Motors, chassis and vehicles

Abstract

The present application provides a motor, a chassis system and a vehicle. The motor includes: a rotor core, the rotor core includes a plurality of core segments, the plurality of core segments are stacked, the rotor core is provided with a mounting hole, the mounting hole penetrates the plurality of core segments along the axial direction of the rotor core; in at least a portion of the core segments, any two adjacent core segments are arranged in a staggered manner in the circumferential direction of the rotor core; a plurality of permanent magnets are arranged in the rotor core, and the plurality of permanent magnets are arranged at intervals along the circumferential direction of the mounting hole; a rotating shaft is passed through the mounting hole; a bearing part is sleeved on the part of the rotating shaft located outside the rotor core; the axial clearance of the bearing part is recorded as σ (mm), the axial preload of the bearing part is recorded as Fz (N), and the sum of the weights of the rotor core, the plurality of permanent magnets, the rotating shaft and the bearing part is recorded as m (kg); wherein A1×(A2+σ)‑Fz≤A3×m, A1=100(N / mm), A2=0.88mm, A3=9.8(N / kg).

Description

Technical Field

[0001] The present application relates to the technical field of motors, and in particular to a motor, a chassis system and a vehicle. Background Art

[0002] In the related art, a vehicle includes a chassis system, and the chassis system includes a motor. With the development of the economy, people are more and more demanding on a low-noise and comfortable driving environment, and thus the requirements for motor performance are getting higher and higher. In the related art, the motor of the chassis system has a large vibration noise, which leads to a large noise when the vehicle is driving, and the product has low performance and cannot meet the low-noise demand. Summary of the invention

[0003] The present application aims to solve at least one of the technical problems existing in the prior art or related art.

[0004] To this end, a first aspect of the present application provides an electric motor.

[0005] A second aspect of the present application provides a chassis system.

[0006] A third aspect of the present application provides a vehicle.

[0007] In view of this, the first aspect of the present application provides a motor, comprising: a rotor core, the rotor core comprising a plurality of core segments, the plurality of core segments are stacked, the rotor core is provided with a mounting hole, the mounting hole penetrates the plurality of core segments along the axial direction of the rotor core; in at least a portion of the core segments, any two adjacent core segments are staggered in the circumferential direction of the rotor core; a plurality of permanent magnets are provided in the rotor core, and the plurality of permanent magnets are arranged at intervals along the circumferential direction of the mounting holes; a rotating shaft is passed through the mounting holes; a bearing portion is sleeved on a portion of the rotating shaft located outside the rotor core; the axial clearance of the bearing portion is denoted as σ (mm), the axial preload of the bearing portion is denoted as Fz (N), and the sum of the weights of the rotor core, the plurality of permanent magnets, the rotating shaft and the bearing portion is denoted as m (kg); wherein, A1×(A2+σ)-Fz≤A3×m, A1=100 (N / mm), A2=0.88mm, A3=9.8 (N / kg).

[0008] The motor provided in the present application includes a rotor core, a plurality of permanent magnets, a rotating shaft and a bearing portion.

[0009] The rotor core comprises a plurality of core segments, which are stacked in the axial direction of the rotor core. The rotor core is provided with a mounting hole, which penetrates through the plurality of core segments in the axial direction of the rotor core.

[0010] The mounting hole is used to assemble the rotating shaft. Specifically, the rotating shaft is inserted into the mounting hole. A plurality of permanent magnets are arranged on the rotor core, and the plurality of permanent magnets are arranged at intervals along the circumference of the mounting hole.

[0011] The bearing part is sleeved on the part of the rotating shaft located outside the rotor core. That is, the bearing part is sleeved on the rotating shaft, and the bearing part is located on one side of the rotor core.

[0012] Among them, in at least a part of the core segments, any two adjacent core segments are staggered in the circumferential direction of the rotor core. That is, in at least a part of the core segments, any two adjacent core segments are staggered in the circumferential direction of the rotor core to form rotor skew poles. The segmented modular arrangement of the rotor core has the advantages of easy installation and maintenance, and skew poles can be formed between multiple core segments.

[0013] The tooth harmonics of the motor are the main source of the vibration and noise of the motor. Therefore, limiting the staggered arrangement of any two adjacent core segments in the circumferential direction of the rotor core can reduce the cogging torque and torque pulsation, thereby reducing electromagnetic vibration. In other words, by dividing the rotor core into multiple core segments and staggering any two adjacent core segments in the circumferential direction of the rotor core, the specific harmonic content in the motor can be effectively suppressed, and the torque pulsation and cogging torque of the motor can be improved, thereby achieving the effect of reducing the vibration and noise of the motor.

[0014] In addition, the axial clearance σ (mm) of the bearing part, the axial preload Fz (N) of the bearing part, the sum of the weights of the rotor core, multiple permanent magnets, the rotating shaft and the bearing part m (kg), A1, A2 and A3 satisfy: A1×(A2+σ)-Fz≤A3×m, A1=100 (N / mm), A2=0.88mm, A3=9.8 (N / kg). This setting further limits the matching structure of the rotor core, multiple permanent magnets, the rotating shaft and the bearing part. Specifically, the relationship between σ, Fz and m is further defined. The relationship between the above parameters can enhance the overall structural stiffness of the rotor core, multiple permanent magnets, the rotating shaft and the bearing part, enhance the overall anti-deformation ability of the rotor core, multiple permanent magnets, the rotating shaft and the bearing part, and reduce the axial movement of the motor when it is working. In this way, the vibration performance of the motor during operation is improved, and the vibration noise of the motor can be further reduced.

[0015] It can be understood that when there is no load, the inner ring of the bearing is fixed and the displacement of the outer ring of the bearing from one extreme position to another extreme position along the axial direction of the rotor core relative to the fixed inner ring is recorded as the axial clearance σ of the bearing. Alternatively, when there is no load, the outer ring of the bearing is fixed and the displacement of the inner ring of the bearing from one extreme position to another extreme position along the axial direction of the rotor core relative to the fixed outer ring is recorded as the axial clearance σ of the bearing.

[0016] It can also be said that when the outer ring or outer ring of the bearing part is subjected to the external axial force, the inner ring and the outer ring will produce axial displacement, and the maximum value of the axial displacement is the axial clearance σ of the bearing.

[0017] Optionally, the permanent magnet is disposed on the outer peripheral wall of the rotor core in a surface-mounted manner.

[0018] Optionally, the rotor core is provided with magnet slots penetrating through the plurality of core segments, and the permanent magnets are arranged in the magnet slots.

[0019] In some embodiments, optionally, σ≤0.05 mm.

[0020] In this embodiment, the value range of the axial clearance σ of the bearing portion is further limited so that σ≤0.05 mm. In this way, the axial vibration of the motor can be further optimized to further optimize the vibration noise of the motor.

[0021] In some embodiments, optionally, the bearing portion includes at least one bearing, and the bearing is located between the end of the rotating shaft and the rotor core.

[0022] In this embodiment, the structure of the bearing portion is further defined such that the bearing portion includes at least one bearing, and the position of the bearing is defined such that the bearing is located between the end of the rotating shaft and the rotor core.

[0023] Alternatively, when the bearing portion includes one bearing, the axial clearance of the bearing is denoted as σ (mm), and the axial preload force of the bearing is denoted as Fz (N).

