Electric motor, suspension system and vehicle

Abstract

An electric motor, a suspension system and a vehicle. The electric motor comprises a magnetic member and a winding structure, wherein the winding structure comprises an iron core and a coil arranged within the iron core; one of the magnetic member and the winding structure surrounds the other, and cooperation between the magnetic member and the winding structure enables the magnetic member and the winding structure to move relative to each other in a first direction. The maximum thrust F of the electric motor and the electromagnetic volume V of the electric motor satisfy: F=kV, where k is the thrust-to-volume ratio of the electric motor, measured in newtons per liter, and 1000≤k≤3500; V=πR2*L, where R is the outer diameter of one of the magnetic member and the winding structure, measured in decimeters, and L is the shorter of the lengths of the magnetic member and the winding structure in the first direction, measured in decimeters; the maximum thrust F of the electric motor is measured in newtons, and the electromagnetic volume V of the electric motor is measured in liters.

Description

Motors, suspension systems and vehicles

[0001] This application claims priority to Chinese patent application filed on November 12, 2024, with application number 202411618737.X and title "Stator core laminations, stator cores, stator assemblies, motors and vehicles".

[0002] Priority is claimed for Chinese patent application filed with the Chinese Patent Office on December 16, 2024, with application number 202411857460.6 and application title "Stator assembly of an electric motor, electric motor, suspension system and vehicle";

[0003] Priority to the Chinese patent application filed with the Chinese Patent Office on December 19, 2024, with application number 202423174386.6 and application title "Electric motor, suspension system and vehicle";

[0004] Priority is claimed for Chinese patent application filed on December 24, 2024, with application number 202411933681.7 and application title "An electric motor, suspension assembly and vehicle";

[0005] Priority to the Chinese patent application filed with the Chinese Patent Office on December 31, 2024, application number 202411999905.4, entitled "Electric motor, electromagnetic suspension and vehicle";

[0006] Its entire contents are incorporated herein by reference. Technical Field

[0007] This application relates to the field of vehicle technology, and more particularly to motors, suspension systems, and vehicles. Background Technology

[0008] Suspension systems, such as electromagnetic suspension, are devices connecting the vehicle body and wheels. Electromagnetic suspension primarily uses linear motors to generate thrust, thereby adjusting the distance between the vehicle body and wheels to ensure vehicle stability. Generally, a wide range of thrust output from the linear motor is desirable to cope with complex road conditions. However, the thrust range of linear motors in current technology is relatively small, making it difficult for electromagnetic suspension to handle complex road conditions. Summary of the Invention

[0009] The purpose of this application is to provide an electric motor, a suspension system, and a vehicle, with the aim of solving the problem of how to increase the thrust of the electric motor in the suspension system.

[0010] To achieve the above objectives, this application adopts the following technical solution:

[0011] In a first aspect, this application provides an electric motor, comprising a magnetic component and a winding structure. The winding structure includes an iron core and a coil disposed within the iron core. One of the magnetic component and the winding structure surrounds the other, and the magnetic component and the winding structure cooperate to allow relative movement between them along a first direction. The maximum thrust F of the motor and the electromagnetic volume V of the motor satisfy: F = kV, where k is the thrust-to-volume ratio of the motor, in Newtons per liter, 1000 ≤ k ≤ 3500, and V = πR. 2 *L and R are the outer diameters of either the magnetic component or the winding structure, in decimeters. L is the shorter of the lengths of the magnetic component in the first direction and the winding structure in the first direction, in decimeters. The maximum thrust F of the motor is in Newtons, and the electromagnetic volume V of the motor is in liters.

[0012] The motor provided in this application embodiment satisfies the following condition: the thrust-volume ratio k of the motor 10 satisfies 1000≤k≤3500. This allows the motor 10 to have a larger thrust range while keeping its electromagnetic volume constant. In other words, the maximum thrust of the motor 10 can be larger, thus meeting the requirement of high thrust of the motor 10. This enables the motor 10 to better adjust the stability of the vehicle body, making the vehicle suitable for more working conditions, even some harsh working conditions such as off-road conditions, thereby improving the performance of the vehicle.

[0013] In some embodiments, the thrust-to-volume ratio of the motor satisfies: 1000≤k≤3000, or 1500≤k≤3000, or 2000≤k≤3500, or 2000≤k≤3000, or 2500≤k≤3500.

[0014] In some embodiments, the relationship between the maximum thrust F of the motor and the modulation ratio X of the motor satisfies: F = 2450.7lnX + 1000V + 231.2, where X = Pm / Pa, Pm is the number of pole pairs of the magnetic component, and Pa is the number of pole pairs of the winding structure.

[0015] In some embodiments, the core includes a plurality of core blocks stacked along a first direction, with a winding space formed between two adjacent core blocks, and a coil disposed in the winding space.

