.

[0242] In some examples, the tooth 1121B also includes an adhesive. Any two adjacent supports 1121D are bonded together by the adhesive. For example, the adhesive can be epoxy resin adhesive, polyurethane adhesive, silicone rubber, etc.

[0243] By bonding and fixing multiple support members 1121D with adhesive, the stability of the connected support members 1121D can be improved. It should be noted that the thickness of the adhesive should also be as thin as possible to avoid the adhesive occupying too much space between two adjacent support members 1121D, which would lead to an excessive reduction in the magnetic permeability of the iron core 1121 and affect the performance of the motor 1.

[0244] In some examples, the adhesive is made of an insulating material. For example, the adhesive material can be epoxy resin, polyurethane, silicone rubber, etc.

[0245] In this way, the eddy currents generated by the magnetic lines of force in the iron core 1121 can be broken by the adhesive, thereby reducing the eddy current loss of the iron core 1121 and improving the working performance of the motor 1.

[0246] In some examples, referring to Figures 28 and 29, the yoke 1121A has a snap-fit ​​groove 1121E extending circumferentially along the first mounting hole 1121C, the snap-fit ​​groove 1121E being recessed from the outer peripheral surface of the yoke 1121A toward the inner peripheral surface of the yoke 1121A. The support member 1121D has a protrusion 1121F at one end facing the yoke 1121A, protruding axially along the first mounting hole 1121C, the protrusion 1121F engaging within the snap-fit ​​groove 1121E.

[0247] By engaging the protrusions 1121F of multiple support members 1121D into the engaging grooves 1121E of the yoke 1121A, the connection between the support members 1121D and the yoke 1121A can be achieved, which facilitates the connection between the support members 1121D and the yoke 1121A.

[0248] In some examples, the protrusion 1121F can be connected to the surface of the snap-fit ​​groove 1121E by an interference fit.

[0249] In some examples, referring to Figure 30, the thickness of the support member 1121D in the axial direction (thickness H2 shown in Figure 30) gradually decreases along the direction of the support member 1121D toward the yoke 1121A. This reduces the space occupied by the support member 1121D while maintaining the magnetic conductivity of the core 1121, thereby reducing the space occupied by the core 1121 and making the structure of the motor 1 more compact.

[0250] In some embodiments, along the direction of the support member 1121D toward the yoke 1121A, the distance between the two circumferential surfaces of the support member 1121D (the distance L1 shown in FIG. 30) gradually decreases. This reduces the space occupied by the support member 1121D while maintaining the magnetic conductivity of the iron core 1121, thereby reducing the space occupied by the iron core 1121 and making the structure of the motor 1 more compact.

[0251] In some embodiments, referring to FIG31, the core 1121 includes a yoke 1121A and a toothed portion 1121B. The toothed portion 1121B includes a plurality of separately arranged support members 1121D. The plurality of support members 1121D are arranged circumferentially along the yoke 1121A and connected to the yoke 1121A. A first gap is formed between two adjacent support members 1121D.

[0252] By dividing the toothed portion 1121B into multiple support members 1121D, and arranging the multiple support members 1121D separately, the multiple support members 1121D are arranged circumferentially along the yoke portion 1121A, and there is a first gap between any two adjacent support members 1121D. When magnetic lines of force flow in the iron core 1121, the eddy currents generated by the magnetic lines of force can be interrupted by the first gap between the multiple support members 1121D in the circumferential direction of the first mounting hole 1121C. This can break down the larger eddy currents generated by the magnetic lines of force into smaller eddy currents, thereby reducing the eddy current loss of the iron core 1121 and improving the working performance of the motor 1.

[0253] In some examples, the number of support members 1121D can be greater than or equal to 2 and less than or equal to 12. For example, the number of support members 1121D can be 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, etc. In this way, the number of first gaps that can be formed between multiple support members 1121D can effectively reduce the eddy current loss of the iron core 1121, and the number of support members 1121D is also more appropriate, which can reduce the workload of assembling the support members 1121D and the yoke 1121A and improve the assembly efficiency.

[0254] In some examples, the width of the first gap is equal everywhere along the radial direction of the first mounting hole 1121C. That is, the first gap is parallel to the two inner wall surfaces in the circumferential direction of the core 1121. By making the width of the first gap equal everywhere, the first gap can reduce the eddy current loss of the tooth 1121B and also make the tooth 1121B more aesthetically pleasing.

[0255] At this time, the width of the first gap formed between two adjacent support members 1121D (the width M1 shown in Figure 31) can be greater than or equal to 0.1mm. For example, the width of the first gap can be 0.1mm, 0.2mm, 0.3mm, 0.4mm, 0.5mm, 0.6mm, 0.7mm, 0.8mm, 0.9mm, 1mm, etc. In this way, it can be avoided that the width of the first gap between two adjacent support members 1121D is too large, which would affect the thrust density of the motor 1 and thus affect the working performance of the motor 1.

[0256] It should be noted that the thrust density of motor 1 refers to the magnitude of the thrust of motor 1 per unit volume or unit mass.

[0257] In other examples, the width of the first gap gradually increases along the radial direction of the first mounting hole 1121C. This gradual increase in the width of the first gap reduces eddy current losses in the tooth 1121B and also facilitates heat dissipation for the motor 1 through the first gap in the tooth 1121B.

[0258] At this point, the minimum width of the first gap is greater than or equal to 0.1 mm. For example, the minimum width of the first gap can be 0.1 mm, 0.2 mm, 0.3 mm, 0.4 mm, 0.5 mm, 0.6 mm, 0.7 mm, 0.8 mm, 0.9 mm, 1 mm, etc. In this way, it can be avoided that the width of the first gap between two adjacent support members 1121D is too large, which would affect the thrust density of the motor 1 and thus affect the working performance of the motor 1.

[0259] For example, the width of the first gap gradually increases in the direction from the inner edge to the outer edge of the tooth 1121B. At this time, the minimum width of the first gap is the width of the first gap located at the inner edge of the tooth 1121B.

[0260] Alternatively, the width of the first gap gradually increases along the direction from the outer edge to the inner edge of the tooth 1121B. In this case, the minimum width of the first gap is the width of the first gap located at the outer edge of the tooth 1121B.

[0261] After dividing the toothed portion 1121B of the iron core 1121 into multiple support members 1121D, in order to improve the structural strength of the iron core 1121, any two adjacent support members 1121D in the iron core 1121 can be connected. For example, in some embodiments, referring to Figures 32 and 33, one of any two adjacent support members 1121D is provided with a first snap-fit ​​notch 1121G, and the other of any two adjacent support members 1121D is provided with a first snap-fit ​​protrusion 1121H. The first snap-fit ​​protrusion 1121H snaps into the first snap-fit ​​notch 1121G.

[0262] By connecting two adjacent support members 1121D through the first snap-fit ​​protrusion 1121H and the first snap-fit ​​notch 1121G, multiple support members 1121D can support each other, thereby improving the structural strength of the toothed portion 1121B and thus the structural strength of the core 1121. Furthermore, the snap-fit ​​between the first snap-fit ​​protrusion 1121H and the first snap-fit ​​notch 1121G also allows for convenient and quick connection of adjacent support members 1121D, thereby improving the connection efficiency of multiple support members 1121D.

[0263] In some examples, please continue to refer to Figure 33. For one of the support members 1121D, there are two adjacent support members 1121D (i.e., two support members 1121D located on both sides of the first mounting hole 1121C in the circumferential direction of the one support member 1121D). In this case, a first snap-fit ​​notch 1121G can be provided at each end of the one support member 1121D in the circumferential direction of the first mounting hole 1121C, and a first snap-fit ​​protrusion 1121H can be provided at the end of the two adjacent support members 1121D near the one support member 1121D.

[0264] In some other embodiments, adjacent support members 1121D can also be connected in other ways. For example, adjacent support members 1121D can be connected by screwing, welding, or other methods.

[0265] In some examples, the first snap-fit ​​notch 1121G can be a dovetail groove structure, a C-shaped structure, a convex structure, etc. The shape of the first snap-fit ​​protrusion 1121H matches the shape of the first snap-fit ​​notch 1121G.

[0266] In some embodiments, referring to Figures 34 and 35, the yoke 1121A is a split structure. The yoke 1121A includes a plurality of arcuate segments 1121K arranged circumferentially along the first mounting hole 1121C. A second gap is formed between two adjacent arcuate segments 1121K. That is, the yoke 1121A is divided into a plurality of individual arcuate segments 1121K along the circumferential direction of the first mounting hole 1121C.

[0267] In this way, a second gap is formed between any two adjacent arc segments 1121K in the multiple arc segments 1121A of the yoke 1121A. When magnetic lines of force flow in the iron core 1121, the eddy currents generated by the magnetic lines of force in the yoke 1121A can be interrupted by the second gap between the multiple arc segments 1121K. This can break up the larger eddy currents generated by the magnetic lines of force into smaller eddy currents, thereby reducing the eddy current loss of the iron core 1121 and improving the working performance of the motor 1.

[0268] In some examples, the number of arc segments 1121K can be greater than or equal to 2 and less than or equal to 12. For example, the number of arc segments 1121K can be 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, etc. In this way, the number of gaps that can be formed between multiple arc segments 1121K can effectively reduce the eddy current loss of the iron core 1121, and the number of arc segments 1121K is also more appropriate, which can reduce the workload of assembling the iron core 1121 and improve the assembly efficiency.

[0269] In some examples, the width of the second gap is equal everywhere along the radial direction of the first mounting hole 1121C. That is, the second gap is parallel to the two inner wall surfaces of the first mounting hole 1121C in the circumferential direction. By making the width of the second gap equal everywhere, the second gap can both reduce the eddy current loss of the yoke 1121A and make the yoke 1121A more aesthetically pleasing.

[0270] At this point, the width of the second gap between two adjacent arc segments 1121K (width M2 as shown in Figure 35) can be greater than or equal to 0.1mm. For example, the width of the second gap can be 0.1mm, 0.2mm, 0.3mm, 0.4mm, 0.5mm, 0.6mm, 0.7mm, 0.8mm, 0.9mm, 1mm, etc. This avoids the second gap between two adjacent arc segments 1121K being too wide, which would affect the thrust density of motor 1 and thus its performance.

[0271] In other examples, the width of the second gap gradually increases along the radial direction of the first mounting hole 1121C. This gradual increase in the width of the second gap not only reduces eddy current losses in the yoke 1121A but also facilitates heat dissipation for the motor 1 through the second gap in the yoke 1121A.

[0272] At this point, the minimum width of the second gap is greater than or equal to 0.1 mm. For example, the minimum width of the second gap can be 0.1 mm, 0.2 mm, 0.3 mm, 0.4 mm, 0.5 mm, 0.6 mm, 0.7 mm, 0.8 mm, 0.9 mm, 1 mm, etc. This avoids the second gap between two adjacent arc segments 1121K being too wide, which could affect the thrust density of motor 1 and thus its operating performance.

[0273] For example, the width of the second gap gradually increases along the direction from the inner edge to the outer edge of the yoke 1121A. At this time, the minimum width of the second gap is the width of the second gap located at the inner edge of the yoke 1121A.

[0274] Alternatively, the width of the second gap gradually increases along the direction from the outer edge to the inner edge of the yoke 1121A. In this case, the minimum width of the second gap is the width of the second gap located at the outer edge of the yoke 1121A.

[0275] In some examples, an arc segment 1121K is connected to at least one support member 1121D. After two adjacent supports 1121D are connected by a first snap-fit ​​protrusion 1121H and a first snap-fit ​​notch 1121G, multiple arc segments 1121K can be connected together by multiple supports 1121D.

[0276] An arc segment 1121K can be connected to a support member 1121D. An arc segment 1121K can also be connected to multiple support members 1121D. The number of arc segments 1121K can be the same as the number of support members 1121D. The number of arc segments 1121K can also be different from the number of support members 1121D.

[0277] In other examples, a support member 1121D is connected to at least one arc segment 1121K. That is, a support member 1121D can be connected to one arc segment 1121K. A support member 1121D can also be connected to multiple arc segments 1121K.

[0278] To facilitate the installation of multiple arc segments 1121K and multiple support members 1121D, the number of arc segments 1121K can be the same as the number of support members 1121D, and multiple arc segments 1121K correspond one-to-one with multiple support members 1121D, with one arc segment 1121K connected to one support member 1121D.

[0279] Furthermore, to improve the structural strength of the core 1121, in some examples, an arc-shaped segment 1121K and a support member 1121D can be integrally formed, for example, by connecting the arc-shaped segment 1121K and the support member 1121D together through a stamping process. This results in a higher connection strength between the arc-shaped segment 1121K and the support member 1121D. Furthermore, when multiple arc-shaped segments 1121K are connected by multiple support members 1121D, the structural strength of the core 1121 can also be improved.

[0280] In other examples, the arc segment 1121K and the support 1121D can also be connected by snap-fit, screw-fit, welding, or other methods.

[0281] In some other embodiments, referring to Figures 36, 37, and 38, the tooth portion 1121B includes a separately disposed first tooth portion 112A and a second tooth portion 112B. The first tooth portion 112A includes a plurality of first support members 112C spaced circumferentially along the first mounting hole 1121C. The second tooth portion 112B includes a plurality of second support members 112D spaced circumferentially along the first mounting hole 1121C. The plurality of first support members 112C and the plurality of second support members 112D are arranged alternately along the circumferential direction of the first mounting hole 1121C, and a third gap is formed between adjacent first support members 112C and second support members 112D.

[0282] A third gap is formed between the first support member 112C and the second support member 112D. In the circumferential direction of the first mounting hole 1121C, the eddy currents generated by the magnetic lines of force can be interrupted by the third gap, thereby breaking down the larger eddy currents generated by the magnetic lines of force into smaller eddy currents, thereby reducing the eddy current loss of the iron core 1121 and improving the working performance of the motor 1.

[0283] Furthermore, with the provision of the first tooth 112A and the second tooth 112B, when assembling the iron core 1121, it is only necessary to install the first support member 112C of the first tooth 112A between the adjacent second support members 112D of the second tooth 112B along the axial direction of the first mounting hole 1121C, thereby facilitating the assembly of the iron core 1121.