[0024] Optionally, when the bearing portion includes multiple (eg, greater than or equal to two) bearings, the axial clearance of any one of the multiple bearings is denoted as σ (mm), and the axial preload force of any one of the multiple bearings is denoted as Fz (N).

[0025] Optionally, when the bearing portion includes multiple (eg, greater than or equal to two) bearings, the axial clearance of at least some of the multiple bearings is recorded as σ (mm), and the axial preload force of at least some of the multiple bearings is recorded as Fz (N).

[0026] In some embodiments, optionally, when there are multiple bearings, some of the bearings are located on a first axial side of the rotor core, and another part of the bearings are located on a second axial side of the rotor core.

[0027] In this embodiment, when the number of bearings is multiple, the matching structure of the multiple bearings and the rotor core is defined so that a portion of the multiple bearings are located on the axial first side of the rotor core, and another portion of the multiple bearings are located on the axial second side of the rotor core.

[0028] Optionally, the axial clearance of the bearing located on the first axial side of the rotor core is recorded as σ (mm), and the axial preload is recorded as Fz (N). And / or the axial clearance of the bearing located on the second axial side of the rotor core is recorded as σ (mm), and the axial preload is recorded as Fz (N).

[0029] In some embodiments, optionally, the rotor core is provided with a plurality of magnet slots, which are located between the outer circumferential wall of the rotor core and the bearing, and the plurality of magnet slots are arranged at intervals along the circumference of the mounting hole, and permanent magnets are arranged in the magnet slots; along the axial direction of the rotor core, the distance d (mm) from the bearing to the rotor core, the length Lm (mm) of the permanent magnet in the first direction, the length Wm (mm) of the permanent magnet in the second direction, the thickness Lef (mm) of the core segment, the outer diameter Rr of the rotor core and the number of pole pairs p of the motor satisfy: d ≥ A4 × Wm × Lm × p / (π × Lef × Rr), A4 = 2 mm; wherein the first direction is perpendicular to the second direction, and the first direction is the direction from the mounting hole to the outer circumferential wall of the rotor core.

[0030] In this embodiment, the rotor core is provided with a plurality of magnet slots, the magnet slots are located between the outer peripheral wall of the rotor core and the bearing, and the plurality of magnet slots are arranged at intervals along the circumferential direction of the mounting hole. The magnet slots are used to assemble permanent magnets. Specifically, a permanent magnet is arranged in any magnet slot of the plurality of magnet slots. That is, a permanent magnet is arranged in each magnet slot. The magnet slots penetrate the plurality of core segments along the axial direction of the rotor core.

[0031] The relationship between the number of pole pairs of the bearing, the rotor core, the permanent magnet and the motor is further defined.

[0032] Specifically, along the axial direction of the rotor core, the distance from the bearing to the rotor core is recorded as d (mm), the length of the permanent magnet in the first direction is recorded as Lm (mm), the length of the permanent magnet in the second direction is recorded as Wm (mm), the thickness of the core segment in the axial direction of the rotor core is recorded as Lef (mm), the outer diameter of the rotor core is recorded as Rr, and the number of pole pairs of the motor is recorded as p. Among them, d, A4, Wm, Lm, p, Lef and Rr satisfy: d≥A4×Wm×Lm×p / (π×Lef×Rr), A4=2mm.

[0033] Meeting the above limitations can reduce the impact of the end magnetic leakage of the motor on the bearing, thereby reducing the mechanical friction loss of the bearing, thereby increasing the output torque of the motor, which is beneficial to improving the performance of the motor.

[0034] In some embodiments, optionally, the motor further includes: an elastic portion, which is sleeved on the rotating shaft, and the bearing portion is located between the elastic portion and the rotor core, and the elastic portion is used to apply an axial preload force to the bearing portion.

[0035] In this embodiment, the structure of the motor is further defined, so that the motor also includes an elastic part, and the elastic part is in contact with the bearing part. Specifically, the elastic part is sleeved on the rotating shaft, and the bearing part is located between the elastic part and the rotor core. The elastic part is used to apply an axial preload force to the bearing part, so that the axial preload force of the bearing part satisfies the formula definition of A1×(A2+σ)-Fz≤A3×m.

[0036] It can be understood that the motor includes a housing, a bearing cavity is provided in the housing, and the bearing portion is located in the bearing cavity. After the motor is assembled, the elastic portion is located between the bearing portion and the cavity wall of the bearing cavity, and the elastic portion is squeezed so that the axial preload force of the elastic portion on the bearing portion satisfies the formula A1×(A2+σ)-Fz≤A3×m.

[0037] In some embodiments, optionally, the maximum value R1 of the outer diameter of the elastic portion, the minimum value R2 of the inner diameter of the elastic portion, the inner diameter R3 of the bearing and the outer diameter R4 of the bearing satisfy: 0<(R4-R1) / (R1-R2)≤1, R2≥R3.

[0038] In this embodiment, the matching structure of the elastic part and the bearing is further defined, so that the maximum value of the outer diameter of the elastic part is recorded as R1, the minimum value of the inner diameter of the elastic part is recorded as R2, the inner diameter of the bearing is recorded as R3, and the outer diameter of the bearing is recorded as R4, and the relationship between R1, R2, R3 and R4 is defined to satisfy 0<(R4-R1) / (R1-R2)≤1. In this way, while ensuring the contact area between the elastic part and the bearing and the preload force of the elastic part acting on the bearing, it is also possible to ensure that sufficient installation space is provided for the elastic part to avoid interference when the elastic part is squeezed, thereby providing structural support for ensuring the matching dimensions of the components of the motor.

[0039] If the value of (R4-R1) / (R1-R2) is less than or equal to 0, interference is likely to occur when the elastic portion is squeezed.

[0040] If the value of (R4-R1) / (R1-R2) is greater than 1, the contact area between the elastic part and the bearing is small, and the preload force applied by the elastic part to the bearing cannot be guaranteed.

[0041] In some embodiments, optionally, the elastic portion includes a wave washer or a clip spring.

[0042] In this embodiment, the type of the elastic part is further limited, for example, the elastic part includes a wave pad, and for example, the elastic part includes a clip spring.

[0043] In some embodiments, optionally, the shaft and the bearing are interference fit.

[0044] In this embodiment, the matching structure of the rotating shaft and the bearing is limited so that the rotating shaft and the bearing have an interference fit. This arrangement is beneficial to improving the overall structural stiffness of the rotor core, multiple permanent magnets, the rotating shaft and the bearing part, and enhancing the overall anti-deformation ability of the rotor core, multiple permanent magnets, the rotating shaft and the bearing part, so as to reduce the axial movement of the motor when it is working.

[0045] In some embodiments, optionally, at least a portion of the hole wall of the mounting hole is interference fit with the rotating shaft.

[0046] In this embodiment, the matching structure of the rotor core and the bearing is further defined so that at least a portion of the hole wall of the mounting hole is interference fit with the rotating shaft.

[0047] That is, a part of the hole wall of the mounting hole is in interference fit with the rotating shaft, or the entire hole wall of the mounting hole is in interference fit with the rotating shaft. This arrangement is conducive to improving the overall structural rigidity of the rotor core, multiple permanent magnets, the rotating shaft and the bearing part, and enhancing the overall anti-deformation ability of the rotor core, multiple permanent magnets, the rotating shaft and the bearing part, so as to reduce the axial movement of the motor.