[0016] In some embodiments, the core includes a plurality of core blocks stacked along a first direction. Each core block includes a core block body and a first magnetic adjustment block disposed on the core block body. The material of the first magnetic adjustment block is at least partially different from that of the core block body, and the resistivity of the first magnetic adjustment block is higher than that of the core block body.

[0017] In some embodiments, the core includes a plurality of core blocks stacked along a first direction. Each core block includes a core block body and a first magnetic adjustment block disposed on the core block body. The material of the first magnetic adjustment block is at least partially different from that of the core block body, and the tensile strength of the material of the core block body is greater than that of the material of the first magnetic adjustment block.

[0018] In some embodiments, the core block body is provided with an embedding groove, and the first magnetic adjustment block is embedded in the embedding groove.

[0019] In some embodiments, the embedding groove is an arc-shaped groove, which is arranged around the axis of the iron core block body, and the first magnetic adjustment block is an arc-shaped block.

[0020] In some embodiments, the magnetic element surrounds the winding structure, and the motor further includes a central shaft to which the winding structure is connected; the core block has a first central hole, and the first central holes of a plurality of core blocks are interconnected to form a core hole; the core also includes a second adjusting magnetic block, which is mounted on the wall of the core hole and has a second central hole through which the central shaft passes; the material of the second adjusting magnetic block is at least partially different from that of the core block body, and the resistivity of the second adjusting magnetic block is higher than that of the core block body.

[0021] In some embodiments, the tensile strength of the material of the core block body is greater than the tensile strength of the material of the second magnetic adjustment block.

[0022] In some embodiments, the number of core blocks is N, the axial length of a single core block is P, the axial length of the second adjusting block is Q, P×(N-1)<Q≤P×N, N≥2 and N is an integer.

[0023] In some embodiments, the magnetic components surround the winding structure, and the motor further includes a central shaft to which the winding structure is connected; the central shaft includes a first central shaft body and a second central shaft body, which are arranged and fixedly connected along the axial direction of the central shaft, and a shoulder is formed on the radially outer side of the first central shaft body; a plurality of iron core blocks are assembled on the second central shaft body, and among the plurality of iron core blocks there is a first end iron core block 32b adjacent to the first central shaft body, and the first end iron core block 32b is formed with a support portion, which abuts against the shoulder to limit the relative position of the first end iron core block 32b and the first central shaft body.

[0024] In some embodiments, a clearance space is formed at the end of the first end core block 32b facing the first central shaft, and the clearance space is opposite to the first central shaft in the axial direction of the central shaft so that the first end core block 32b and the first central shaft are spaced apart.

[0025] In some embodiments, along the axial direction of the central axis, the end of the first end core block 32b facing the first central axis body has a recessed clearance space in the direction away from the first central axis body, so as to form a support portion on the radially outer side of the clearance space.

[0026] In some embodiments, the cross-sectional dimension of the clearance space is larger than the cross-sectional dimension of the first central axis, and the orthographic projection of the first central axis is located within the clearance space along the axial direction of the central axis.

[0027] In some embodiments, the cross-section of the clearance space is circular, the cross-section of the first central axis is circular, the maximum diameter of the first central axis is D1, and the diameter of the clearance space is D2, satisfying the relationship: 1.02≤D2 / D1≤1.05.

[0028] In some embodiments, along the axial direction of the central axis, the thickness of the first end core block 32b is H1, and the depth of the clearance space is H2, satisfying the relationship: 0.25≤H2 / H1≤0.55.

[0029] In some embodiments, the motor includes a first component and a second component. The first component includes one of a magnetic element and a winding structure, and the second component includes the other of the first component including a magnetic element and a winding structure. The first component and the second component are movable relative to each other in a first direction. A bearing is provided between the first component and the second component. The first component has a liquid storage space and an oil passage. The oil passage connects the liquid storage space and the bearing so that oil flows to the bearing through the oil passage.

[0030] In some embodiments, the first component is sleeved on the outer periphery of the second component, and an air gap is provided between the first component and the second component. The air gap is connected to the liquid storage space, and the liquid storage space and the air gap are distributed along a first direction. When the second component moves toward the liquid storage space along the first direction, the air pressure in the liquid storage space increases to drive the oil to flow through the oil passage to the bearing.

[0031] In some embodiments, the first component further includes a housing, a magnetic element, and a winding structure disposed within the housing, and the second component at least partially divides the internal space of the housing into an upper chamber and a lower chamber, the lower chamber being configured as a liquid storage space; the bearing includes a first bearing disposed between the housing and the second component; the oil passage includes a first oil passage disposed inside the housing and communicating with the liquid storage space and the first bearing.