[0284] In some examples, multiple first support members 112C are connected to the outer peripheral surface of the yoke 1121A. In this way, when assembling the core 1121, placing the second support member 112D between adjacent first support members 112C allows the second support member 112D to be located on the outer peripheral surface of the yoke 1121A, thereby forming the teeth 1121B of the core 1121 with the first support members 112C and the second support member 112D, which facilitates the positioning of the core 1121 during assembly.

[0285] For example, multiple first support members 112C and the yoke 1121A are integrally formed. For example, the first support members 112C and the yoke 1121A can be formed into one piece by a stamping process, or they can be directly machined as a single piece during processing. Alternatively, the first support members 112C and the yoke 1121A can also be connected by snap-fitting, bonding, or other methods.

[0286] In some examples, the second support member 112D can be connected to the yoke 1121A by means of snap-fit, adhesive bonding, or other methods. The second support member 112D can also be connected to the first support member 112C by means of snap-fit, adhesive bonding, or other methods.

[0287] In some examples, the inner diameter of the first tooth 112A is the same as the outer diameter of the yoke 1121A, and the inner diameter of the second tooth 112B is the same as the outer diameter of the yoke 1121A. This ensures that after the core 1121 is assembled, the first support 112C and the second support 112D can fit tightly against the yoke 1121A, thus guaranteeing the integrity of the core 1121. Furthermore, it prevents excessive gaps between the second support 112D and the yoke 1121A from affecting the thrust density of the motor 1, thereby ensuring the performance of the motor 1.

[0288] In some examples, the outer diameter of the first support 112C is the same as the outer diameter of the second support 112D.

[0289] It should be noted that the inner diameter of the first support member 112C refers to the distance between the surface of the first support member 112C facing the yoke 1121A and the center of the tooth 1121B. The outer diameter of the first support member 112C refers to the distance between the surface of the first support member 112C facing away from the yoke 1121A and the center of the tooth 1121B. The inner diameter of the second support member 112D refers to the distance between the surface of the second support member 112D facing the yoke 1121A and the center of the tooth 1121B. The outer diameter of the second support member 112D refers to the distance between the surface of the second support member 112D facing away from the yoke 1121A and the center of the tooth 1121B.

[0290] In some embodiments, referring to Figures 39 and 40, the yoke 1121A includes a separately configured first yoke 112E and a second yoke 112F. A plurality of first supports 112C are connected to the first yoke 112E, and a plurality of second supports 112D are connected to the second yoke 112F.

[0291] By dividing the yoke 1121A into a first yoke 112E and a second yoke 112F, and connecting multiple first support members 112C to the first yoke 112E and multiple second support members 112D to the second yoke 112F, the first yoke 112E can connect and support the multiple first support members 112C, and the second yoke 112F can connect and support the multiple second support members 112D. In this way, when assembling the core 1121, the first yoke 112E and the multiple first support members 112C can be assembled as a whole, and the second yoke 112F and the multiple second support members 112D can be assembled as a whole, thus reducing the difficulty of assembly.

[0292] In some examples, multiple first support members 112C and first yoke 112E are integrally formed. For example, the first support members 112C and first yoke 112E can be formed into one piece by a stamping process, or they can be machined as a single piece during processing. Alternatively, the first support members 112C and first yoke 112E can be connected by snap-fitting, bonding, or other methods.

[0293] Multiple second support members 112D and second yoke 112F are integrally formed. For example, the second support members 112D and second yoke 112F can be formed into one piece by a stamping process, or they can be directly machined as a single piece during processing. Alternatively, the second support members 112D and second yoke 112F can also be connected by snap-fitting, bonding, or other methods.

[0294] In some examples, the second yoke 112F is located on one side of the first yoke 112E in the axial direction of the first mounting hole 1121C. For example, the first support 112C is connected to the side of the first yoke 112E facing the second yoke 112F, and the second support 112D is connected to the outer peripheral surface of the second yoke 112F. In this way, after the second yoke 112F is located on one side of the first yoke 112E in the axial direction of the first mounting hole 1121C and is mated with the first yoke 112E, one second support 112D can be located between two adjacent first support 112Cs.

[0295] In some examples, the inner diameter of the first yoke 112E is the same as the inner diameter of the second yoke 112F. This ensures the integrity of the yoke 1121A formed by the mating of the first yoke 112E and the second yoke 112F.

[0296] In some examples, the inner diameter of the first support 112C is the same as the inner diameter of the second support 112D. The outer diameter of the first support 112C is the same as the outer diameter of the second support 112D.

[0297] In some examples, the outer diameter of the first yoke 112E may be greater than the outer diameter of the second yoke 112F. The outer diameter of the first yoke 112E may also be equal to the outer diameter of the second yoke 112F.

[0298] In some embodiments, referring to Figures 41 and 42, a portion of the second yoke 112F passes through the interior of the first yoke 112E. This allows for positioning via the first yoke 112E and the second yoke 112F during the assembly of the core 1121, facilitating its assembly.

[0299] In some examples, the height of the second yoke 112F is greater than the height of the first yoke 112E along the axial direction of the first mounting hole 1121C. That is, the second yoke 112F may include a first portion and a second portion disposed along the axial direction of the first mounting hole 1121C, with the second portion located inside the first yoke 112E and the first portion located outside the first yoke 112E. A second support member 112D may be connected to the outer peripheral surface of the first portion of the second yoke 112F, and a first support member 112C may be connected to the side of the first yoke 112E facing the first portion.

[0300] In some examples, the outer diameter of the second yoke 112F is the same as the inner diameter of the first yoke 112E. This allows the second yoke 112F to fit more tightly with the first yoke 112E, thereby improving the structural integrity of the yoke 1121A.

[0301] In some examples, the inner diameter of the first support 112C is the same as the inner diameter of the first yoke 112E. The inner diameter of the second support 112D is the same as the inner diameter of the first yoke 112E.

[0302] In some embodiments, referring to Figures 43 and 44, the first yoke 112E includes a first annular portion 112G and a plurality of first rib portions 112H. The plurality of first rib portions 112H are connected to the outer peripheral surface of the first annular portion 112G and are arranged at circumferential intervals along the first annular portion 112G.

[0303] The second yoke 112F includes a second annular portion 112K and a plurality of second rib portions 112L. The second annular portion 112K is located on one side of the first annular portion 112G in the axial direction of the first mounting hole 1121C. The plurality of first rib portions 112H and the plurality of second rib portions 112L are arranged alternately along the circumferential direction of the first mounting hole 1121C, and a fourth gap is formed between adjacent first rib portions 112H and second rib portions 112L.

[0304] By providing the first rib 112H and the second rib 112L, multiple fourth gaps can be formed in the yoke 1121A of the iron core 1121. These fourth gaps can break the eddy currents generated by the magnetic lines of force in the yoke 1121A, thereby dispersing the larger eddy currents into smaller ones, thus reducing the eddy current losses in the iron core 1121 and improving the working performance of the motor 1.

[0305] In some examples, multiple first support members 112C are connected to the side surface of the first annular portion 112G facing the second annular portion 112K, and a first rib portion 112H is connected to a first support member 112C. Multiple second support members 112D are connected to the outer peripheral surface of the second annular portion 112K, and a second rib portion 112L is connected to the side surface of a second support member 112D facing the first annular portion 112G in the axial direction of the first mounting hole 1121C.

[0306] In this way, during the assembly of the iron core 1121, it is convenient to alternately arrange multiple first support members 112C and multiple second support members 112D along the circumference of the first mounting hole 1121C, and it is convenient to alternately arrange multiple first rib portions 112H and multiple second rib portions 112L along the axial direction of the first mounting hole 1121C, so as to facilitate the assembly of the iron core 1121.

[0307] In some examples, the inner diameter of the first annular portion 112G is the same as the inner diameter of the second annular portion 112K. In this way, the integrity of the yoke portion 1121A of the core 1121 can be guaranteed after the first annular portion 112G and the second annular portion 112K are assembled, thereby improving the structural strength of the core 1121.

[0308] In some examples, the outer diameter of the first rib 112H is the same as the outer diameter of the second rib 112L. The outer diameter of the first rib 112H is the distance between the surface of the first rib 112H facing away from the first mounting hole 1121C and the center of the yoke 1121A. The outer diameter of the second rib 112L is the distance between the surface of the second rib 112L facing away from the first mounting hole 1121C and the center of the yoke 1121A.

[0309] In some embodiments, referring to FIG45, the toothed portion 1121B further includes a plurality of connecting ribs 112M and a plurality of connecting grooves 112N. Any two adjacent first support members 112C are connected by a connecting rib 112M, and the plurality of second support members 112D are provided with connecting grooves 112N. A connecting rib 112M is engaged within a connecting groove 112N.

[0310] By connecting the connecting rib 112M to the connecting groove 112N, the first support member 112C and the second support member 112D can be connected to make the structure of the iron core 1121 more stable after assembly.

[0311] In some embodiments, referring to FIG46, the toothed portion 1121B further includes a plurality of connecting ribs 112M and a plurality of connecting grooves 112N. Any two adjacent second supports 112D are connected by a connecting rib 112M, and the plurality of first supports 112C are provided with connecting grooves 112N. A connecting rib 112M is engaged within a connecting groove 112N.

[0312] In some embodiments, referring to FIG47, the iron core 1121 is provided with a blocking groove 1124. The blocking groove 1124 is located around the first mounting hole 1121C. In this way, when magnetic lines of force flow in the iron core 1121, the eddy currents generated by the magnetic lines of force in the circumferential direction of the first mounting hole 1121C can be interrupted by the blocking groove 1124, thereby breaking down the larger eddy currents generated by the magnetic lines of force into smaller eddy currents, thereby reducing the eddy current loss of the iron core 1121 and improving the working performance of the motor 1.

[0313] The barrier groove 1124 can extend axially along the first mounting hole 1121C. The barrier groove 1124 can also extend along the inner wall surface of the first mounting hole 1121C towards the outer edge of the iron core 1121. The barrier groove 1124 can also extend circumferentially along the first mounting hole 1121C.

[0314] In some embodiments, the blocking groove 1124 includes a first blocking groove 1124A. The first blocking groove 1124A is disposed in the tooth portion 1121B. In some examples, along the axial direction of the first mounting hole 1121C, the first blocking groove 1124A may be recessed from one side surface of the tooth portion 1121B to the other side surface of the tooth portion 1121B. By providing the first blocking groove 1124A in the tooth portion 1121B, when magnetic lines of force flow through the tooth portion 1121B, the first blocking groove 1124A can break the eddy currents formed by the magnetic lines of force in the tooth portion 1121B, thereby reducing the eddy current losses in the tooth portion 1121B, and further reducing the eddy current losses in the iron core 1121, thereby improving the operating performance of the motor 1.

[0315] The number of first blocking grooves 1124A can be one or more. When there are multiple first blocking grooves 1124A, the multiple first blocking grooves 1124A are arranged at intervals along the circumference of the first mounting hole 1121C. By setting multiple first blocking grooves 1124A, the eddy currents of the tooth 1121B can be interrupted at multiple points, thereby reducing the eddy current loss of the tooth 1121B and thus reducing the eddy current loss of the iron core 1121.

[0316] In some examples, referring to Figure 47, the first blocking groove 1124A extends from the inner edge of the tooth 1121B towards the outer edge of the tooth 1121B. For example, the first blocking groove 1124A may extend radially along the tooth 1121B. The first blocking groove 1124A may also extend in a third direction, parallel to the upper end face of the tooth 1121B, with an angle greater than 0° and less than 90° between the third direction and the radial direction of the tooth 1121B. For example, the angle between the third direction and the radial direction of the tooth 1121B may be 10°, 20°, 30°, 40°, 50°, 60°, 70°, 80°, etc. For example, the first blocking groove 1124A may be a straight groove, a trapezoidal groove, an arc-shaped groove, a wavy groove, or an irregular groove. The radial direction of the tooth 1121B coincides with the radial direction of the first mounting hole 1121C and also with the radial direction of the yoke 1121A.

[0317] By extending the first blocking groove 1124A along the inner edge of the toothed portion 1121B toward the outer edge of the toothed portion 1121B, the first blocking groove 1124A can have a certain length, thereby enabling the first blocking groove 1124A to interrupt more eddy currents and reduce the eddy current loss of the iron core 1121.

[0318] For example, referring to Figure 48, the tooth 1121B is annular, and the first blocking groove 1124A extends radially through the tooth 1121B to its inner edge (position X1 shown in Figure 48). In this way, the eddy currents generated by the magnetic field lines at the inner edge of the tooth 1121B can also be interrupted by the first blocking groove 1124A, thereby reducing the eddy current losses of the iron core 1121. At this time, the first blocking groove 1124A may or may not extend to the outer edge of the tooth 1121B.

[0319] In some examples, the first blocking groove 1124A does not extend to either the outer edge or the inner edge of the tooth 1121B. In this way, the eddy current loss of the core 1121 can be reduced by the first blocking groove 1124A, while the integrity of the tooth 1121B can be maintained, thereby improving the structural strength of the tooth 1121B and thus ensuring the structural strength of the core 1121.

[0320] In some examples, the first barrier groove 1124A extends axially along the tooth 1121B.

[0321] Please refer to Figure 47. The blocking groove 1124 also includes a second blocking groove 1124B. The second blocking groove 1124B is provided in the yoke 1121A. By providing the second blocking groove 1124B in the yoke 1121A, when the magnetic lines of force flow in the yoke 1121A, the second blocking groove 1124B can break the eddy currents formed by the magnetic lines of force in the yoke 1121A, thereby reducing the eddy current losses in the yoke 1121A, and further reducing the eddy current losses in the iron core 1121, so as to improve the working performance of the linear motor 1.

[0322] The number of second blocking grooves 1124B can be one or more. When there are multiple second blocking grooves 1124B, they are spaced apart circumferentially along the first mounting hole 1121C. By setting multiple second blocking grooves 1124B, the eddy currents in the yoke 1121A can be interrupted at multiple points, thereby reducing the eddy current loss in the yoke 1121A and thus reducing the eddy current loss in the core 1121.