[0048] In some embodiments, optionally, any two adjacent core segments are staggered in a clockwise direction; or any two adjacent core segments are staggered in a counterclockwise direction.

[0049] In this embodiment, a specific arrangement structure of the plurality of core segments is specifically defined.

[0050] Specifically, any two adjacent core segments among the plurality of core segments are staggered in a clockwise direction.

[0051] Or any two adjacent core segments among the multiple core segments are staggered in the counterclockwise direction.

[0052] In some embodiments, optionally, multiple core segments are divided into a first core group and a second core group, and the first core group and the second core group each include multiple core segments; the staggered angle between two adjacent core segments in the first core group and the second core group is greater than or equal to 0°; in the first core group, any two adjacent core segments are staggered in a clockwise direction, and the staggered angle between any two adjacent core segments is denoted as b1; in the second core group, any two adjacent core segments are staggered in a counterclockwise direction, and the staggered angle between any two adjacent core segments is denoted as b2; wherein, b1 and b2 are not equal.

[0053] In this embodiment, a specific arrangement structure of the plurality of core segments is specifically defined.

[0054] The first type is that the staggered angle between two adjacent core segments in the first core group and the second core group is equal to 0°. In the first core group, any two adjacent core segments are staggered in the clockwise direction, and the staggered angle between any two adjacent core segments is recorded as b1. In the second core group, any two adjacent core segments are staggered in the counterclockwise direction, and the staggered angle between any two adjacent core segments is recorded as b2. Among them, b1 and b2 are not equal.

[0055] The second type is that the staggered angle between two adjacent core segments in the first core group and the second core group is greater than 0°. In the first core group, any two adjacent core segments are staggered in the clockwise direction, and the staggered angle between any two adjacent core segments is recorded as b1. In the second core group, any two adjacent core segments are staggered in the counterclockwise direction, and the staggered angle between any two adjacent core segments is recorded as b2. Among them, b1 and b2 are not equal.

[0056] Specifically, the positioning surface and the positioning line are defined. Specifically, the line between the center of the mounting hole and the center of the magnet slot extends along the axial direction of the rotating shaft to form the positioning surface, and the line between the center of the portion of the rotor core located between two adjacent magnet slots and the center of the mounting hole is the positioning line. The angle between the positioning line and the positioning surface is the staggered angle of two adjacent core segments.

[0057] A second aspect of the present application provides a chassis system, comprising: the motor as in the first aspect.

[0058] The chassis system provided in the present application includes the motor as in the first aspect, and therefore has all the beneficial effects of the above-mentioned motor, which will not be described one by one here.

[0059] Optionally, the chassis system includes a transmission system, a driving system, a steering system (such as an electric power steering system) and a braking system. The chassis system is used to support and install the vehicle engine and its components to form the overall shape of the vehicle, and receive the power of the engine to make the vehicle move and ensure normal driving.

[0060] A third aspect of the present application provides a vehicle, comprising: the motor as in the first aspect; or the chassis system as in the second aspect.

[0061] The vehicle provided in the present application includes the motor as in the first aspect or the chassis system as in the second aspect, and therefore has all the beneficial effects of the above-mentioned motor or chassis system, which will not be stated one by one here.

[0062] It is worth noting that the vehicle can be a new energy vehicle, which includes pure electric vehicles, extended-range electric vehicles, hybrid electric vehicles, fuel cell electric vehicles, hydrogen engine vehicles, etc.

[0063] Additional aspects and advantages of the present application will become apparent in the following description or will be learned through practice of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0064] The above and / or additional aspects and advantages of the present application will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0065] Figure 1A schematic diagram of the first part of the structure of a motor according to an embodiment of the present application is shown;

[0066] Figure 2 A schematic diagram showing the dimension marking of a first part of the structure of a motor according to an embodiment of the present application is shown;

[0067] Figure 3 A schematic diagram of the second part of the structure of a motor according to an embodiment of the present application is shown;

[0068] Figure 4 A schematic structural diagram of an elastic portion of an embodiment of the present application is shown;

[0069] Figure 5 A schematic structural diagram of a bearing according to an embodiment of the present application is shown;

[0070] Figure 6 A schematic structural diagram of a bearing and a rotating shaft according to an embodiment of the present application is shown;

[0071] Figure 7 A schematic diagram of a curve showing the change of the vibration amplitude as X changes according to an embodiment of the present application is shown;

[0072] Figure 8 A schematic diagram of a curve showing the change of vibration amplitude with σ according to an embodiment of the present application is shown;

[0073] Fig. 9 A schematic diagram of a curve showing the change of axial force with displacement according to an embodiment of the present application is shown;

[0074] Fig.10 A schematic diagram showing a curve of output torque changing with changes in X1 according to an embodiment of the present application;

[0075] Fig.11 A schematic structural diagram of a rotor core according to a first embodiment of the present application is shown;

[0076] Fig.12 A schematic structural diagram of a rotor core according to a second embodiment of the present application is shown;

[0077] Fig.13 A schematic structural diagram of a rotor core according to a third embodiment of the present application is shown;

[0078] Fig.14 A schematic structural diagram of a rotor core according to a fourth embodiment of the present application is shown.

[0079] in, Figures 1 to 7 , Fig.11 , Fig.12 , Fig.13 and Fig.14The corresponding relationship between the reference numerals and component names in the figure is:

[0080] 10 motor, 100 rotor core, 110 core segments, 110a first core segment, 110b second core segment, 110c third core segment, 110d fourth core segment, 112 mounting hole, 114 magnet slot, 120 outer peripheral wall of the rotor core, 130 first core group, 140 second core group, 200 permanent magnet, 300 rotating shaft, 400 bearing part, 410 bearing, 412 inner ring, 414 outer ring, 500 elastic part, 600 positioning surface, 700 positioning line. DETAILED DESCRIPTION

[0081] In order to more clearly understand the above-mentioned purposes, features and advantages of the present application, the present application is further described in detail below in conjunction with the accompanying drawings and specific implementation methods. It should be noted that the embodiments of the present application and the features in the embodiments can be combined with each other without conflict.

[0082] In the following description, many specific details are set forth to facilitate a full understanding of the present application. However, the present application may also be implemented in other ways different from those described herein. Therefore, the scope of protection of the present application is not limited to the specific embodiments disclosed below.

[0083] Refer to the following Figures 1 to 14 A motor 10 , a chassis system, and a vehicle according to some embodiments of the present application.

[0084] like Figure 1 , Figure 2 , Figure 5 and Figure 6 As shown, a motor 10 according to some embodiments of the present application includes a rotor core 100 , a plurality of permanent magnets 200 , a rotating shaft 300 and a bearing portion 400 .

[0085] The rotor core 100 includes a plurality of core segments 110 .

[0086] A plurality of core segments 110 are stacked.

[0087] The rotor core 100 is provided with a mounting hole 112 .

[0088] The mounting hole 112 penetrates through the plurality of core segments 110 along the axial direction of the rotor core 100 .

[0089] In at least a portion of the core segments 110 , any two adjacent core segments 110 are staggered in the circumferential direction of the rotor core 100 .