[0323] In some examples, referring to Figure 47, the second blocking groove 1124B extends axially along the yoke 1121A. That is, the second blocking groove 1124B extends axially along the first mounting hole 1121C. By extending the second blocking groove 1124B axially along the yoke 1121A, the second blocking groove 1124B can have a certain length in the axial direction of the yoke 1121A, thereby allowing the second blocking groove 1124B to interrupt more eddy currents and reduce eddy current losses in the core 1121. For example, the second blocking groove 1124B can be a straight groove, a trapezoidal groove, an arc groove, a wavy groove, or an irregular groove, etc.

[0324] In some examples, along the axial direction of the yoke 1121A, the second blocking groove 1124B can extend from one side of the yoke 1121A to the other side. This increases the length of the second blocking groove 1124B in the axial direction of the yoke 1121A, thereby reducing the eddy current loss of the core 1121.

[0325] In some examples, the second blocking groove 1124B extends along the inner edge of the yoke 1121A towards the outer edge of the yoke 1121A. For example, the second blocking groove 1124B may extend radially along the yoke 1121A. The second blocking groove 1124B may also extend along a fourth direction parallel to the upper end face of the yoke, with the angle between the fourth direction and the radial direction of the yoke 1121A being greater than 0° and less than 90°. For example, the angle between the fourth direction and the radial direction of the yoke 1121A may be 10°, 20°, 30°, 40°, 50°, 60°, 70°, 80°, etc. The radial direction of the yoke 1121A coincides with the radial direction of the first mounting hole 1121C.

[0326] By extending the second blocking groove 1124B along the direction from the inner edge of the yoke 1121A to the outer edge of the yoke 1121A, the length of the second blocking groove 1124B in the direction from the inner edge of the yoke 1121A to the outer edge of the yoke 1121A can be increased, thereby enabling the second blocking groove 1124B to interrupt more eddy currents and reduce the eddy current loss of the iron core 1121.

[0327] In some examples, the second blocking groove 1124B may extend to the inner edge of the yoke 1121A. In this case, the second blocking groove 1124B may extend to the outer edge of the yoke 1121A, or it may not extend to the outer edge of the yoke 1121A. In other examples, referring to FIG49, the second blocking groove 1124B extends to the outer edge of the yoke 1121A. In this case, the second blocking groove 1124B may extend to the inner edge of the yoke 1121A, or it may not extend to the inner edge of the yoke 1121A413.

[0328] In some examples, the second barrier groove 1124B extends circumferentially along the yoke 1121A.

[0329] In some examples, referring further to Figure 49, the second blocking groove 1124B can communicate with the first blocking groove 1124A. For instance, the first blocking groove 1124A extends to the inner edge of the tooth 1121B, and the second blocking groove 1124B extends axially through the yoke 1121A along the first mounting hole 1121C and radially to the outer edge of the yoke 1121A along the first mounting hole 1121C. Along the extending direction of the first blocking groove 1124A, the projection of the first blocking groove 1124A partially overlaps with the projection of the second blocking groove 1124B, thereby achieving communication between the first blocking groove 1124A and the second blocking groove 1124B.

[0330] In this way, the eddy currents at the connection between the tooth 1121B and the yoke 1121A can also be interrupted by the first blocking groove 1124A and the second blocking groove 1124B, thereby reducing the eddy current loss of the iron core 1121.

[0331] When there are multiple first blocking grooves 1124A and multiple second blocking grooves 1124B, one first blocking groove 1124A is connected to one second blocking groove 1124B.

[0332] Based on the above, referring to Figure 50, in some embodiments, the first blocking groove 1124A extends to the outer edge of the tooth 1121B (position X2 shown in Figure 50) and also extends to the inner edge of the tooth 1121B (position X3 shown in Figure 50). That is, the first blocking groove 1124A extends through the tooth 1121B in the direction from the inner edge to the outer edge. In this way, the length of the first blocking groove 1124A in the direction from the inner edge to the outer edge of the tooth 1121B can be increased, thereby increasing the eddy current region interrupted by the first blocking groove 1124A to reduce the eddy current loss of the core 1121.

[0333] Furthermore, in some other embodiments, referring to FIG51, the first blocking groove 1124A may extend to the outer edge of the tooth 1121B. In this case, the first blocking groove 1124A does not extend to the inner edge of the tooth 1121B.

[0334] In some embodiments, referring to FIG52, the second barrier groove 1124B extends to the inner edge of the yoke 1121A and also extends to the outer edge of the yoke 1121A. That is, the second barrier groove 1124B extends through the yoke 1121A in the direction from the outer edge to the inner edge.

[0335] By extending the second blocking groove 1124B through to the inner edge and outer edge of the yoke 1121A, the size of the second blocking groove 1124B in the direction from the outer edge to the inner edge of the yoke 1121A can be increased, thereby increasing the eddy current region interrupted by the second blocking groove 1124B and reducing the eddy current loss of the iron core 1121.

[0336] In other embodiments, the second barrier groove 1124B does not extend to either the inner or outer edge of the yoke 1121A. This allows for both reduction of eddy current losses in the core 1121 through the second barrier groove 1124B and maintenance of the integrity of the yoke 1121A, thereby improving the structural strength of the yoke 1121A and ultimately ensuring the structural strength of the core 1121.

[0337] In some embodiments, the iron core 1121 is made using a powder metallurgy process.

[0338] In some embodiments, the raw materials for the iron core 1121 include a powdered soft magnetic composite material and an insulating material, with the insulating material coated on the surface of the soft magnetic composite material. In this way, since the material of the iron core 1121 contains insulating material, and the insulating material is coated on the surface of the soft magnetic composite material, the eddy currents generated when magnetic lines of force are conducted on the iron core 1121 can be broken by the insulating material. This disperses the larger eddy currents generated by the magnetic lines of force into smaller eddy currents, thereby reducing the eddy current losses of the iron core 1121 and improving the operating performance of the motor 1.

[0339] In some examples, the soft magnetic composite material can be iron powder or iron-nickel alloy powder, etc. The insulating material can be resin, rubber, etc.

[0340] In some examples, please refer to Figure 53, the iron core 1121 is provided with a rib groove 1125, and a reinforcing member is provided in the rib groove 1125. By providing the rib groove 1125 and providing the reinforcing member in the rib groove 1125, the structure of the iron core 1121 can be strengthened by the reinforcing member, thereby improving the structural strength of the iron core 1121.

[0341] In some examples, the reinforcing member is manufactured using injection molding. That is, the reinforcing member is formed directly within the rib groove 1125 by injection molding. Using injection molding allows the reinforcing member to bond more firmly to the iron core 1121, thereby improving the reinforcing effect. In other examples, the reinforcing member can also be a rod-shaped structural member, a plate-shaped structural member, etc., located within the rib groove 1125.

[0342] In some examples, the rib groove 1125 extends circumferentially along the core 1121. In other examples, the rib groove 1125 extends radially along the core 1121. In still other examples, there are multiple rib grooves 1125, some extending axially along the core 1121 and others extending radially along the core 1121.

[0343] In some examples, the rib groove 1125 is provided in the tooth portion 1121B. In other examples, the rib groove 1125 is provided in the yoke portion 1121A. In still other examples, part of the rib groove 1125 is provided in the tooth portion 1121B, and another part of the rib groove 1125 is provided in the yoke portion 1121A.

[0344] In some examples, referring to Figures 53 to 56, along the axial direction of the core 1121, the core 1121 includes a first surface 1121M and a second surface 1121N. For example, the first surface 1121M includes one side surface of the yoke 1121A along the axial direction of the core 1121 and one side surface of the tooth 1121B along the axial direction of the core 1121. The second surface 1121N includes the other side surface of the yoke 1121A along the axial direction of the core 1121 and the other side surface of the tooth 1121B along the axial direction of the core 1121.

[0345] The ribbed groove 1125 includes a plurality of first ribbed grooves 1125A, a plurality of second ribbed grooves 1125B, and a plurality of third ribbed grooves 1125C. The plurality of first ribbed grooves 1125A are spaced apart circumferentially along the core 1121, and are recessed from the first surface 1121M toward the second surface 1121N. The plurality of second ribbed grooves 1125B are spaced apart circumferentially along the core 1121, and are recessed from the second surface 1121N toward the first surface 1121M. The plurality of third ribbed grooves 1125C are spaced apart circumferentially along the core 1121, and are recessed from the inner circumferential surface of the core 1121 toward the outer circumferential surface.

[0346] By setting the first rib groove 1125A, the second rib groove 1125B and the third rib groove 1125C, the structure of the iron core 1121 can be strengthened at multiple locations, thereby improving the structural strength of the iron core 1121.

[0347] In some examples, the first rib groove 1125A is provided in the tooth portion 1121B. The second rib groove 1125B is provided in the tooth portion 1121B. The third rib groove 1125C is provided in the yoke portion 1121A.

[0348] In some examples, referring to Figures 57 and 58, along the circumference of the core 1121, the first rib groove 1125A includes a first inner wall surface 1125D and a second inner wall surface 1125E. The second rib groove 1125B includes a third inner wall surface 1125F and a fourth inner wall surface 1125G. One first rib groove 1125A corresponds to one second rib groove 1125B. For the corresponding first rib groove 1125A and second rib groove 1125B, along the axial direction of the core 1121, the projection of the second inner wall surface 1125E coincides with the projection of the third inner wall surface 1125F, and along the circumference of the core 1121, the first inner wall surface 1125D and the fourth inner wall surface 1125G are located on both sides of the first inner wall surface 1125D.

[0349] In other words, the corresponding first rib groove 1125A and second rib groove 1125B are offset in the circumferential direction of the iron core 1121, and their inner wall surfaces overlap along the axial direction of the iron core 1121. This allows the corresponding first rib groove 1125A and second rib groove 1125B to be relatively close. After reinforcing members are installed in the first rib groove 1125A and second rib groove 1125B, the iron core 1121 can be structurally strengthened from both sides in the axial direction, thereby improving the structural strength of the iron core 1121.

[0350] Based on this, the rib groove 1125 also includes multiple fourth rib grooves 1125H. The fourth rib grooves 1125H extend axially along the core 1121, and a first rib groove 1125A is connected to a second rib groove 1125B through a fourth rib groove 1125H. In this way, after reinforcing members are installed in the first rib groove 1125A, the second rib groove 1125B, and the fourth rib groove 1125H through injection molding, the reinforcing members in the first rib groove, the second rib groove 1125B, and the fourth rib groove 1125H can be connected together as a whole, thereby enhancing the reinforcing effect and improving the structural strength of the core 1121.

[0351] In some examples, the third rib groove 1125C extends through the core 1121 along its axial direction, and at least one of the first rib groove 1125A and the second rib groove 1125B communicates with the third rib groove 1125C. Thus, after reinforcing members are installed in the first rib groove 1125A, the second rib groove 1125B, and the third rib groove 1125C through injection molding, at least one of the reinforcing members in the first rib groove and the second rib groove 1125B can be connected to the reinforcing member in the third rib groove 1125C to form a whole, thereby enhancing the reinforcing effect and improving the structural strength of the core 1121.

[0352] In some examples, the outer surface of the core 1121 is covered by injection molding. In this way, the reinforcing members in the first rib groove 1125A, the second rib groove 1125B, the third rib groove 1125C, and the fourth rib groove 1125H can be connected into a whole by injection molding on the outer surface of the core 1121, thereby improving the integrity and structural strength of the core 1121.

[0353] In some embodiments, referring to FIG53, the core 1121 further includes a force-bearing member 1125K. The force-bearing member 1125K is disposed within the first mounting hole 1121C and extends circumferentially along the first mounting hole 1121C. The force-bearing member 1125K can support the core 1121 from its inner surface, thereby improving the structural strength of the core 1121.

[0354] In some examples, the load-bearing component 1125K can be a metal ring. For example, the load-bearing component 1125K can be a steel ring, an aluminum ring, an aluminum alloy ring, etc.

[0355] In some examples, along the axial direction of the core 1121, the height of the load-bearing member 1125K is less than the height of the yoke 1121A of the core 1121. This allows the load-bearing member 1125K to be also covered during injection molding of the outer surface of the core 1121, resulting in a tighter fit between the load-bearing member 1125K and the yoke 1121A, thus improving the structural strength of the core 1121.

[0356] In some examples, referring to Figures 59 and 60, a first recess 1125M is formed on the outer peripheral surface of the force-bearing member 1125K. A first protrusion is formed on the inner peripheral surface of the yoke 1121A. The first protrusion is located within the first recess 1125M. In this way, the first recess 1125M can limit the first protrusion, thereby preventing the force-bearing member 1125K from rotating circumferentially relative to the yoke 1121A, thus improving the tightness between the force-bearing member 1125K and the yoke 1121A and improving the structural strength of the core 1121.

[0357] For example, the first recess 1125M may extend along the axial direction of the core 1121. The first protrusion may also extend along the axial direction of the core 1121.

[0358] In some examples, the force-bearing member 1125K has a second recess 1125N formed on one side of the iron core 1121 along the axial direction. A second protrusion is formed on the inner circumferential surface of the yoke 1121A. The second protrusion is located within the second recess 1125N. In this way, the second protrusion can limit the second recess 1125N, thereby preventing the force-bearing member 1125K from rotating circumferentially relative to the yoke 1121A, thus improving the tightness between the force-bearing member 1125K and the yoke 1121A and improving the structural strength of the iron core 1121.

[0359] For example, the second recess 1125N can be a notch provided on the force-bearing member 1125K. The second protrusion can be an injection-molded part. That is, the second protrusion located in the second recess 1125N is formed by injection molding on the iron core 1121.

[0360] In some examples, a third protrusion 1125P is formed on the inner circumferential surface of the force-bearing member 1125K. A third recess is formed on the outer circumferential surface of the center rod 111. The center rod 111 passes through the force-bearing member 1125K, and the third protrusion 1125P is located within the third recess. In this way, the third protrusion 1125P can limit the third recess, thereby preventing the force-bearing member 1125K and the center rod 111 from rotating relative to each other in the circumferential direction, and thus preventing the core 1121 and the center rod 111 from rotating relative to each other in the circumferential direction, thereby improving the stability of the connection between the core 1121 and the center rod 111.

[0361] For example, the third protrusion 1125P may extend along the axial direction of the core 1121. The third recess may also extend along the axial direction of the core 1121.

[0362] In some embodiments, referring to Figures 61 and 62, the plurality of iron cores 1121 include a first end iron core 1126A, a second end iron core 1126B, and a middle iron core 1126C. The middle iron core 1126C is disposed between the first end iron core 1126A and the second end iron core 1126B.

[0363] The first end core 1126A is provided with a first magnetic isolation groove 1126D, which is recessed from the side surface of the first end core 1126A opposite to the second end core 1126B toward the second end core 1126B. The second end core 1126B is provided with a second magnetic isolation groove 1126E, which is recessed from the side surface of the second end core 1126B opposite to the first end core 1126A toward the first end core 1126A.

[0364] By providing a first magnetic isolation groove 1126D at the first end core 1126A and a second magnetic isolation groove 1126E at the second end core 1126B, the magnetic lines of force can form a closed loop at both ends of the winding assembly 112 along the axial direction of the central rod 111 during transmission within the core 1121, returning to the core 1121 along a smaller path. This reduces magnetic leakage, thereby increasing the thrust density of the motor 1 and improving its performance.

[0365] The first magnetic isolation groove 1126D allows the end face of the first end core 1126A to have several end faces with different axial heights, and the second magnetic isolation groove 1126E allows the end face of the second end core 1126B to have several end faces with different axial heights. The phase and magnitude of the magnetic resistance can be adjusted by the staggered height difference and the area of ​​the staggered end faces, thereby reducing the magnetic resistance.

[0366] In some examples, the first magnetic isolation groove 1126D extends circumferentially along the first end core 1126A. The second magnetic isolation groove 1126E extends circumferentially along the second end core 1126B. In this way, the first isolation groove 1124A and the second isolation groove 1124B can allow magnetic lines of force to form closed loops back into the core 1121 at more locations along smaller paths, thereby reducing magnetic leakage.

[0367] In some examples, referring to Figures 63 and 64, a first limiting protrusion 1126F is formed on the inner circumferential surface of the first end core 1126A, and a second limiting protrusion 1126G is formed on the inner circumferential surface of the second end core 1126B. A first limiting groove and a second limiting groove are formed on the outer circumferential surface of the center rod 111, with the first limiting protrusion 1126F located within the first limiting groove and the second limiting protrusion 1126G located within the second limiting groove.

[0368] The engagement of the first limiting protrusion 1126F with the first limiting groove prevents relative rotation between the first end core 1126A and the center rod 111 in the circumferential direction, thus ensuring a more stable fit between the first end core 1126A and the center rod 111. Similarly, the engagement of the second limiting protrusion 1126G with the second limiting groove prevents relative rotation between the second end core 1126B and the center rod 111 in the circumferential direction, further ensuring a more stable fit between the second end core 1126B and the center rod 111.

[0369] In some embodiments, referring to Figures 65 and 66, the core 1121 further includes a first tooth crown 1126H, which is disposed on the outer edge of the tooth portion 1121B and surrounds the tooth portion 1121B. Along the radial direction of the core 1121, the projection of the tooth portion 1121B does not exceed the projection range of the first tooth crown 1126H.

[0370] By setting the first tooth crown 1126H, the width of the outer edge of the receiving groove 1123 in the axial direction of the central rod 111 can be optimized, thereby optimizing the magnetic field distribution, reducing magnetic resistance, and improving the performance of the motor 1.

[0371] For example, the first end core 1126A is provided with a first tooth crown 1126H. This can optimize the magnetic field distribution at the edge of the first end core 1121 and improve the performance of the motor 1.

[0372] For example, the second end core 1126B is provided with a first tooth crown 1126H. This can optimize the magnetic field distribution at the edge of the second end core 1121 and improve the performance of the motor 1.

[0373] For example, the central iron core 1126C is provided with a first tooth crown 1126H, which can optimize the magnetic field distribution at the edge of the central iron core 1126C and improve the performance of the motor 1.

[0374] In some examples, the first crown 1126H protrudes axially along the core 1121 to at least one side of the tooth portion 1121B of the core 1121. That is, the first crown 1126H may protrude to the upper side of the tooth portion 1121B, or to the lower side of the core 1121, or both to the upper and lower side of the tooth portion 1121B.

[0375] In some examples, the first crown 1126H is formed with a first inclined surface 1126M and a second inclined surface 1126N. The first inclined surface 1126M and the second inclined surface 1126N are arranged along the axial direction of the core 1121, and the distance between the first inclined surface 1126M and the second inclined surface 1126N gradually increases along the direction from the outer peripheral surface of the core 1121 to the inner peripheral surface.

[0376] For example, if the first inclined plane 1126M is located above the second inclined plane 1126N, then the upper end of the first inclined plane 1126M is closer to the yoke 1121A of the iron core 1121 than the lower end of the first inclined plane 1126M. Similarly, the lower end of the second inclined plane 1126N is closer to the yoke 1121A of the iron core 1121 than the upper end of the second inclined plane 1126N.

[0377] By setting the first inclined plane 1126M and the second inclined plane 1126N, the magnetic lines of force can be guided to transition more smoothly at the outer edge of the iron core 1121, thereby reducing abrupt changes in the magnetic lines of force and optimizing the magnetic field distribution of the iron core 1121, reducing magnetic resistance, and improving the performance of the motor 1.

[0378] In some embodiments, referring to FIG. 67, the iron core 1121 is provided with a wire passage groove 1127A. The wire passage groove 1127A is recessed from the outer peripheral surface of the iron core 1121 toward the inner peripheral surface, and the wire passage groove 1127A extends through the iron core 1121 along the axial direction. Along the axial direction of the iron core 1121, the projections of the wire passage grooves 1127A of the plurality of iron cores 1121 coincide, so that the wire passage grooves 1127A of the plurality of iron cores 1121 form a wire passage channel 1127B. The wire passage channel 1127B is configured to accommodate the conductor connection segment 1122A of the coil 1122, and the conductor connection segment 1122A is configured to connect adjacent in-phase coils 1122.

[0379] By placing the wire connection segment 1122A of the coil 1122 within the wire passage 1127B, the wire connection segment 1122A can be limited by the wire passage 1127B, improving the positional stability of the wire connection segment 1122A. Furthermore, compared to placing the wire connection segment 1122A outside the iron core 1121, placing it within the wire passage 1127B reduces the space occupied by the wire connection segment 1122A, making the motor 1 more compact.

[0380] It should be noted that since coil 1122 has three-phase conductors, the conductor connection segments 1122A of each phase conductor need to be connected together. Therefore, the number of wire passages 1127B can be three. The three wire passages 1127B are arranged at intervals along the circumference of the iron core 1121. The conductor connection segment 1122A of each phase conductor is located within one wire passage 1127B to avoid mutual interference between the three phase conductors.

[0381] In some embodiments, referring to Figures 68 and 69, the center rod 111 includes a first rod segment 111A and a second rod segment 111B. The winding assembly 112 is connected to the second rod segment 111B. The first rod segment 111A has a lead-out channel 111E. Among the in-phase coils 1122, the coil 1122 closest to the first rod segment 111A includes a lead-out head 1122B. The lead-out head 1122B is disposed within the lead-out channel 111E and is configured to connect the lead-out wire of the winding assembly 112. The lead-out wire passes through the lead-out channel 111E and is configured to connect to a connector.

[0382] With the above configuration, after the wire connection section 1122A of the coil 1122 of the same phase is connected, it extends into the wire outlet channel 111E in the center rod 111 through the wire outlet head 1122B and is connected to the wire outlet wire provided in the wire outlet channel 111E. The wire outlet is connected to the connector to connect to the motor controller or power supply through the connector, so as to facilitate the power supply to the coil 1122 and control the current magnitude and direction of the coil 1122.

[0383] A cable outlet channel 111E is provided inside the center rod 111. The cable outlet channel 111E can limit and protect the cable outlet head 1122B and the cable outlet wire, improve the positional stability of the cable outlet head 1122B and the cable outlet wire, and prevent damage to the cable outlet head 1122B and the cable outlet wire from affecting the performance of the motor 1.

[0384] In some examples, referring further to Figure 69, the cable outlet channel 111E includes a radial hole 111F and an axial hole 111G. The radial hole 111F communicates with the axial hole 111G. The axial hole 111G extends axially along the center rod 111. For example, the axial hole 111G extends from the side surface of the first rod segment 111A facing away from the second rod segment 111B toward the second rod segment 111B. The radial hole 111F extends radially along the center rod 111. For example, the radial hole 111F is located at the end of the first rod segment 111A facing the second rod segment 111B, and extends from the outer circumferential surface of the first rod segment 111A to the inner circumferential surface.

[0385] By providing the axial hole 111G, the outgoing wire can be conveniently placed inside the axial hole 111G, so as to limit and protect the outgoing wire through the axial hole 111G. By providing the radial hole 111F, the outgoing head 1122B of the coil 1122 can easily pass through the radial hole 111F and extend into the axial hole 111G to connect with the outgoing wire.

[0386] In some examples, the cable exit channel 111E is located inside the first pole segment 111A. By placing the cable exit channel 111E inside the first pole segment 111A, the central pole 111 can provide better protection for the cable exit conductor and the cable exit head 1122B.

[0387] In some embodiments, referring to Figures 70 and 71, the motion assembly 12 further includes a first linear bearing 124. The first linear bearing 124 is disposed in the second mounting hole 1211 and connected to the housing 121. The center rod 111 passes through the first linear bearing 124 and is slidably connected to the first linear bearing 124.

[0388] By setting the first linear bearing 124, the relative sliding between the center rod 111 and the housing 121 can be smoother, thereby reducing the system resistance when the motor 1 is working and improving the performance of the motor 1.

[0389] In some embodiments, the motion assembly 12 further includes a first seal 125 and a second seal 126. The first seal 125 is disposed around the inner wall of the second mounting hole 1211 between the first seal 125 and the center rod 111. The second seal 126 is disposed around the inner wall of the second mounting hole 1211 between the second seal 126 and the center rod 111. A first linear bearing 124 is disposed between the first seal 125 and the second seal 126.

[0390] The first seal 125, the second seal 126, the center rod 111, and the inner wall of the mounting hole form a first oil reservoir, which contains lubricating fluid.

[0391] With the above configuration, the first seal 125 and the second seal 126 can seal the lubricant between the center rod 111 and the first linear bearing 124. In this way, during the relative movement of the center rod 111 and the housing 121, the lubricant can lubricate both the center rod 111 and the first linear bearing 124, thereby reducing the friction between them and reducing the system resistance when the motor 1 is operating.

[0392] Furthermore, the lubricant can reduce wear between the center rod 111 and the first linear bearing 124, thereby increasing their service life. Additionally, the lubricant supply structure is relatively simple, facilitating the assembly of the various components of the motor 1.

[0393] In some examples, the housing 121 is provided with an oil filling hole 1212. The oil filling hole 1212 extends from the outer wall of the housing 121 into the first oil reservoir. The moving assembly 12 also includes a sealing member 127. The sealing member 127 is detachably connected to the oil filling hole 1212.

[0394] By providing an oil filling hole 1212 and a sealing member 127 detachably connected to the oil filling hole 1212, the sealing member 127 can be easily installed and removed from the oil filling hole 1212, thereby facilitating the replacement of the lubricating fluid in the first oil reservoir through the oil filling hole 1212 to ensure the lubricating performance of the lubricating fluid in the first oil reservoir.

[0395] In some examples, the plug 127 can be a screw plug. In other examples, the plug 127 can also be a component such as a rubber plug that can seal the oil filling hole 1212.

[0396] In some examples, the first seal 125 is a lip seal. The first seal 125 is located on the side of the first linear bearing 124 opposite to the lower fork arm 13. For example, referring to Figure 71, the sealing bracket 128 is located on the outside of the housing 121 and is detachably connected to the top wall of the housing 121. For example, the sealing bracket 128 can be connected to the top wall by means of screws, snap-fits, etc.

[0397] A portion of the first seal 125 is disposed between the top wall and the sealing bracket 128. The sealing bracket 128 and the top wall can clamp the first seal 125 from both sides, thereby fixing the first seal 125 to the housing 121. In this way, the installation of the first seal 125 is carried out outside the housing 121, which is not limited by space and facilitates the installation of the first seal 125.

[0398] In some examples, referring to Figure 72, the first seal 125 includes an annular sealing portion 1251 and a support portion 1252. The inner circumferential surface of the annular sealing portion 1251 contacts the central rod 111. For example, the central rod 111 passes through the annular sealing portion 1251 and abuts against the inner wall surface of the annular sealing portion 1251.

[0399] The support portion 1252 is connected to the outer peripheral surface of the annular sealing portion 1251 and is disposed around the annular sealing portion 1251. The support portion 1252 is located between the top wall and the sealing bracket 128. For example, the support portion 1252 can surround the annular sealing portion 1251. The arrangement of the annular sealing portion 1251 and the support portion 1252 facilitates the fixing of the first sealing member 125 by the sealing bracket 128, and enables the first sealing member 125 to seal the gap between the center rod 111 and the inner wall surface of the second mounting hole 1211.

[0400] The annular sealing part 1251 can also be a cylindrical, elliptical, or irregularly shaped cylindrical structure, or a circular, elliptical, or irregularly shaped annular sheet structure. The only requirement is that it can seal the gap between the center rod 111 and the inner wall of the second mounting hole 1211.

[0401] In some examples, the support portion 1252 may be a sheet-like structure. In other examples, the radial cross-section of the support portion 1252 may be square, circular, elliptical, etc., and the radial cross-section passes through the axis of the support portion 1252.

[0402] In some other examples, referring to Figure 73, the annular sealing portion 1251 has a first sealing end 1251A and a second sealing end 1251B at its two axial ends. Along the axial direction of the annular sealing portion 1251, a support portion 1252 is located between the first sealing end 1251A and the second sealing end 1251B.

[0403] In other words, along the axial direction of the annular sealing portion 1251, the annular sealing portion 1251 extends to both sides of the support portion 1252. This enhances the structural strength of the first sealing element 125, and when the central rod 111 slides relative to the first sealing element 125, portions of the annular sealing portion 1251 on both sides of the support portion 1252 in the axial direction of the first sealing element 125 rub against the central rod 111, thereby reducing excessive axial wobble of the annular sealing portion 1251 and improving the sealing effect.