[0090] A plurality of permanent magnets 200 are provided on the rotor core 100, and the plurality of permanent magnets 200 are arranged at intervals along the circumferential direction of the mounting hole 112.

[0091] The rotating shaft 300 passes through the mounting hole 112 .

[0092] The bearing portion 400 is sleeved on a portion of the rotating shaft 300 located outside the rotor core 100 .

[0093] The axial play of the bearing portion 400 is represented by σ (mm).

[0094] The axial preload force of the bearing portion 400 is denoted as Fz (N).

[0095] The total weight of the rotor core 100 , the plurality of permanent magnets 200 , the rotation shaft 300 , and the bearing 400 is expressed as m (kg).

[0096] Among them, A1×(A2+σ)-Fz≤A3×m, A1=100(N / mm), A2=0.88mm, A3=9.8(N / kg).

[0097] The motor 10 provided in the present application includes a rotor core 100 , a plurality of permanent magnets 200 , a rotating shaft 300 , and a bearing portion 400 .

[0098] The rotor core 100 includes a plurality of core segments 110, which are stacked in the axial direction of the rotor core 100. The rotor core 100 is provided with a mounting hole 112, which penetrates the plurality of core segments 110 in the axial direction of the rotor core 100.

[0099] The mounting hole 112 is used to assemble the rotating shaft 300 . Specifically, the rotating shaft 300 passes through the mounting hole 112 .

[0100] A plurality of permanent magnets 200 are disposed on the rotor core 100 , and the plurality of permanent magnets 200 are arranged at intervals along the circumferential direction of the mounting hole 112 .

[0101] The bearing portion 400 is sleeved on the portion of the rotating shaft 300 located outside the rotor core 100 . That is, the bearing portion 400 is sleeved on the rotating shaft 300 , and the bearing portion 400 is located on one side of the rotor core 100 .

[0102] Among them, in at least a portion of the core segments 110, any two adjacent core segments 110 are staggered in the circumferential direction of the rotor core 100. That is, in at least a portion of the core segments 110, any two adjacent core segments 110 are staggered in the circumferential direction of the rotor core 100 to form rotor skew poles. The segmented modular arrangement of the rotor core 100 has the advantages of easy installation and maintenance, and skew poles can be formed between multiple core segments 110.

[0103] The tooth harmonics of the motor 10 are the main source of the vibration noise of the motor 10. Therefore, limiting the staggered arrangement of any two adjacent core segments 110 in the circumferential direction of the rotor core 100 can reduce the cogging torque and torque pulsation, thereby reducing the electromagnetic vibration. In other words, by dividing the rotor core 100 into a plurality of core segments 110 and staggering any two adjacent core segments 110 in the circumferential direction of the rotor core 100, the specific harmonic content in the motor 10 can be effectively suppressed, and the torque pulsation and cogging torque of the motor 10 can be improved, thereby achieving the effect of reducing the vibration noise of the motor 10.

[0104] In addition, the axial clearance σ (mm) of the bearing part 400, the axial preload Fz (N) of the bearing part 400, the sum of the weights m (kg) of the rotor core 100, the plurality of permanent magnets 200, the shaft 300 and the bearing part 400, A1, A2 and A3 satisfy: A1×(A2+σ)-Fz≤A3×m, A1=100(N / mm), A2=0.88mm, A3=9.8(N / kg). This setting further defines the matching structure of the rotor core 100, the plurality of permanent magnets 200, the shaft 300 and the bearing part 400. Specifically, the relationship between σ, Fz and m is further defined. By limiting the relationship between the above parameters, the overall structural stiffness of the rotor core 100, multiple permanent magnets 200, the rotating shaft 300 and the bearing part 400 can be enhanced, and the overall anti-deformation ability of the rotor core 100, multiple permanent magnets 200, the rotating shaft 300 and the bearing part 400 can be enhanced, and the axial movement of the motor 10 during operation can be reduced. In this way, the vibration performance of the motor 10 during operation is improved, and the vibration noise of the motor 10 can be further reduced.

[0105] It is understandable that if Figure 5 and Figure 6 As shown, when there is no load, the inner ring 412 of the bearing part 400 is fixed, and the displacement of the outer ring 414 of the bearing part 400 from one extreme position to another extreme position along the axial direction of the rotor core 100 relative to the fixed inner ring 412 is recorded as the axial clearance σ of the bearing part 400. Alternatively, when there is no load, the outer ring 414 of the bearing part 400 is fixed, and the displacement of the inner ring 412 of the bearing part 400 from one extreme position to another extreme position along the axial direction of the rotor core 100 relative to the fixed outer ring 414 is recorded as the axial clearance σ of the bearing part 400.

[0106] It can also be said that Figure 6 As shown, it can also be said that when the outer ring 414 or the outer ring 414 of the bearing portion 400 is subjected to an external axial force, the inner ring 412 and the outer ring 414 will produce an axial displacement, and the maximum value of the axial displacement is the axial clearance σ of the bearing 410, where, Figure 6 The arrow at Fz indicates the direction of force.

[0107] In some embodiments, optionally, σ≤0.05 mm.

[0108] In this embodiment, the value range of the axial clearance σ of the bearing portion 400 is further limited so that σ≤0.05 mm. In this way, the axial vibration of the motor 10 can be further optimized to further optimize the vibration noise of the motor 10 .

[0109] Optionally, σ=0.45 mm, σ=0.04 mm, σ=0.035 mm, σ=0.03 mm and σ=0.025 mm, etc., which are not listed here one by one.

[0110] In some embodiments, optionally, Figure 1 and Figure 2 As shown, the bearing portion 400 includes at least one bearing 410 .

[0111] The bearing 410 is located between the end of the rotating shaft 300 and the rotor core 100 .

[0112] In this embodiment, the structure of the bearing portion 400 is further defined such that the bearing portion 400 includes at least one bearing 410 , and the position of the bearing 410 is defined such that the bearing 410 is located between the end of the rotating shaft 300 and the rotor core 100 .

[0113] Optionally, when the bearing portion 400 includes one bearing 410 , the axial clearance of the bearing 410 is denoted as σ (mm), and the axial preload force of the bearing 410 is denoted as Fz (N).

[0114] Optionally, when the bearing portion 400 includes multiple (eg, greater than or equal to two) bearings 410, the axial clearance of any bearing 410 among the multiple bearings 410 is recorded as σ (mm), and the axial preload force of any bearing 410 among the multiple bearings 410 is recorded as Fz (N).

[0115] Optionally, when the bearing portion 400 includes multiple (e.g., greater than or equal to two) bearings 410, the axial clearance of at least some of the multiple bearings 410 is recorded as σ (mm), and the axial preload force of at least some of the multiple bearings 410 is recorded as Fz (N).

[0116] In some embodiments, optionally, Figure 1 and Figure 2 As shown, when there are multiple bearings 410 , some of the bearings 410 are located on a first axial side of the rotor core 100 , and another part of the bearings 410 are located on a second axial side of the rotor core 100 .

[0117] In this embodiment, when the number of bearings 410 is multiple, the matching structure of the multiple bearings 410 and the rotor core 100 is defined so that a portion of the multiple bearings 410 are located on the axial first side of the rotor core 100, and another portion of the multiple bearings 410 are located on the axial second side of the rotor core 100.

[0118] Optionally, the axial clearance of the bearing 410 located on the first axial side of the rotor core 100 is recorded as σ (mm), and the axial preload is recorded as Fz (N). And / or the axial clearance of the bearing 410 located on the second axial side of the rotor core 100 is recorded as σ (mm), and the axial preload is recorded as Fz (N).

[0119] In some embodiments, optionally, Figure 1 and Figure 2 As shown, the rotor core 100 is provided with a plurality of magnet slots 114 , and the magnet slots 114 are located between the outer peripheral wall 120 of the rotor core and the bearing 410 .

[0120] A plurality of magnet slots 114 are arranged at intervals along the circumference of the mounting hole 112 .

[0121] A permanent magnet 200 is disposed in the magnet slot 114 .

[0122] Along the axial direction of the rotor core 100 , the distance from the bearing 410 to the rotor core 100 is denoted as d (mm).

[0123] The length of the permanent magnet 200 in the first direction is denoted as Lm (mm).

[0124] The length of the permanent magnet 200 in the second direction is denoted as Wm (mm).

[0125] The thickness of the core segment 110 is denoted as Lef (mm).

[0126] The outer diameter of the rotor core 100 is denoted by Rr.

[0127] The number of pole pairs of the motor 10 is denoted by p.

[0128] d, A4, Wm, Lm, p, Lef and Rr satisfy: d≥A4×Wm×Lm×p / (π×Lef×Rr), A4=2mm.

[0129] The first direction is perpendicular to the second direction, and the first direction is a direction from the mounting hole 112 to the outer peripheral wall 120 of the rotor core.

[0130] In this embodiment, the rotor core 100 is provided with a plurality of magnet slots 114, which are located between the outer peripheral wall 120 of the rotor core and the bearing 410, and the plurality of magnet slots 114 are arranged at intervals along the circumferential direction of the mounting hole 112. The magnet slots 114 are used to assemble the permanent magnets 200. Specifically, a permanent magnet 200 is disposed in any magnet slot 114 of the plurality of magnet slots 114. That is, a permanent magnet 200 is disposed in each magnet slot 114.

[0131] The relationship among the number of pole pairs of the bearing 410 , the rotor core 100 , the permanent magnet 200 , and the motor 10 is further defined.

[0132] Specifically, along the axial direction of the rotor core 100, the distance from the bearing 410 to the rotor core 100 is recorded as d (mm), the length of the permanent magnet 200 in the first direction is recorded as Lm (mm), the length of the permanent magnet 200 in the second direction is recorded as Wm (mm), the thickness of the core segment 110 in the axial direction of the rotor core 100 is recorded as Lef (mm), the outer diameter of the rotor core 100 is recorded as Rr, and the number of pole pairs of the motor 10 is recorded as p. Among them, d, A4, Wm, Lm, p, Lef and Rr satisfy: d≥A4×Wm×Lm×p / (π×Lef×Rr), A4=2mm.

[0133] By meeting the above limitations, the influence of the end magnetic leakage of the motor 10 on the bearing 410 can be reduced, so as to reduce the mechanical friction loss of the bearing 410, thereby increasing the output torque of the motor 10, which is beneficial to improving the performance of the motor 10.

[0134] In some embodiments, optionally, Figure 3 As shown, the motor 10 further includes an elastic portion 500 .

[0135] The elastic portion 500 is sleeved on the rotating shaft 300 , and the bearing portion 400 is located between the elastic portion 500 and the rotor core 100 .

[0136] The elastic portion 500 is used to apply an axial preload force to the bearing portion 400 .

[0137] In this embodiment, the structure of the motor 10 is further defined, so that the motor 10 further includes an elastic portion 500, and the elastic portion 500 is in contact with the bearing portion 400. Specifically, the elastic portion 500 is sleeved on the rotating shaft 300, and the bearing portion 400 is located between the elastic portion 500 and the rotor core 100. The elastic portion 500 is used to apply an axial preload force to the bearing portion 400, so that the axial preload force of the bearing portion 400 satisfies the formula definition of A1×(A2+σ)-Fz≤A3×m.

[0138] It is understandable that the motor 10 includes a housing, a bearing 410 cavity is provided in the housing, and the bearing portion 400 is located in the bearing 410 cavity. After the motor 10 is assembled, the elastic portion 500 is located between the bearing portion 400 and the cavity wall of the bearing 410 cavity, and the elastic portion 500 is squeezed so that the axial preload force of the elastic portion 500 acting on the bearing portion 400 satisfies the formula definition of A1×(A2+σ)-Fz≤A3×m.

[0139] In some embodiments, optionally, Figure 4 , Figure 5 and Figure 6 As shown, the maximum value of the outer diameter of the elastic portion 500 is represented by R1.

[0140] The minimum value of the inner diameter of the elastic portion 500 is represented by R2.

[0141] The inner diameter of the bearing 410 is denoted as R3.

[0142] The outer diameter of the bearing 410 is denoted as R4.

[0143] R1, R2, R3 and R4 satisfy: 0<(R4-R1) / (R1-R2)≤1, R2≥R3.

[0144] In this embodiment, the matching structure of the elastic part 500 and the bearing 410 is further defined, so that the maximum value of the outer diameter of the elastic part 500 is recorded as R1, the minimum value of the inner diameter of the elastic part 500 is recorded as R2, the inner diameter of the bearing 410 is recorded as R3, and the outer diameter of the bearing 410 is recorded as R4, and the relationship between R1, R2, R3 and R4 is defined to satisfy 0<(R4-R1) / (R1-R2)≤1. In this way, the contact area between the elastic part 500 and the bearing 410 can be guaranteed. While ensuring the preload force of the elastic part 500 acting on the bearing 410, it is also possible to ensure that sufficient installation space is provided for the elastic part 500, avoiding interference when the elastic part 500 is squeezed, and providing structural support for ensuring the matching dimensions of the components of the motor 10.

[0145] If the value of (R4-R1) / (R1-R2) is less than or equal to 0, interference is likely to occur when the elastic portion 500 is squeezed.

[0146] If the value of (R4-R1) / (R1-R2) is greater than 1, the contact area between the elastic part 500 and the bearing 410 is small, and the preload force applied by the elastic part 500 to the bearing 410 cannot be guaranteed.

[0147] Optionally, (R4-R1) / (R1-R2)=0.2, (R4-R1) / (R1-R2)=0.4, (R4-R1) / (R1-R2)=0.5, (R4-R1) / (R1-R2)=0.7 and (R4-R1) / (R1-R2)=0.9, etc., which are not listed here one by one.

[0148] In some embodiments, optionally, the elastic portion 500 includes a wave washer or a clip spring.

[0149] In this embodiment, the type of the elastic part 500 is further limited, for example, the elastic part 500 includes a wave pad, for example, the elastic part 500 includes a clip spring.

[0150] In some embodiments, optionally, the rotating shaft 300 and the bearing 410 are interference fit.

[0151] In this embodiment, the matching structure of the rotating shaft 300 and the bearing 410 is limited so that the rotating shaft 300 and the bearing 410 are interference fit. This arrangement is beneficial to improving the overall structural stiffness of the rotor core 100, multiple permanent magnets 200, the rotating shaft 300 and the bearing part 400, and enhancing the overall anti-deformation ability of the rotor core 100, multiple permanent magnets 200, the rotating shaft 300 and the bearing part 400, so as to reduce the axial movement of the motor 10 when it is working.