[0404] In some examples, a portion of the annular sealing part 1251 is located within the second mounting hole 1211 and contacts the inner wall surface of the second mounting hole 1211. This allows for a sealing cap to cover the gap between the center rod 111 and the inner wall surface of the second mounting hole 1211, improving the sealing effect.

[0405] In some examples, as shown in FIG74, when the annular seal 1251 is in a free state (i.e., when the first seal 125 is not installed on the housing 121), the distance between the inner circumferential surface of the annular seal 1251 and the axis of the annular seal 1251 (the vertical dashed line shown in FIG74) along the axial direction of the annular seal 1251 (the distance L3 shown in FIG74) first increases and then decreases.

[0406] In other words, the inner edge of the radial section of the annular seal 1251 is an arc, with the concave side of the arc facing the axis of the annular seal 1251. Alternatively, the inner edge of the radial section of the annular seal 1251 can be two intersecting line segments, with the angle formed by the intersection of the two line segments facing the axis of the annular seal 1251. The radial section of the annular seal 1251 passes through the axis of the annular seal 1251.

[0407] By first increasing and then decreasing the distance between the inner circumferential surface of the annular sealing part 1251 and the axis of the annular sealing part 1251, the annular sealing part 1251 is more likely to deform when it abuts against the center rod 111, thereby making the annular sealing part 1251 fit more tightly against the center rod 111 and improving the sealing effect of the annular sealing part 1251.

[0408] In some embodiments, referring to FIG75, the sealing bracket 128 includes a main body 1281 and a connecting portion 1282. The main body 1281 is located on the side of the support portion 1252 facing away from the top wall. The main body 1281 contacts the surface of the support portion 1252 facing away from the top wall, thereby clamping the support portion 1252 from both sides through the main body 1281 and the top wall to fix the support portion 1252 to the housing 121.

[0409] The connecting part 1282 is connected to the main body 1281 and also to the housing 121. For example, the connecting part 1282 is a flange structure, and the connecting part 1282 is provided with a plurality of bolt holes spaced apart circumferentially along the first sealing member 125. The connection between the connecting part 1282 and the housing 121 is achieved by bolts passing through the bolt holes and being screwed to the top wall.

[0410] For example, the connecting part 1282 can also be a snap-fit ​​structure. For example, the connecting part 1282 is a snap-fit ​​protrusion provided around the main body 1281. The connecting part 1282 is snapped into the snap-fit ​​groove on the top wall to realize the connection between the connecting part 1282 and the housing 121.

[0411] As shown in Figures 76 and 77, the sealing bracket 128 and the first sealing element 125 are viewed from both sides along the axial direction of the first sealing element 125, respectively.

[0412] The connecting portion 1282 is disposed around the supporting portion 1252. That is, the supporting portion 1252 is located inside the connecting portion 1282. And the annular sealing portion 1251 is located between the sealing bracket 128 and the central rod 111. In this way, the connecting portion 1282 can cover the supporting portion 1252, thereby allowing the sealing bracket 128 to cover the first sealing element 125, thus protecting the first sealing element 125 and preventing it from being leaked and damaged.

[0413] Furthermore, the connecting part 1282 can directly contact and connect with the top wall to reduce the gap between the sealing bracket 128 and the top wall and improve the aesthetics of the motor 1.

[0414] In some other examples, the first seal 125 may also be a seal of other structures such as a sealing ring.

[0415] In some examples, the second seal 126 can be a sealing ring, a lip seal, etc.

[0416] In some embodiments, referring to Figures 70 and 78, the central rod 111 has a guide hole 111D extending axially along the central rod 111. A guide rod 123 is located inside the housing 121, and at least a portion of the guide rod 123 is located within the guide hole 111D. The fixing assembly 11 also includes a second linear bearing 114, which is disposed in the guide hole 111D and connected to the central rod 111. The guide rod 123 passes through the second linear bearing 114 and is slidably connected to the second linear bearing 114.

[0417] By setting the second linear bearing 114, the relative sliding between the center rod 111 and the guide rod 123 can be smoother, thereby reducing the system resistance when the motor 1 is working and improving the performance of the motor 1.

[0418] In some examples, the second linear bearing 114 can be the structure of the bearing assembly 113 described above, or it can be a cylindrical linear bearing structure.

[0419] In some embodiments, referring to Figures 70 and 78, a second oil reservoir 111M is formed between the guide rod 123 and the inner wall surface of the guide hole 111D, and the second oil reservoir 111M contains lubricating fluid. For example, the second oil reservoir 111M may include a gap between the guide rod 123 and the inner wall surface of the central rod 111 along the radial direction of the central rod 111, and a portion of the space of the guide hole 111D located on the side of the guide rod 123 opposite to the lower fork arm 13.

[0420] The fixing assembly 11 also includes a third seal 115. The third seal 115 is disposed around the inner wall of the guide hole 111D and between it and the guide rod 123. The second linear bearing 114 is located on the side of the third seal 115 facing the second oil reservoir 111M. That is, the third seal 115 is located on the side of the second linear bearing 114 facing the lower fork arm 13.

[0421] In this way, the lubricant can enter the gap between the second linear bearing 114 and the guide rod 123. When the guide rod 123 moves relative to the center rod 111, the lubricant can lubricate the second linear bearing 114 and the guide rod 123 to reduce the friction between the guide rod 123 and the second linear bearing 114, thereby reducing the system resistance when the motor 1 is working.

[0422] Furthermore, the lubricant can reduce wear between the guide rod 123 and the second linear bearing 114, thereby increasing their service life. In addition, the aforementioned lubricant supply structure is relatively simple and compact, facilitating the assembly of the various components of the motor 1 and contributing to the compactness of the motor 1.

[0423] In some embodiments, referring to FIG79, the suspension system 300 further includes an upper support assembly 2 and a buffer body 3. The upper support assembly 2 is disposed outside the housing 121 and connected to the center rod 111, and the upper support assembly 2 is connected to the vehicle body 100. The buffer body 3 is connected to the side of the upper support assembly 2 facing the housing 121.

[0424] In other words, the buffer body 3 is located between the upper support assembly 2 and the housing 121. This allows the housing 121 to contact the buffer body 3 when the fixed assembly 11 and the moving assembly 12 move relative to each other to their compression limit position (i.e., the fixed assembly 11 and the moving assembly 12 move relative to each other to their limit position), thereby compressing the buffer body 3 and limiting and cushioning the housing 121. When the fixed assembly 11 and the moving assembly 12 move in opposite directions, the compressed buffer body 3 returns to its original position. Thus, the buffer body 3 can buffer the impact of the road surface, improving the comfort of the vehicle 1000.

[0425] In some examples, the buffer 3 can be a buffer structure made of flexible materials such as rubber or latex.

[0426] In some embodiments, referring to Figures 80 and 81, the upper support assembly 2 includes an outer bracket 22 and a connecting assembly 23. The outer bracket 22 is provided with a mounting space 221 and a first clearance hole 222. For example, the mounting space 221 may be recessed into the housing 121 from the side surface of the outer bracket 22 facing away from the housing 121. The first clearance hole 222 may extend from the side surface of the outer bracket 22 facing the housing 121 into the mounting space 221 to communicate with the mounting space 221.

[0427] The center rod 111 passes through the first clearance hole 222, and the buffer body 3 is connected to the side of the outer bracket 22 facing the housing 121. The connecting assembly 23 is provided in the installation space 221 and connects the outer bracket 22 and the center rod 111.

[0428] By integrating the buffer body 3 onto the outer bracket 22 of the upper support assembly 2, the overall structure of the buffer body 3 and the upper support assembly 2 can be simplified. Furthermore, when installing the buffer body 3 and the upper support assembly 2, they can be connected as a whole to the central rod 111, thus facilitating their installation.

[0429] In some examples, the buffer body 3 and the outer support 22 are an integral structure. For instance, the buffer body 3 and the outer support 22 can be formed into an integral structure through a vulcanization process. This makes the connection between the buffer body 3 and the outer support 22 more stable.

[0430] In some examples, the buffer body 3 is spaced apart from the center rod 111. In this way, during the relative movement of the center rod 111 and the housing 121, the buffer body 3 and the center rod 111 will not rub against each other, thereby reducing the frictional resistance caused by the buffer body 3 to the center rod 111 and improving the performance of the motor 1.

[0431] In some embodiments, referring to FIG82, the connecting assembly 23 includes an inner sleeve 231, a fastener 232, a cover plate 233, and a fourth seal 234. The inner sleeve 231 is connected to the outer bracket 22 and is disposed around the central rod 111. The fastener 232 is disposed on the side of the inner sleeve 231 opposite to the housing 121 and is threadedly connected to the central rod 111. The inner sleeve 231 is configured to support the fastener 232 to improve the stability of the connection between the fastener 232 and the central rod 111.

[0432] For example, the fastener 232 can be a nut, the center rod 111 has an external thread, the fastener 232 is sleeved on the center rod 111 and threadedly connected to the center rod 111.

[0433] For example, the inner sleeve 231 can be made of flexible materials such as rubber or plastic. Furthermore, the inner sleeve 231 also possesses a certain degree of rigidity to support the fastener 232.

[0434] The cover plate 233 is located on the side of the inner bushing 231 facing away from the housing 121 and is arranged around the fixing member 232. The cover plate 233 is connected to the outer bracket 22. The fourth sealing member 234 is connected between the cover plate 233 and the fixing member 232.

[0435] By providing a fourth sealing element 234 between the cover plate 233 and the fixing element 232, the fourth sealing element 234 can seal the gap between the cover plate 233 and the fixing element 232, thereby preventing external impurities from entering the installation space 221 of the outer bracket 22. This prevents impurities from affecting components such as the inner bushing 231 in the installation space 221, thus ensuring the stability of the motor 1 during operation.

[0436] In some examples, the fourth seal 234 is capable of radial expansion and contraction along the cover plate 233. For example, the fourth seal 234 may be made of an elastic material such as rubber or latex. In this way, when the fourth seal 234 is subjected to tensile force, the fourth seal 234 can undergo elastic deformation, thereby preventing damage to the fourth seal 234.

[0437] In some examples, the fourth seal 234 is an annular corrugated plate, and the corrugated portion of the fourth seal 234 extends circumferentially along the cover plate 233. The radial section of the fourth seal 234 is corrugated, and the radial section passes through the axis of the fourth seal 234.

[0438] At this time, the material of the fourth seal 234 may include at least one of rubber, plastic, asbestos, and metal. For example, the fourth seal 234 may be made of elastic materials such as rubber or latex, or it may be made of materials such as plastic or asbestos, or it may be made of metals such as aluminum, iron, copper, aluminum alloy, or stainless steel. For example, part of the fourth seal 234 may be made of rubber, and another part may be made of plastic.

[0439] Because the fourth seal 234 is annularly corrugated, it can expand and contract when subjected to tension, thereby preventing damage to the fourth seal 234.

[0440] In some embodiments, referring further to FIG82, the suspension system 300 also includes a fifth seal 4. The fifth seal 4 is disposed around the inner wall of the inner bushing 231 and between the center rod 111.

[0441] In this way, the gap between the inner wall of the inner bushing 231 and the center rod 111 can be sealed by the fifth sealing element 4, thereby preventing impurities from entering the installation space 221 from the gap between the inner wall of the inner bushing 231 and the center rod 111 and affecting the motor 1, so as to improve the working performance of the motor 1.

[0442] In some examples, the fifth seal 4 can be a sealing ring.

[0443] In some embodiments, referring to FIG83, the center rod 111 is provided with a socket 111N. For example, the socket 111N may coincide with the cable outlet channel 111E within the center rod 111.

[0444] The fixing assembly 11 also includes a connector 116 and at least one sixth seal 117. The connector 116 is configured to connect the lead wire of the winding assembly 112, and a portion of the connector 116 is received within a socket 111N. In this way, the connector 116 can be limited through the socket 111N to facilitate connection of the connector 116 to the center rod 111.

[0445] For example, the connector 116 and the center rod 111 can be connected by snap-fit, screw connection or other methods.

[0446] At least one sixth seal 117 is disposed around the inner wall of the socket 111N and between it and the connector 116. That is, the portion of the connector 116 extending into the socket 111N passes through the sixth seal 117, and the sixth seal 117 abuts against both the portion of the connector 116 extending into the socket 111N and the inner wall of the socket 111N. This seals the gap between the portion of the connector 116 extending into the socket 111N and the inner wall of the socket 111N, thereby preventing external impurities from entering the socket 111N and protecting the outgoing wire.

[0447] In some examples, the number of sixth seals 117 can be one or more. When there are multiple sixth seals 117, they are spaced apart along the axial direction of the center rod 111. Providing multiple sixth seals 117 enables multi-stage sealing of the gap between the portion of the connector 116 extending into the insertion hole 111N and the inner wall of the insertion hole 111N, thereby improving the sealing effect.

[0448] Furthermore, even if one of the sixth seals 117 is damaged, the gap between the portion of the connector 116 that extends into the socket 111N and the inner wall of the socket 111N can be sealed.

[0449] In some examples, the second sealing structure is also a sealing ring.

[0450] In some embodiments, referring to Figures 3 and 84, the suspension system 300 further includes a dust sleeve 5. The dust sleeve 5 is sleeved on the outside of the housing 121, and the first end of the dust sleeve 5 is connected to the upper support assembly 2, the second end of the dust sleeve 5 is connected to the housing 121, and the dust sleeve 5 is capable of extending and retracting along the axial direction of the housing 121.

[0451] The dustproof sleeve 5 can isolate impurities outside the dustproof sleeve 5, preventing impurities from entering the gap between the inner wall of the second mounting hole 1211 and the center rod 111, and preventing impurities from entering the housing 121 through the gap between the inner wall of the second mounting hole 1211 and the center rod 111. This allows the center rod 111 to slide more smoothly and stably relative to the housing 121, and ensures the working performance of the motor 1.

[0452] During the operation of motor 1, the housing 121 slides relative to the central rod 111 and the upper support assembly 2, which generates tensile or compressive forces on the dustproof sleeve 5. To prevent the dustproof sleeve 5 from being damaged by tensile or compressive forces, the dustproof sleeve 5 can be made to extend and retract along the axial direction of the housing 121.