[0152] In some embodiments, optionally, at least a portion of the hole wall of the mounting hole 112 is interference fit with the rotating shaft 300 .

[0153] In this embodiment, the matching structure between the rotor core 100 and the bearing 410 is further defined so that at least a portion of the hole wall of the mounting hole 112 is interference-fitted with the rotating shaft 300 .

[0154] That is, a part of the hole wall of the mounting hole 112 is in interference fit with the rotating shaft 300, or the entire hole wall of the mounting hole 112 is in interference fit with the rotating shaft 300. This arrangement is conducive to improving the overall structural rigidity of the rotor core 100, the plurality of permanent magnets 200, the rotating shaft 300 and the bearing part 400, and enhancing the overall anti-deformation ability of the rotor core 100, the plurality of permanent magnets 200, the rotating shaft 300 and the bearing part 400, so as to reduce the axial movement of the motor 10 when it is working.

[0155] According to some other embodiments of the present application, the chassis system includes: the motor 10 as in any of the above embodiments.

[0156] The chassis system provided in the present application includes a motor 10 .

[0157] The motor 10 includes a rotor core 100 , a plurality of permanent magnets 200 , a rotating shaft 300 , and a bearing portion 400 .

[0158] The rotor core 100 includes a plurality of core segments 110, and the plurality of core segments 110 are stacked along the axial direction of the rotor core 100. The rotor core 100 is provided with a mounting hole 112 and a plurality of magnet slots 114, the mounting hole 112 penetrates the plurality of core segments 110 along the axial direction of the rotor core 100, and any magnet slot 114 of the plurality of magnet slots 114 penetrates the plurality of core segments 110 along the axial direction of the rotor core 100.

[0159] The mounting hole 112 is used to assemble the rotating shaft 300. Specifically, the rotating shaft 300 is passed through the mounting hole 112. The magnet slot 114 is used to assemble the permanent magnet 200. Specifically, any magnet slot 114 of the plurality of magnet slots 114 has a permanent magnet 200 therein, that is, each magnet slot 114 has a permanent magnet 200 therein.

[0160] The bearing portion 400 is sleeved on the portion of the rotating shaft 300 located outside the rotor core 100 . That is, the bearing portion 400 is sleeved on the rotating shaft 300 , and the bearing portion 400 is located on one side of the rotor core 100 .

[0161] Among them, any two adjacent core segments 110 are staggered in the circumferential direction of the rotor core 100. That is, any two adjacent core segments 110 are staggered in the circumferential direction of the rotor core 100 to form rotor skew poles, and the segmented modular setting of the rotor core 100 has the advantages of easy installation and maintenance, and skew poles can be formed between multiple core segments 110.

[0162] The tooth harmonics of the motor 10 are the main source of the vibration noise of the motor 10. Therefore, limiting the staggered arrangement of any two adjacent core segments 110 in the circumferential direction of the rotor core 100 can reduce the cogging torque and torque pulsation, thereby reducing the electromagnetic vibration. In other words, by dividing the rotor core 100 into a plurality of core segments 110 and staggering any two adjacent core segments 110 in the circumferential direction of the rotor core 100, the specific harmonic content in the motor 10 can be effectively suppressed, and the torque pulsation and cogging torque of the motor 10 can be improved, thereby achieving the effect of reducing the vibration noise of the motor 10.

[0163] In addition, the axial clearance σ (mm) of the bearing part 400, the axial preload Fz (N) of the bearing part 400, the sum of the weights m (kg) of the rotor core 100, the plurality of permanent magnets 200, the shaft 300 and the bearing part 400, A1, A2 and A3 satisfy: A1×(A2+σ)-Fz≤A3×m, A1=100(N / mm), A2=0.88mm, A3=9.8(N / kg). This setting further defines the matching structure of the rotor core 100, the plurality of permanent magnets 200, the shaft 300 and the bearing part 400. Specifically, the relationship between σ, Fz and m is further defined. By limiting the relationship between the above parameters, the overall structural stiffness of the rotor core 100, multiple permanent magnets 200, the rotating shaft 300 and the bearing part 400 can be enhanced, and the overall anti-deformation ability of the rotor core 100, multiple permanent magnets 200, the rotating shaft 300 and the bearing part 400 can be enhanced, and the axial movement of the motor 10 during operation can be reduced. In this way, the vibration performance of the motor 10 during operation is improved, and the vibration noise of the motor 10 can be further reduced.

[0164] Optionally, the chassis system includes a transmission system, a driving system, a steering system (such as an electric power steering system) and a braking system. The chassis system is used to support and install the vehicle engine and its components to form the overall shape of the vehicle, and receive the power of the engine to make the vehicle move and ensure normal driving.

[0165] According to some further embodiments of the present application, the vehicle includes: the motor 10 as in any of the above embodiments; or the chassis system as in the above embodiments.

[0166] The vehicle provided in the present application includes a motor 10 or a chassis system.

[0167] The chassis system includes an electric machine 10 .

[0168] The motor 10 includes a rotor core 100 , a plurality of permanent magnets 200 , a rotating shaft 300 , and a bearing portion 400 .

[0169] The rotor core 100 includes a plurality of core segments 110, and the plurality of core segments 110 are stacked along the axial direction of the rotor core 100. The rotor core 100 is provided with a mounting hole 112 and a plurality of magnet slots 114, the mounting hole 112 penetrates the plurality of core segments 110 along the axial direction of the rotor core 100, and any magnet slot 114 of the plurality of magnet slots 114 penetrates the plurality of core segments 110 along the axial direction of the rotor core 100.

[0170] The mounting hole 112 is used to assemble the rotating shaft 300. Specifically, the rotating shaft 300 is passed through the mounting hole 112. The magnet slot 114 is used to assemble the permanent magnet 200. Specifically, any magnet slot 114 of the plurality of magnet slots 114 has a permanent magnet 200 therein, that is, each magnet slot 114 has a permanent magnet 200 therein.

[0171] The bearing portion 400 is sleeved on the portion of the rotating shaft 300 located outside the rotor core 100 . That is, the bearing portion 400 is sleeved on the rotating shaft 300 , and the bearing portion 400 is located on one side of the rotor core 100 .

[0172] Among them, any two adjacent core segments 110 are staggered in the circumferential direction of the rotor core 100. That is, any two adjacent core segments 110 are staggered in the circumferential direction of the rotor core 100 to form rotor skew poles, and the segmented modular setting of the rotor core 100 has the advantages of easy installation and maintenance, and skew poles can be formed between multiple core segments 110.

[0173] The tooth harmonics of the motor 10 are the main source of the vibration noise of the motor 10. Therefore, limiting the staggered arrangement of any two adjacent core segments 110 in the circumferential direction of the rotor core 100 can reduce the cogging torque and torque pulsation, thereby reducing the electromagnetic vibration. In other words, by dividing the rotor core 100 into a plurality of core segments 110 and staggering any two adjacent core segments 110 in the circumferential direction of the rotor core 100, the specific harmonic content in the motor 10 can be effectively suppressed, and the torque pulsation and cogging torque of the motor 10 can be improved, thereby achieving the effect of reducing the vibration noise of the motor 10.