[0453] For example, the dustproof sleeve 5 can be made of elastic materials such as rubber or latex. In this way, when the housing 121 slides relative to the central rod 111 and the upper support assembly 2, the dustproof sleeve 5 can undergo elastic deformation under force, thereby preventing damage to the dustproof sleeve 5.

[0454] For example, the dustproof sleeve 5 has a corrugated tubular structure. In this case, the dustproof sleeve 5 can be made of elastic materials such as rubber or latex, or materials such as plastic or asbestos, or even metal materials such as aluminum, iron, copper, aluminum alloy, or stainless steel. Because the dustproof sleeve 5 has a corrugated tubular structure, it can extend and retract when the housing 121 slides relative to the central rod 111 and the upper support assembly 2, thereby preventing damage to the dustproof sleeve 5.

[0455] In some examples, the elastic element 3A is fitted over the outside of the dustproof sleeve 5.

[0456] In some embodiments, referring to FIG85, the center rod 111 is provided with a first positioning portion 111H, and the winding assembly 112 is provided with a second positioning portion 112P. The first positioning portion 111H and the second positioning portion 112P cooperate to keep the center rod 111 and the winding assembly 112 relatively stationary.

[0457] By cooperating with the first positioning part 111H and the second positioning part 112P, the center rod 111 and the winding assembly 112 can be kept relatively stationary, so as to avoid the center rod 111 and the winding assembly 112 from rotating circumferentially when the motor 1 is working, thereby ensuring the stability of the motor 1 and improving the performance of the motor 1.

[0458] In some examples, the first positioning part 111H is formed as a groove on the outer peripheral wall of the center rod 111, and the second positioning part 112P is formed as a groove on the winding assembly 112. The anti-rotation rod 111K is disposed between the first positioning part 111H and the second positioning part 112P.

[0459] By providing anti-rotation rod 111K on the first positioning part 111H and the second positioning part 112P, the anti-rotation rod 111K can cooperate with the groove on the outer peripheral wall of the center rod 111 to limit the center rod 111. The anti-rotation rod 111K can also cooperate with the groove of the winding assembly 112 to limit the winding assembly 112, thereby preventing the winding assembly 112 and the center rod 111 from rotating circumferentially.

[0460] In some examples, the groove provided in the winding assembly 112 may be provided on the inner wall surface of the core 1121.

[0461] In some other examples, one of the first positioning part 111H and the second positioning part 112P is a positioning groove, and the other of the first positioning part 111H and the second positioning part 112P is a positioning protrusion. The positioning protrusion engages with the positioning groove to limit the movement of the core rod and the winding assembly 112, thereby preventing the core rod and the winding assembly 112 from rotating in the circumferential direction.

[0462] The above are merely specific embodiments of this disclosure, but the scope of protection of this disclosure is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in this disclosure should be included within the scope of protection of this disclosure. Therefore, the scope of protection of this disclosure should be determined by the scope of the claims.

Claims

1. A suspension system (300), comprising: A motor (1) adapted to be connected between the vehicle body (100) and the wheels (200) to adjust the distance between the vehicle body (100) and the wheels (200); The motor (1) includes a permanent magnet (122) and a winding assembly (112), one of which is adapted to be connected to the vehicle body (100), and the other of which is adapted to be connected to the wheel (200); the permanent magnet (122) cooperates with the winding assembly (112) to drive the motor (1) to work; The motor (1) is provided with a cooling channel (14), which is configured to cool the winding assembly (112) by controlling at least one of the temperature or flow rate of the cooling medium in the cooling channel (14) so ​​that the motor (1) provides at least the required thrust corresponding to the current operating condition, and the temperature of the permanent magnet (122) corresponding to the net heat generated at least for the target duration of operation under the required thrust does not exceed the demagnetization temperature of the permanent magnet (122); The net heat generation is the heat generated by the winding assembly (112) under a given current minus the heat carried away by the cooling medium.

2. The suspension system (300) according to claim 1, wherein, Under different operating conditions of the vehicle, the thrust provided by the motor (1) to the vehicle body (100) is not less than the required thrust corresponding to the current operating condition, and under the required thrust corresponding to the current operating condition, the maximum duration of continuous operation of the motor (1) is not less than the target duration, the target duration is the shortest duration for which the motor (1) continuously operates with the required thrust corresponding to the current operating condition to complete the current operating condition, and the maximum duration of continuous operation of the motor (1) is the maximum duration for which the temperature of the permanent magnet corresponding to the net heat generated by the motor (1) continuously operating under the required thrust corresponding to the current operating condition is maintained at no more than the demagnetization temperature of the permanent magnet, wherein the thrust provided by the motor (1) to the vehicle body (100) increases with the increase of the impact degree of the road surface on the vehicle body (100).

3. The suspension system (300) according to claim 1 or 2, wherein, When the vehicle is in the first working condition, the thrust of the motor (1) is not less than the first threshold F1, and the duration of continuous operation of the motor (1) is not less than T1. The first threshold F1 and T1 are configured to reduce the impact on the vehicle when it is in the first working condition, wherein the first working condition includes the condition of the vehicle passing through undulating road surface. When the vehicle is in the second working condition, the thrust of the motor (1) is not less than the second threshold F2, and the duration of continuous operation of the motor (1) is not less than T2. ​​The second threshold F2 and T2 are configured to reduce the degree of tilt of the vehicle when it is in the second working condition, wherein the second working condition includes the turning condition of the vehicle. When the vehicle is in the third operating condition, the thrust of the motor (1) is not less than the third threshold F3, and the duration of continuous operation of the motor (1) is not less than T3. The third threshold F3 and T3 are configured to reduce the pitch of the vehicle along the X direction when the vehicle is in the third operating condition. The third operating condition includes the starting and stopping conditions of the vehicle. Among them, F1 > F2 > F3, and T1 < T2 < T3.

4. The suspension system (300) according to any one of claims 1-3, wherein, The relationship between the net heat generation of the motor (1), the heat generation of the motor (1), and the heat carried away by the cooling medium is as follows: in, E is the net heat output of the motor (1). g q represents the heat generated by the motor (1). c ρ is the heat carried away by the cooling medium, v is the density of the cooling medium, v is the volume of the cooling channel (14), c is the specific heat capacity of the cooling medium, T is the temperature of the motor (1), and t is the cooling time. ∞ R is the temperature of the cooling medium, and R is the thermal resistance of the motor (1).

5. The suspension system (300) according to any one of claims 1-4, wherein, The motor (1) also includes a center rod (111), the winding assembly (112) is disposed on the center rod (111), and the cooling channel (14) is disposed inside the center rod (111).

6. The suspension system (300) according to claim 5, wherein, The relationship between the thrust of the motor (1) and the maximum duration of continuous operation of the motor (1) is: y = kx n Where y is the maximum duration of continuous operation of the motor (1), x is the thrust of the motor (1), k and n are constants, and k is a positive number and n is a negative number.

7. The suspension system (300) according to claim 6, wherein, Along the radial direction of the central rod (111), the projection of the cooling channel (14) is a first projection, and the projection of the winding assembly (112) is a second projection; The overlap of the first projection and the second projection in the radial direction of the central rod (111) is the length of the overlap along the axial direction of the central rod (111). k decreases as the overlap length decreases, and n decreases as the overlap length decreases.

8. The suspension system (300) according to any one of claims 5-7, wherein, The projection of the cooling channel (14) on the radial side of the central rod (111) is the first projection, and the length of the first projection along the axial direction of the central rod (111) is not less than the length of the winding assembly (112).

9. The suspension system (300) according to claim 8, wherein, The projection of the winding assembly (112) on the radial direction of the central rod (111) is a second projection; The overlap of the first projection and the second projection in the radial direction of the central rod (111) has an overlap length along the axial direction of the central rod (111); the overlap length is equal to the length of the second projection in the axial direction of the central rod (111).

10. The suspension system (300) according to claim 9, wherein, The projection of the winding assembly (112) on the radial direction of the central rod (111) is a second projection; The overlap of the first projection and the second projection in the radial direction of the central rod (111) is the overlap length along the axial direction of the central rod (111); The maximum duration of continuous operation of the motor (1) decreases as the overlap length decreases.

11. The suspension system (300) according to any one of claims 5-10, wherein, The winding assembly (112) includes: Multiple iron cores (1121) are arranged along the axial direction of the central rod (111), and a receiving groove (1123) is formed between two adjacent iron cores (1121). A coil (1122) is housed within the receiving groove (1123).

12. The suspension system (300) according to claim 11, wherein, The coil (1122) includes three-phase conductors, wherein the cross-sectional area of ​​each phase conductor is greater than or equal to 2.5 square millimeters and less than or equal to 3.5 square millimeters. The length of each phase conductor is not less than a first length, which is greater than or equal to 28 meters and less than or equal to 42 meters.

13. The suspension system (300) according to claim 12, wherein, The resistance of each phase conductor is no greater than 0.5 ohms.

14. The suspension system (300) according to any one of claims 5-13, wherein, The motor (1) serves as both a power element and an actuating element.

15. The suspension system according to claim 14, wherein, The motor (1) includes a motion component (12) and a fixed component (11). The fixed component (11) includes the center rod (111) and the winding component (112). The motion component (12) and the fixed component (11) are capable of relative movement along the axial direction of the center rod (111). The motion component (12) is formed as the actuating element, and the motion component (12) and the fixed component (11) cooperate to form the power element.

16. The suspension system (300) according to claim 15, wherein, The motion component (12) includes: The housing (121) has a portion of the central rod (111) located inside the housing (121) and the central rod (111) is slidably connected to the housing (121), and the winding assembly (112) is disposed inside the housing (121); A lower fork arm (13), said lower fork arm (13) being connected to the outside of the housing (121) and adapted to connect to the wheel (200); and A permanent magnet (122) is connected to the inner wall of the housing (121) and is arranged around the winding assembly (112); The housing (121) and the lower fork (13) are formed as the actuating element, and the permanent magnet (122) and the winding assembly (112) are formed as the power element.

17. The suspension system (300) according to claim 15 or 16, wherein, The mating gap between the moving component (12) and the fixed component (11) forms an electromagnetic gap.

18. The suspension system (300) according to any one of claims 15-17, wherein, The motor (1) also includes a sensor (15), which includes a reading head (151) and a magnetic strip (152). One of the reading head (151) and the magnetic strip (152) is located in the motion component (12), and the other of the reading head (151) and the magnetic strip (152) is located in the fixed component (11). The reading head (151) can sense the magnetic field signal of the magnetic strip (152) to detect the relative displacement of the fixed component (11) and the moving component (12).

19. The suspension system (300) according to any one of claims 5-18, wherein, The resistance of the suspension system (300) is less than 150N.

20. The suspension system (300) according to claim 19, wherein, The motor (1) includes a motion component (12) and a fixed component (11). The fixed component (11) includes the center rod (111) and the winding component (112). The motion component (12) and the fixed component (11) are capable of relative movement along the axial direction of the center rod (111). The motion component (12) includes a guide rod (123), and the center rod (111) and the guide rod (123) are nested together to form a guide component, wherein the guide stiffness of the guide component is not less than 7767 N / mm.

21. The suspension system (300) according to claim 20, wherein, The guide diameter of the guide rod (123) is not less than 23mm.

22. The suspension system (300) according to claim 20 or 21, wherein, The elastic modulus of both the guide rod (123) and the center rod (111) is not less than 200 GPa.

23. The suspension system (300) according to any one of claims 20-22, wherein, The fixing assembly (11) also includes a lower fork (13) adapted to connect to the wheel (200); The guide rod (123) includes a rod body (1231) and a base (1232). The first end of the rod body (1231) is nested with the central rod (111). The base (1232) is connected to the second end of the rod body (1231) and is detachably connected to the lower fork arm (13). Along the axial direction of the rod body (1231), the thickness of the base (1232) is not less than 3mm.

24. The suspension system (300) according to claim 23, wherein, The guide rod (123) is made of a first material, and the lower fork arm (13) is made of a second material. The density of the first material is not less than the density of the second material.

25. The suspension system (300) according to any one of claims 20-24, wherein, The central rod (111) is provided with a guide hole (111D) extending axially along the central rod (111), and at least a portion of the guide rod (123) is located within the guide hole (111D); The motion component (12) further includes a bearing assembly (113), which includes a cylindrical bearing seat (1131) and a plurality of balls (1132). The bearing seat (1131) is disposed in the guide hole (111D) and fixed to the central rod (111). The plurality of balls (1132) are embedded in the bearing seat (1131) and are rotatable relative to the bearing seat (1131). The guide rod (123) passes through the bearing seat (1131) and rolls with the plurality of balls (1132).

26. The suspension system (300) according to claim 25, wherein, The guide rod (123) is provided with at least one guide groove (1233). The at least one guide groove (1233) is recessed from the peripheral wall surface of the guide rod (123) toward the axis of the guide rod (123) and extends along the axial direction of the guide rod (123). A portion of any one of the plurality of balls (1132) is located in the corresponding guide groove (1233) of the at least one guide groove (1233) and rolls with the corresponding guide groove (1233).

27. The suspension system (300) according to claim 26, wherein, The cross-section of the at least one guide groove (1233) is arc-shaped, and the arc shape matches the corresponding ball (1132) among the plurality of balls (1132); the cross-section of the at least one guide groove (1233) is perpendicular to the axial direction of the guide rod (123).

28. The suspension system (300) according to claim 27, wherein, The coefficient of friction of the inner wall surface of the at least one guide groove (1233) is less than or equal to 0.

05.

29. The suspension system (300) according to any one of claims 26-28, wherein, The plurality of balls (1132) includes a plurality of sets of balls (1132), which are arranged at intervals along the circumference of the guide rod (123); The at least one guide groove (1233) includes a plurality of guide grooves (1233), which are arranged at intervals along the circumference of the guide rod (123), and one set of balls (1132) of the plurality of balls (1132) rolls into contact with one of the guide grooves (1233) of the plurality of guide grooves (1233).

30. The suspension system (300) according to any one of claims 11-29, wherein, The winding assembly (112) includes a plurality of iron cores (1121), any one of the plurality of iron cores (1121) comprising: A yoke (1121A), wherein the yoke (1121A) is provided with a first mounting hole (1121C), and the center rod (111) passes through the first mounting hole (1121C); and A tooth (1121B) is connected to the yoke (1121A) and is disposed around the first mounting hole (1121C).