[0174] In addition, the axial clearance σ (mm) of the bearing part 400, the axial preload Fz (N) of the bearing part 400, the sum of the weights m (kg) of the rotor core 100, the plurality of permanent magnets 200, the shaft 300 and the bearing part 400, A1, A2 and A3 satisfy: A1×(A2+σ)-Fz≤A3×m, A1=100(N / mm), A2=0.88mm, A3=9.8(N / kg). This setting further defines the matching structure of the rotor core 100, the plurality of permanent magnets 200, the shaft 300 and the bearing part 400. Specifically, the relationship between σ, Fz and m is further defined. By limiting the relationship between the above parameters, the overall structural stiffness of the rotor core 100, multiple permanent magnets 200, the rotating shaft 300 and the bearing part 400 can be enhanced, and the overall anti-deformation ability of the rotor core 100, multiple permanent magnets 200, the rotating shaft 300 and the bearing part 400 can be enhanced, and the axial movement of the motor 10 during operation can be reduced. In this way, the vibration performance of the motor 10 during operation is improved, and the vibration noise of the motor 10 can be further reduced.

[0175] Optionally, the rotor includes a rotor core 100 (the rotor core 100 includes a plurality of core segments 110), a plurality of permanent magnets 200, a rotating shaft 300 and at least one bearing 410. The rotor core 100 is provided with a mounting hole 112 and a plurality of magnet slots 114, and the plurality of permanent magnets 200 are distributed along the circumference of the rotor core 100, and a permanent magnet 200 is arranged in each magnet slot 114. The number of core segments 110 is greater than or equal to 2. Any two adjacent core segments 110 are staggered in the circumferential direction of the rotor core 100. The rotating shaft 300 is placed in the mounting hole 112 of the rotor core 100, and a bearing 410 is provided on at least one side of the rotating shaft 300, and the bearing 410 has an inner ring 412 and an outer ring 414. When the outer ring 414 or the inner ring 412 is subjected to an external axial force, the inner ring 412 and the outer ring 414 will produce axial displacement, and the maximum value of the axial displacement is the axial clearance σ of the bearing 410. As Figure 6 As shown, the outer ring 414 of the bearing 410 is subjected to an axial preload force Fz (N). The sum of the weights of the rotor core 100, the plurality of permanent magnets 200, the shaft 300 and the bearing 400 is denoted as m (kg).

[0176] Among them, (A1×(A2+σ)-Fz) / (A3×m)≤1.

[0177] Among them, σ≤0.05mm.

[0178] The axial preload force Fz of the bearing 410 is provided by spring steel (ie, the elastic portion 500 ), for example, the spring steel includes a wave washer or a retaining spring, etc., which are not listed here one by one.

[0179] The core segment 110 includes a plurality of stacked rotor sheets. The assembly method of the plurality of rotor sheets includes any one of the following or a combination thereof: riveting, welding and gluing.

[0180] A partial surface area or the entire surface area of ​​the hole wall of the mounting hole 112 of the rotor core 100 and the rotating shaft 300 adopt an interference fit.

[0181] The rotating shaft 300 and the bearing 410 are interference fit.

[0182] Optionally, let (A1×(A2+σ)-Fz) / (A3×m)=X. Taking the motor 10 with 12 slots and 8 poles as an example, m=0.447 kg, axial clearance σ=0.11 mm, and X changes with the change of the axial preload force Fz. Figure 7 is the trend of the vibration amplitude of the main order (e.g., 24th order) of the motor 10 as X changes, given by Figure 7 It can be seen that when Fz≥94.6N, that is, X≤1, the vibration amplitude of the motor 10 is better.

[0183] Optionally, a motor 10 with 12 slots and 8 poles is taken as an example, and σ≤0.05 mm. Figure 8 The trend of the vibration amplitude of the main order (e.g., 24th order) of the motor 10 as σ changes is shown. Figure 8 It can be seen that when σ≤0.05 mm, the vibration amplitude of the motor 10 is better.

[0184] Alternatively, if Fig. 9 As shown, an axial force Fz is continuously applied to the outer ring 414 of the bearing 410, and the value of the axial force obtained by the test changes with the displacement of the inner ring 412 and the outer ring 414 of the bearing 410. Fig. 9 As shown, as the slope changes, two inflection points op1 and op2 appear on the curve, and the axial clearance σ is the difference in displacement between op1 and op2. Fig. 9 It shows that σ=0.155-0.04=0.115. The axial preload force Fz is the minimum value of the force between op1 and op2. Fig. 9 It is shown that Fz=75N.

[0185] Along the axial direction of the rotor core 100, the distance d (mm) from the bearing 410 to the rotor core 100, the length Lm (mm) of the permanent magnet 200 in the first direction, the length Wm (mm) of the permanent magnet 200 in the second direction, the thickness Lef (mm) of the core segment 110, the outer diameter Rr of the rotor core 100 and the number of pole pairs p of the motor 10 satisfy: d ≥ A4 × Wm × Lm × p / (π × Lef × Rr), A4 = 2mm. Satisfying the above formula can reduce the influence of the end leakage magnetic field of the motor 10 on the bearing 410, reduce the mechanical friction loss of the bearing 410, and thus improve the output torque of the motor 10.

[0186] Alternatively, if Fig.10 As shown, let (d×π×Lef×Rr) / (A4×Wm×Lm×p)=X1. When X1≥1, that is, d≥A4×Wm×Lm×p / (π×Lef×Rr), the output torque of the motor 10 is better.

[0187] The outer diameter of the outer ring 414 of the bearing 410 is recorded as R4, and the outer diameter of the inner ring 412 of the bearing 410 is recorded as R3. When the wave pad is free and not subjected to force, the maximum outer diameter of the outer edge of the wave pad is recorded as R1, and the minimum inner diameter of the inner edge of the wave pad is recorded as R2, wherein 0<(R4-R1) / (R1-R2)≤1, R2≥R3. Meeting the above formula restrictions can ensure reasonable installation and working space of the wave pad.

[0188] In some embodiments, optionally, Fig.11 , Fig.12 and Fig.13 As shown, any two adjacent core segments 110 are staggered in a clockwise direction; or any two adjacent core segments 110 are staggered in a counterclockwise direction.

[0189] In this embodiment, a specific arrangement structure of the plurality of core segments 110 is specifically defined.

[0190] Specifically, any two adjacent core segments 110 among the plurality of core segments 110 are staggered in a clockwise direction.

[0191] Alternatively, any two adjacent core segments 110 among the plurality of core segments 110 are staggered in the counterclockwise direction.

[0192] Among them, Fig.12 As shown, the staggered angle between any two adjacent core segments 110 is b.

[0193] In some embodiments, optionally, Fig.14 As shown, a plurality of core segments 110 are divided into a first core group 130 and a second core group 140, and the first core group 130 and the second core group 140 each include a plurality of core segments 110; the staggered angle between two adjacent core segments 110 in the first core group 130 and the second core group 140 is greater than or equal to 0°; in the first core group 130, any two adjacent core segments 110 are staggered in a clockwise direction, and the staggered angle between any two adjacent core segments 110 is denoted as b1; in the second core group 140, any two adjacent core segments 110 are staggered in a counterclockwise direction, and the staggered angle between any two adjacent core segments 110 is denoted as b2; wherein b1 and b2 are not equal.

[0194] In this embodiment, a specific arrangement structure of the plurality of core segments 110 is specifically defined.

[0195] The first one, such as Fig.14 As shown, the staggered angle of two adjacent core segments 110 in the first core group 130 and the second core group 140 is equal to 0°. In the first core group 130, any two adjacent core segments 110 are staggered in the clockwise direction, and the staggered angle of any two adjacent core segments 110 is recorded as b1. In the second core group 140, any two adjacent core segments 110 are staggered in the counterclockwise direction, and the staggered angle of any two adjacent core segments 110 is recorded as b2. Wherein, b1 and b2 are not equal.

[0196] The second type is that the staggered angle of two adjacent core segments 110 in the first core group 130 and the second core group 140 is greater than 0°. In the first core group 130, any two adjacent core segments 110 are staggered in the clockwise direction, and the staggered angle of any two adjacent core segments 110 is recorded as b1. In the second core group 140, any two adjacent core segments 110 are staggered in the counterclockwise direction, and the staggered angle of any two adjacent core segments 110 is recorded as b2. Among them, b1 and b2 are not equal.

[0197] Specifically, Fig.12 As shown, a positioning surface 600 and a positioning line 700 are defined. Specifically, the line between the center of the mounting hole 112 and the center of the magnet slot 114 extends along the axial direction of the rotating shaft 300 to form the positioning surface 600, and the line between the center of the portion of the rotor core 100 located between two adjacent magnet slots 114 and the center of the mounting hole 112 is the positioning line 700. The angle b between the positioning line 700 and the positioning surface 600 is the positioning angle. When the core segment 110 rotates along the circumferential direction of the rotor core 100, the positioning surface 600 is set to be stationary, one end point of the positioning line 700 (i.e., the center of the mounting hole 112) is stationary, and the other end point of the positioning line 700 (i.e., the center of the portion of the rotor core 100 located between two adjacent magnet slots 114) rotates accordingly. The difference in the positioning angles of two adjacent core segments 110 is the staggered angle of the two adjacent core segments 110.

[0198] like Fig.14 As shown, the first core group 130 includes a first core segment 110a and a second core segment 110b, and the second core group 140 includes a third core segment 110c and a fourth core segment 110d. The first core segment 110a and the third core segment 110c are arranged adjacent to each other. The staggered angle between the first core segment 110a and the third core segment 110c is 0°. The staggered angle between the second core segment 110b and the first core segment 110a is b1, and the staggered angle between the third core segment 110c and the fourth core segment 110d is b2, and b1 is not equal to b2.

[0199] In this application, the term "plurality" means two or more than two, unless otherwise clearly defined. The terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral connection; "connected" can be a direct connection or an indirect connection through an intermediate medium. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to the specific circumstances.

[0200] In the description of this specification, the description of the terms "one embodiment", "some embodiments", "specific embodiments", etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in a suitable manner in any one or more embodiments or examples. The above description is only a preferred embodiment of the present application and is not intended to limit the present application. For those skilled in the art, the present application may have various changes and variations. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present application shall be included in the scope of protection of the present application.

Claims

1. A motor, characterized in that: include: A rotor core, the rotor core comprising a plurality of core segments, the plurality of core segments being stacked, the rotor core being provided with a mounting hole, the mounting hole penetrating the plurality of core segments along the axial direction of the rotor core; In at least a portion of the core segments, any two adjacent core segments are staggered in the circumferential direction of the rotor core; A plurality of permanent magnets are disposed on the rotor core, and the plurality of permanent magnets are spaced apart along the circumference of the mounting hole; A rotating shaft is passed through the mounting hole; A bearing portion, sleeved on a portion of the rotating shaft located outside the rotor core; The axial clearance of the bearing portion is denoted as σ (mm), the axial preload of the bearing portion is denoted as Fz (N), and the sum of the weights of the rotor core, the plurality of permanent magnets, the rotating shaft and the bearing portion is denoted as m (kg); Among them, A1×(A2+σ)-Fz≤A3×m, A1=100(N / mm), A2=0.88mm, A3=9.8(N / kg).

2. The motor according to claim 1, characterized in that σ≤0.05mm.

3. The motor according to claim 1 or 2, characterized in that: The bearing portion includes at least one bearing, and the bearing is located between an end portion of the rotating shaft and the rotor core.

4. The motor according to claim 3, characterized in that When there are multiple bearings, some of the bearings are located on a first axial side of the rotor core, and another part of the bearings are located on a second axial side of the rotor core.

5. The motor according to claim 3, characterized in that The rotor core is provided with a plurality of magnet slots, the magnet slots are located between the outer peripheral wall of the rotor core and the bearing, and the plurality of magnet slots are arranged at intervals along the circumferential direction of the mounting hole, and the permanent magnets are arranged in the magnet slots; Along the axial direction of the rotor core, the distance d (mm) from the bearing to the rotor core, the length Lm (mm) of the permanent magnet in the first direction, the length Wm (mm) of the permanent magnet in the second direction, the thickness Lef (mm) of the core segment, the outer diameter Rr of the rotor core and the number of pole pairs p of the motor satisfy: d ≥ A4 × Wm × Lm × p / (π × Lef × Rr), A4 = 2 mm; The first direction is perpendicular to the second direction, and the first direction is a direction from the mounting hole to the outer peripheral wall of the rotor core.

6. The motor according to claim 3, characterized in that Also includes: The elastic part is sleeved on the rotating shaft, and the bearing part is located between the elastic part and the rotor core. The elastic part is used to apply an axial preload force to the bearing part.

7. The motor according to claim 6, characterized in that The maximum value R1 of the outer diameter of the elastic portion, the minimum value R2 of the inner diameter of the elastic portion, the inner diameter R3 of the bearing and the outer diameter R4 of the bearing satisfy: 0<(R4-R1) / (R1-R2)≤1, R2≥R3.

8. The motor according to claim 6, characterized in that The elastic part includes a wave washer or a clip spring.

9. The motor according to claim 3, characterized in that The rotating shaft and the bearing are interference fit.

10. The motor according to claim 1 or 2, characterized in that: At least a portion of the hole wall of the mounting hole is interference fit with the rotating shaft.

11. The motor according to claim 1 or 2, characterized in that: Any two adjacent core segments are staggered in a clockwise direction; or any two adjacent core segments are staggered in a counterclockwise direction.

12. The motor according to claim 1 or 2, characterized in that: The plurality of core segments are divided into a first core group and a second core group; The staggered angle between two adjacent core segments in the first core group and the second core group is greater than or equal to 0°; In the first core group, any two adjacent core segments are staggered in a clockwise direction, and the staggered angle between any two adjacent core segments is denoted as b1; In the second core group, any two adjacent core segments are staggered in a counterclockwise direction, and the staggered angle between any two adjacent core segments is denoted as b2; Among them, b1 and b2 are not equal.

13. A chassis system, characterized in that: include: An electric machine as claimed in any one of claims 1 to 12.

14. A vehicle, characterized in that: include: The electric machine according to any one of claims 1 to 12; or The chassis system of claim 13.

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