31. The suspension system (300) according to claim 30, wherein, The toothed portion (1121B) includes a plurality of separately arranged support members (1121D), which are arranged circumferentially along the yoke portion (1121A) and connected to the yoke portion (1121A).

32. The suspension system (300) according to claim 31, wherein, The toothed portion (1121B) also includes an insulating element, which is provided between any two adjacent supports (1121D) among the plurality of supports (1121D).

33. The suspension system (300) according to claim 32, wherein, The sides of any two adjacent support members (1121D) facing each other are the first side and the second side, respectively; the insulating member is an insulating coating, which is disposed on at least one of the first side and the second side.

34. The suspension system (300) according to any one of claims 31-33, wherein, The toothed portion (1121B) also includes an adhesive member, through which any two adjacent supports (1121D) among the plurality of supports (1121D) are bonded together.

35. The suspension system (300) according to claim 34, wherein, The adhesive is made of insulating material.

36. The suspension system (300) according to any one of claims 31-35, wherein, The yoke (1121A) is provided with a snap-fit ​​groove (1121E) extending circumferentially along the first mounting hole (1121C), and the snap-fit ​​groove (1121E) is recessed from the outer peripheral surface of the yoke (1121A) toward the inner peripheral surface. One of the plurality of support members (1121D) has a protrusion (1121F) at one end facing the yoke (1121A) that protrudes axially along the first mounting hole (1121C), and the protrusion (1121F) is engaged in the engaging groove (1121E).

37. The suspension system (300) according to any one of claims 31-36, wherein, Along the direction of any one of the plurality of supports (1121D) toward the yoke (1121A), the thickness of any one of the supports (1121D) in the axial direction of the first mounting hole (1121C) gradually decreases.

38. The suspension system (300) according to any one of claims 31-37, wherein, Along the direction of any one of the plurality of supports (1121D) toward the yoke (1121A), the distance between the two side surfaces of any one of the supports (1121D) in the circumferential direction of the first mounting hole (1121C) gradually decreases.

39. The suspension system (300) according to any one of claims 31-38, wherein, A first gap is formed between two adjacent support members (1121D) among the plurality of support members (1121D).

40. The suspension system (300) according to claim 39, wherein, Along the radial direction of the first mounting hole (1121C), the width of the first gap is equal everywhere.

41. The suspension system (300) according to claim 39, wherein, Along the radial direction of the first mounting hole (1121C), the width of the first gap gradually increases.

42. The suspension system (300) according to claim 41, wherein, The minimum width of the first gap is greater than or equal to 0.1 mm.

43. The suspension system (300) according to any one of claims 39-42, wherein, In any two adjacent support members (1121D) of the plurality of support members (1121D), one is provided with a first snap-fit ​​notch (1121G) and the other is provided with a first snap-fit ​​protrusion (1121H), and the first snap-fit ​​protrusion (1121H) snaps into the first snap-fit ​​notch (1121G).

44. The suspension system (300) according to any one of claims 39-43, wherein, The yoke (1121A) includes a plurality of arc segments (1121K) arranged circumferentially along the yoke (1121A), and a second gap is formed between two adjacent arc segments (1121K).

45. The suspension system (300) according to claim 44, wherein, Along the radial direction of the first mounting hole (1121C), the width of the second gap is equal everywhere.

46. ​​The suspension system (300) according to claim 44, wherein, Along the radial direction of the first mounting hole (1121C), the width of the second gap gradually increases.

47. The suspension system (300) according to any one of claims 44-46, wherein, The minimum width of the second gap is greater than or equal to 0.1 mm.

48. The suspension system (300) according to any one of claims 44-47, wherein, Any one of the plurality of arc segments (1121K) is connected to at least one of the plurality of support members (1121D); or, Any one of the plurality of support members (1121D) is connected to at least one of the plurality of arc segments (1121K).

49. The suspension system (300) according to claim 30, wherein, The toothed portion (1121B) includes a first toothed portion (112A) and a second toothed portion (112B) that are separately arranged; the first toothed portion (112A) includes a plurality of first support members (112C) that are circumferentially spaced along the first mounting hole (1121C); the second toothed portion (112B) includes a plurality of second support members (112D) that are circumferentially spaced along the first mounting hole (1121C); The plurality of first support members (112C) and the plurality of second support members (112D) are arranged alternately along the circumference of the first mounting hole (1121C), and a third gap is formed between adjacent first support members (112C) and second support members (112D).

50. The suspension system (300) according to claim 49, wherein, The plurality of first support members (112C) are connected to the outer peripheral surface of the yoke (1121A).

51. The suspension system (300) according to claim 50, wherein, The plurality of first support members (112C) and the yoke (1121A) are an integral structure.

52. The suspension system (300) according to claim 50 or 51, wherein, The inner diameter of the first tooth (112A) is the same as the outer diameter of the yoke (1121A), and the inner diameter of the second tooth (112B) is the same as the outer diameter of the yoke (1121A).

53. The suspension system (300) according to any one of claims 49-52, wherein, The yoke (1121A) includes a first yoke (112E) and a second yoke (112F) that are separately arranged. The plurality of first support members (112C) are connected to the first yoke (112E), and the plurality of second support members (112D) are connected to the second yoke (112F).

54. The suspension system (300) according to claim 53, wherein, The plurality of first support members (112C) and the first yoke (112E) are integral structures, and the plurality of second support members (112D) and the second yoke (112F) are integral structures.

55. The suspension system (300) according to claim 53 or 54, wherein, The second yoke (112F) is located on the side of the first yoke (112E) in the axial direction of the first mounting hole (1121C).

56. The suspension system (300) according to claim 55, wherein, The inner diameter of the first yoke (112E) is the same as the inner diameter of the second yoke (112F).

57. The suspension system (300) according to any one of claims 53-55, wherein, A portion of the second yoke (112F) passes through the interior of the first yoke (112E).

58. The suspension system (300) according to claim 57, wherein, The outer diameter of the second yoke (112F) is the same as the inner diameter of the first yoke (112E).

59. The suspension system (300) according to any one of claims 53-58, wherein, The first yoke (112E) includes a first annular portion (112G) and a plurality of first rib portions (112H), the plurality of first rib portions (112H) being connected to the outer peripheral surface of the first annular portion (112G) and arranged at intervals along the circumferential direction of the first annular portion (112G); The second yoke (112F) includes a second annular portion (112K) and a plurality of second rib portions (112L). The second annular portion (112K) is located on one side of the first annular portion (112G) in the axial direction of the first mounting hole (1121C). The plurality of first rib portions (112H) and the plurality of second rib portions (112L) are arranged alternately along the circumference of the first mounting hole (1121C), and a fourth gap is formed between adjacent first rib portions (112H) and second rib portions (112L).

60. The suspension system (300) according to claim 59, wherein, The plurality of first support members (112C) are connected to the side surface of the first annular portion (112G) facing the second annular portion (112K), and any one of the plurality of first rib portions (112H) is connected to a corresponding first support member (112C) among the plurality of first support members (112C). The plurality of second support members (112D) are connected to the outer peripheral surface of the second annular portion (112K), and any one of the plurality of second rib portions (112L) is connected to the side surface of the corresponding second support member (112D) of the plurality of second support members (112D) facing the first annular portion (112G) in the axial direction of the first mounting hole (1121C).

61. The suspension system (300) according to claim 59 or 60, wherein, The inner diameter of the first annular portion (112G) is the same as the inner diameter of the second annular portion (112K).

62. The suspension system (300) according to any one of claims 49-61, wherein, The toothed portion (1121B) further includes a plurality of connecting ribs (112M) and a plurality of connecting grooves (112N), wherein the plurality of connecting ribs (112M) are respectively engaged in the plurality of connecting grooves (112N); Any two adjacent first support members (112C) among the plurality of first support members (112C) are connected by one of the plurality of connecting ribs (112M), and one of the plurality of connecting grooves (112N) is provided between any two adjacent second support members (112D); or, Any two adjacent second support members (112D) among the plurality of second support members (112D) are connected by one of the multiple connecting ribs (112M). One of the multiple connecting grooves (112N) is provided between two adjacent first support members (112C) among the plurality of first support members (112C).

63. The suspension system (300) according to any one of claims 53-62, wherein, The plurality of first support members (112C) are connected to the side surface of the first yoke (112E) facing the second yoke (112F), and the plurality of second support members (112D) are connected to the outer peripheral surface of the second yoke (112F).

64. The suspension system (300) according to claim 30, wherein, The iron core (1121) is provided with a barrier groove (1124).

65. The suspension system (300) according to claim 64, wherein, The barrier groove (1124) includes a first barrier groove (1124A), which is disposed on the tooth (1121B).

66. The suspension system (300) according to claim 65, wherein, The first barrier groove (1124A) extends circumferentially along the tooth (1121B).

67. The suspension system (300) according to claim 65 or 66, wherein, The first barrier groove (1124A) extends along the inner edge of the tooth (1121B) toward the outer edge of the tooth (1121B).

68. The suspension system (300) according to claim 65 or 66, wherein, The first barrier groove (1124A) extends radially along the tooth (1121B).

69. The suspension system (300) according to any one of claims 65-68, wherein, The barrier groove (1124) further includes a second barrier groove (1124B), which is disposed on the yoke (1121A).

70. The suspension system (300) according to claim 69, wherein, The second barrier groove (1124B) extends circumferentially along the yoke (1121A).

71. The suspension system (300) according to claim 69 or 70, wherein, The second barrier groove (1124B) extends along the inner edge of the yoke (1121A) toward the outer edge of the yoke (1121A).

72. The suspension system (300) according to claim 69 or 70, wherein, The second barrier groove (1124B) extends radially along the yoke (1121A).

73. The suspension system (300) according to any one of claims 69-72, wherein, The at least one first barrier groove (1124A) includes a plurality of first barrier grooves (1124A), which are arranged circumferentially at intervals along the first mounting hole (1121C); The at least one second barrier groove (1124B) includes a plurality of second barrier grooves (1124B), which are arranged circumferentially at intervals along the first mounting hole (1121C).

74. The suspension system (300) according to claim 73, wherein, The plurality of first barrier grooves (1124A) are respectively connected to the plurality of second barrier grooves (1124B).

75. The suspension system (300) according to claim 30, wherein, The iron core (1121) is made using powder metallurgy.

76. The suspension system (300) according to claim 75, wherein, The raw materials of the iron core (1121) include powdered soft magnetic composite material and insulating material, wherein the insulating material is coated on the surface of the soft magnetic composite material.

77. The suspension system (300) according to claim 75 or 76, wherein, The iron core (1121) is provided with a rib groove (1125), and a reinforcing member is provided in the rib groove (1125).

78. The suspension system (300) according to claim 77, wherein, The reinforcing component is manufactured using injection molding.

79. The suspension system (300) according to claim 77 or 78, wherein, The rib groove (1125) extends circumferentially along the iron core (1121); or, the rib groove (1125) extends radially along the iron core (1121).

80. The suspension system (300) according to any one of claims 77-79, wherein, Along the axial direction of the iron core (1121), the iron core (1121) includes a first surface (1121M) and a second surface (1121N); The rib groove (1125) includes: A plurality of first rib grooves (1125A) are arranged at intervals along the circumference of the iron core (1121), and the plurality of first rib grooves (1125A) are recessed from the first surface (1121M) toward the second surface (1121N); A plurality of second rib grooves (1125B) are arranged at circumferential intervals along the iron core (1121), and the plurality of second rib grooves (1125B) are recessed from the second surface (1121N) toward the first surface (1121M); and Multiple third rib grooves (1125C) are provided at intervals along the circumference of the iron core (1121), and the multiple third rib grooves (1125C) are recessed from the inner circumferential surface of the iron core (1121) toward the outer circumferential surface.

81. The suspension system (300) according to claim 80, wherein, Along the circumferential direction of the iron core (1121), any one of the plurality of first rib grooves (1125A) includes a first inner wall surface (1125D) and a second inner wall surface (1125E), and any one of the plurality of second rib grooves (1125B) includes a third inner wall surface (1125F) and a fourth inner wall surface (1125G). The plurality of first rib grooves (1125A) correspond to the plurality of second rib grooves (1125B). For the corresponding first rib groove (1125A) and second rib groove (1125B), along the axial direction of the iron core (1121), the projection of the second inner wall surface (1125E) coincides with the projection of the third inner wall surface (1125F). Along the circumference of the iron core (1121), the first inner wall surface (1125D) and the fourth inner wall surface (1125G) are located on both sides of the first inner wall surface (1125D).

82. The suspension system (300) according to claim 81, wherein, The third rib groove (1125C) extends through the iron core (1121) along the axial direction of the iron core (1121), and at least one of the corresponding first rib groove (1125A) and second rib groove (1125B) is connected to one of the third rib grooves (1125C) among the plurality of third rib grooves (1125C).

83. The suspension system (300) according to claim 82, wherein, The rib groove (1125) further includes a plurality of fourth rib grooves (1125H), which extend along the axial direction of the iron core (1121). The first rib groove (1125A) is connected to the corresponding second rib groove (1125B) through one of the fourth rib grooves (1125H).

84. The suspension system (300) according to any one of claims 75-83, wherein, The iron core (1121) also includes a force-bearing component (1125K), which is disposed in the first mounting hole (1121C) and extends circumferentially along the first mounting hole (1121C).

85. The suspension system (300) according to claim 84, wherein, The outer peripheral surface of the force-bearing member (1125K) has a first recess (1125M), and the inner peripheral surface of the yoke (1121A) has a first protrusion, the first protrusion being located within the first recess (1125M).

86. The suspension system (300) according to claim 84 or 85, wherein, The force-bearing member (1125K) has a second recess (1125N) formed on one side of the iron core (1121) in the axial direction, and the inner circumferential surface of the yoke (1121A) has a second protrusion, which is located inside the second recess (1125N).

87. The suspension system (300) according to any one of claims 84-86, wherein, The inner circumferential surface of the force-bearing member (1125K) has a third protrusion, and the outer circumferential surface of the central rod (111) has a third recess. The central rod (111) passes through the force-bearing member (1125K), and the third protrusion is located in the third recess.

88. The suspension system (300) according to claim 30, wherein, The plurality of iron cores (1121) includes a first end iron core (1126A), a second end iron core (1126B), and a middle iron core (1126C), wherein the middle iron core (1126C) is disposed between the first end iron core (1126A) and the second end iron core (1126B); The first end core (1126A) is provided with a first magnetic isolation groove (1126D), and the first magnetic isolation groove (1126D) is recessed from the side surface of the first end core (1126A) facing away from the second end core (1126B) toward the second end core (1126B); The second end core (1126B) is provided with a second magnetic isolation groove (1126E), which is recessed from the side surface of the second end core (1126B) facing away from the first end core (1126A) toward the first end core (1126A).

89. The suspension system (300) according to claim 88, wherein, The first magnetic isolation groove (1126D) extends circumferentially along the first end iron core (1126A), and the second magnetic isolation groove (1126E) extends circumferentially along the second end iron core (1126B).

90. The suspension system (300) according to claim 88 or 89, wherein, The inner circumferential surface of the first end core (1126A) is provided with a first limiting protrusion (1126F), and the inner circumferential surface of the second end core (1126B) is provided with a second limiting protrusion (1126G). A first limiting groove and a second limiting groove are formed on the outer peripheral surface of the center rod (111). The first limiting protrusion (1126F) is located in the first limiting groove, and the second limiting protrusion (1126G) is located in the second limiting groove.

91. The suspension system (300) according to any one of claims 75-90, wherein, The iron core (1121) further includes a first tooth crown (1126H), which is disposed on the outer edge of the tooth portion (1121B) and surrounds the tooth portion (1121B); along the radial direction of the iron core (1121), the projection of the tooth portion (1121B) does not exceed the projection range of the first tooth crown (1126H).

92. The suspension system (300) according to claim 91, wherein, The first crown (1126H) is formed with a first inclined surface (1126M) and a second inclined surface (1126N). The first inclined surface (1126M) and the second inclined surface (1126N) are arranged along the axial direction of the iron core (1121) and the distance between the first inclined surface (1126M) and the second inclined surface (1126N) gradually increases along the direction from the outer peripheral surface of the iron core (1121) to the inner peripheral surface.

93. The suspension system (300) according to claim 11, wherein, The iron core (1121) is provided with a wire passage groove (1127A), which is recessed from the outer peripheral surface of the iron core (1121) toward the inner peripheral surface, and the wire passage groove (1127A) penetrates the iron core (1121) along the axial direction of the iron core (1121). Along the axial direction of the iron core (1121), the projections of the wire passage slots (1127A) of the plurality of iron cores (1121) coincide, so that the wire passage slots (1127A) of the plurality of iron cores (1121) form a wire passage channel (1127B); the wire passage channel (1127B) is configured to accommodate the wire connection segment (1122A) of the coil (1122), and the wire connection segment (1122A) is configured to connect adjacent in-phase coils (1122).

94. The suspension system (300) according to claim 93, wherein, The central rod (111) includes a first rod segment (111A) and a second rod segment (111B), the winding assembly (112) is connected to the second rod segment (111B), and the first rod segment (111A) is provided with a wire outlet channel (111E); The coil (1122) closest to the first rod segment (111A) among the coils (1122) of the same phase includes a lead-out end (1122B) which is located in the lead-out channel (111E) and is configured to connect the lead-out wire of the winding assembly (112). The lead-out wire passes through the lead-out channel (111E) and is configured to connect to the connector (116).

95. The suspension system (300) according to claim 94, wherein, The outgoing channel (111E) includes a radial hole (111F) and an axial hole (111G), and the radial hole (111F) communicates with the axial hole (111G).

96. The suspension system (300) according to claim 94 or 95, wherein, The outgoing cable channel (111E) is located inside the first pole segment (111A).

97. The suspension system (300) according to claim 5, wherein, The motor (1) includes a motion component (12) and a fixed component (11). The fixed component (11) includes the center rod (111) and the winding component (112). The motion component (12) and the fixed component (11) are capable of relative movement along the axial direction of the center rod (111). The motion component (12) includes a housing (121), the housing (121) is provided with a second mounting hole (1211), the second mounting hole (1211) communicates with the internal space of the housing (121), the center rod (111) passes through the second mounting hole (1211), and the winding assembly (112) is located inside the housing (121).

98. The suspension system (300) according to claim 97, wherein, The motion component (12) further includes a first linear bearing (124), which is disposed in the second mounting hole (1211) and connected to the housing (121). The center rod (111) passes through the first linear bearing (124) and is slidably connected to the first linear bearing (124).

99. The suspension system (300) according to claim 98, wherein, The motion component (12) also includes: A first seal (125) is disposed around the inner wall of the second mounting hole (1211) between the central rod (111); and The second seal (126) is disposed around the inner wall of the second mounting hole (1211) and between the center rod (111); the first linear bearing (124) is disposed between the first seal (125) and the second seal (126); The first seal (125), the second seal (126), the center rod (111), and the inner wall of the mounting hole form a first oil storage cavity, which contains lubricating fluid.

100. The suspension system (300) according to claim 98 or 99, wherein, The housing (121) is provided with an oil injection hole (1212), which extends from the outer wall of the housing (121) to the first oil storage cavity; The motion component (12) also includes a sealing element (127), which is detachably connected to the oil injection hole (1212).

101. The suspension system (300) according to any one of claims 98-100, wherein, The motion component (12) further includes a sealing bracket (128), which is disposed on the outside of the housing (121) and is detachably connected to the top wall of the housing (121); A portion of the first seal (125) is disposed between the top wall and the sealing bracket (128).

102. The suspension system (300) according to claim 101, wherein, The first seal (125) includes: An annular sealing portion (1251), the inner circumferential surface of which contacts the central rod (111); and A support portion (1252) is connected to the outer peripheral surface of the annular sealing portion (1251) and is disposed around the annular sealing portion (1251). The support portion (1252) is disposed between the top wall and the sealing bracket (128).

103. The suspension system (300) according to claim 102, wherein, When the annular sealing part (1251) is in a free state, along the axial direction of the annular sealing part (1251), the distance between the inner circumferential surface of the annular sealing part (1251) and the axis of the annular sealing part (1251) first increases and then decreases.

104. The suspension system (300) according to claim 102 or 103, wherein, The sealing bracket (128) includes: The main body (1281) is located on the side of the support (1252) opposite to the top wall; and A connecting part (1282) is connected to the main body part (1281) and is disposed around the support part (1252). The connecting part (1282) is connected to the housing (121).

105. The suspension system (300) according to claim 97, wherein, The central rod (111) is provided with a guide hole (111D) extending along the axial direction of the central rod (111); The motion component (12) further includes a guide rod (123) located inside the housing (121), and at least a portion of the guide rod (123) is located within the guide hole (111D); The fixing component (11) further includes a second linear bearing (114), which is disposed in the guide hole (111D) and connected to the center rod (111). The guide rod (123) passes through the second linear bearing (114) and is slidably connected to the second linear bearing (114).

106. The suspension system (300) according to claim 105, wherein, The guide rod (123) and the inner wall of the guide hole (111D) form a second oil storage cavity (111M), and the second oil storage cavity (111M) is filled with lubricating fluid; The fixing assembly (11) further includes a third seal (115), which is disposed around the inner wall of the guide hole (111D) and between the guide rod (123), and the second linear bearing (114) is located on the side of the third seal (115) facing the second oil reservoir (111M).

107. The suspension system (300) according to claim 97, further comprising: Upper support assembly (2), the upper support assembly (2) being disposed outside the housing (121) and connected to the central rod (111), the upper support assembly (2) being configured to connect to the vehicle body (100); and A buffer body (3) is connected to the side of the upper support assembly (2) facing the housing (121).

108. The suspension system (300) according to claim 107, wherein, The upper support component (2) includes: An outer bracket (22) is provided with an installation space (221) and a first clearance hole (222). The center rod (111) passes through the first clearance hole (222). The buffer body (3) is connected to the side of the outer bracket (22) facing the housing (121). A connecting component (23) is provided in the installation space (221) and connects the outer bracket (22) and the center rod (111).

109. The suspension system (300) according to claim 108, wherein, The buffer body (3) and the outer support (22) are an integral structure.

110. The suspension system (300) according to claim 108 or 109, wherein, The connection component (23) includes: Inner sleeve (231), the inner sleeve (231) is connected to the outer bracket (22) and is arranged around the central rod (111); The fastener (232) is located on the side of the inner bushing (231) opposite to the housing (121) and is threadedly connected to the center rod (111); A cover plate (233) is disposed on the side of the inner liner (231) opposite to the housing (121) and surrounds the fastener (232). The cover plate (233) is connected to the outer bracket (22). A fourth seal (234) is connected between the cover plate (233) and the fixing member (232).

111. The suspension system (300) according to claim 110, wherein, The fourth seal (234) is capable of radial extension and retraction along the cover plate (233).

112. The suspension system (300) according to claim 111, wherein, The fourth seal (234) is in the shape of an annular corrugated plate, and the corrugated portion of the fourth seal (234) extends circumferentially along the cover plate (233).

113. The suspension system (300) according to claim 110 further includes a fifth seal (4), the fifth seal (4) being disposed around the inner wall of the inner bushing (231) and between the center rod (111).

114. The suspension system (300) according to claim 97, wherein, The central rod (111) is provided with a socket (111N); The fixing component (11) also includes: A connector (116) configured to connect the outgoing wires of the winding assembly (112), a portion of the connector (116) being accommodated within the socket (111N); and At least one sixth seal (117) is disposed around the inner wall of the socket (111N) between the plug (116).

115. The suspension system (300) according to claim 107 further includes a dust sleeve (5), the dust sleeve (5) being sleeved on the outside of the housing (121), and the first end of the dust sleeve (5) being connected to the upper support assembly (2), the second end of the dust sleeve (5) being connected to the housing (121), and the dust sleeve (5) being capable of extending and retracting along the axial direction of the housing (121).

116. The suspension system (300) according to claim 107, further comprising: A lower support (30A) is connected to the housing (121); as well as An elastic element (3A) is disposed between the upper support assembly (2) and the lower support (30A).

117. The suspension system (300) according to claim 5, wherein, The center rod (111) is provided with a first positioning part (111H), and the winding assembly (112) is provided with a second positioning part (112P). The first positioning part (111H) and the second positioning part (112P) cooperate to make the center rod (111) and the winding assembly (112) relatively stationary.

118. The suspension system (300) according to claim 117, wherein, The first positioning part (111H) is formed as a groove on the outer peripheral wall of the center rod (111), the second positioning part (112P) is formed as a groove on the winding assembly (112), and the anti-rotation rod (111K) is disposed between the first positioning part (111H) and the second positioning part (112P).

119. The suspension system (300) according to claim 5, wherein, The central rod (111) includes a first rod segment (111A) and a second rod segment (111B), and the winding assembly (112) is connected to the second rod segment (111B); The cooling channel (14) includes: Water inlet channel (141) extends from the side surface of the first rod segment (111A) opposite to the second rod segment (111B) to the end of the second rod segment (111B) opposite to the first rod segment (111A); A water outlet channel (142) extending from the side surface of the first rod segment (111A) opposite to the second rod segment (111B) to the end of the second rod segment (111B) opposite to the first rod segment (111A); and A confluence channel (143) is provided at one end of the second rod segment (111B) opposite to the first rod segment (111A) and connects the inlet channel (141) and the outlet channel (142).

120. The suspension system (300) according to claim 119 further satisfies at least one of the following: The at least one water inlet channel (141) includes a plurality of water inlet channels (141), which are spaced apart circumferentially along the central rod (111); or, The at least one water outlet channel (142) includes a plurality of water outlet channels (142), which are arranged at circumferential intervals along the central rod (111).

121. The suspension system (300) according to claim 120, wherein, The confluence channel (143) extends circumferentially along the central rod (111).

122. The suspension system (300) according to claim 18, wherein, The motion component (12) includes a housing (121), the housing (121) is provided with a second mounting hole (1211), the second mounting hole (1211) communicates with the internal space of the housing (121), and the central rod (111) passes through the second mounting hole (1211); The reading head (151) is connected to the surface of the housing (121) that mates with the central rod (111), the magnetic strip (152) is connected to the central rod (111), and the sensing surface of the reading head (151) faces the magnetic strip (152).

123. The suspension system (300) according to claim 122, wherein, The central rod (111) is provided with a mounting groove (111C), and the magnetic strip (152) is disposed in the mounting groove (111C).

124. The suspension system (300) according to claim 123, wherein, The sensor (15) also includes a back plate (153), which is disposed in the mounting groove (111C), and the magnetic strip (152) is disposed on the side surface of the back plate (153) facing the reading head (151).

125. The suspension system (300) according to claim 124, wherein, At least a portion of the back plate (153) is interference-fitted with the inner wall of the mounting groove (111C).

126. The suspension system (300) according to claim 125, wherein, The backplate (153) includes: Ontology (1531); The first mating part (1532) and the second mating part (1533) are respectively connected to the two ends of the body part (1531) in a first direction, wherein the first direction is perpendicular to the arrangement direction of the back plate (153) and the magnetic strip (152). The first mating part (1532) and the inner wall surface of the mounting groove (111C) are both interference-fitted, as are the second mating part (1533) and the inner wall surface of the mounting groove (111C).

127. An electric motor (1) for use in a suspension system (300) according to any one of claims 1-126, the electric motor (1) comprising a motion component (12) and a fixed component (11), the motion component (12) and the fixed component (11) being capable of relative movement along the axial direction of the central rod (111).

128. An actuator (10), comprising: The motor (1) according to claim 127; as well as Upper support component (2) is connected to the fixing component (11).

129. The actuator (10) according to claim 128, further comprising: A lower support (30A) is connected to the motion component (12); as well as An elastic element (3A) is disposed between the upper support assembly (2) and the lower support (30A).

130. A vehicle (1000), comprising: The suspension system (300) according to any one of claims 1-126; Body (100); as well as A wheel (200) is located on the underside of the vehicle body (100), and a suspension system (300) is connected between the vehicle body (100) and the wheel (200).

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