[0032] In some embodiments, the second component includes a central shaft, a portion of which is housed within a housing, a first bearing sleeved on the central shaft, and a guide hole formed in the central shaft; the first component also includes a guide member, at least partially passing through the guide hole, and the guide member is movable relative to the central shaft in a first direction; the bearing also includes a second bearing, which is disposed between the guide member and the central shaft and located within the guide hole; the oil passage includes a second oil passage disposed inside the guide member and communicating with the reservoir space and the second bearing.

[0033] In some embodiments, the motor includes a first component and a second component, the first component including one of a magnetic element and a winding structure, the second component including the other of a magnetic element and a winding structure, the first component and the second component being movable relative to each other along a first direction; the motor also includes a sensing component disposed on the first component and / or the second component, and adapted to generate a displacement signal characterizing the relative position of the first component and the second component.

[0034] In some embodiments, the motor further includes a shielding assembly mounted on the first assembly and / or the second assembly, and adapted to reduce the influence of the magnetic field generated after the coil current flows on the displacement signal.

[0035] In some embodiments, the shielding assembly includes a first shielding member disposed on the first assembly, the first shielding member being used to change the direction of the magnetic induction lines generated by the coil.

[0036] In some embodiments, the first component includes a housing and a magnetic element disposed on the housing, the second component includes a winding structure, a mounting cavity is formed inside the housing, the winding structure is movably disposed in the mounting cavity along a first direction, and the first shielding element is mounted on the housing.

[0037] In some embodiments, the sensing assembly includes a sensing element and a signaling element, the sensing element being adapted to acquire a signal from the signaling element to generate a displacement signal, and the sensing element being adapted to move between a first position away from the coil and a second position close to the coil; the shielding assembly includes a second shielding element disposed on the first assembly, the second shielding element being used to change the direction of the magnetic induction lines generated by the coil, and when the sensing element is in the second position, the second shielding element covers the coil axially in the motor.

[0038] In some embodiments, the first component includes a housing and a magnetic element, the magnetic element being disposed on the inner side of the housing, and a second shielding element being disposed on the outer side of the housing, and the second shielding element being at least partially overlapping the magnetic element in the axial direction of the motor.

[0039] In some embodiments, the shielding assembly includes a third shielding member adapted to change the direction of the magnetic induction lines generated by the coil along a first direction.

[0040] In some embodiments, the second component includes a central shaft and a winding structure, the winding structure being connected to the central shaft, the central shaft being coaxially arranged with the coil, and the central shaft including a first central shaft body and a second central shaft body connected to each other; wherein, the coil is mounted and fixed on the second central shaft body, and a third shielding member is disposed on the first central shaft body.

[0041] In some embodiments, the motor includes a first component, which includes one of a magnetic element and a winding structure; the first component further includes a housing, an end cap, and a first sealing structure, wherein the housing has a mounting cavity and a communicating hole, the mounting cavity having a first opening; the communicating hole communicates with the mounting cavity and is adapted to communicate with the inner cavity of an air spring; the end cap covers the first opening and is connected to the housing, forming a first gap between the end cap and the housing; the first sealing structure is used to block fluid communication between the mounting cavity and the external space through the first gap.

[0042] In some embodiments, a second component is further included, which includes another of a magnetic element and a winding structure. The first component and the second component are movable relative to each other along a first direction. The second component is disposed in the mounting cavity and is movable relative to the housing along the first direction within the mounting cavity. The housing is a cylindrical structure. In the first direction, one of the housing and the end cover includes a first end face, and the other includes a second end face. A first gap is provided between the first end face and the second end face, and the first gap communicates the mounting cavity and the external space.

[0043] In some embodiments, the motor further includes a sensing component, which includes a sensing element and a signal element. The sensing element is adapted to acquire the signal of the signal element to generate a displacement signal. The housing is provided with a wire outlet hole that penetrates the housing. The signal element is connected to the second component, and the sensing element is connected to the side of the housing opposite to the end cover and covers the wire outlet hole. The connecting wire of the sensing element is led out to the outside of the housing through the wire outlet hole.

[0044] In some embodiments, a second gap is formed between the sensor and the housing, the second gap connecting the mounting cavity and the external space, and is adapted to connect the air spring and the external space; the motor also includes a second sealing structure for blocking fluid communication between the mounting cavity and the external space, and between the air spring and the external space through the second gap.

[0045] In some embodiments, a second sealing structure is disposed between the sensor and the housing and surrounds the outlet hole; in a first direction, one of the sensor housings includes a third end face and the other includes a fourth end face, and a second gap is provided between the third end face and the fourth end face.

[0046] A second aspect of this application provides a suspension system including the aforementioned motor.

[0047] A third aspect of this application provides a vehicle that includes the aforementioned motor or suspension system.

[0048] It should be noted that the technical effects of the implementation methods of the second and third aspects can be found in the technical effects of the corresponding implementation methods in the first aspect, and will not be repeated here. Attached Figure Description

[0049] To more clearly illustrate the technical solutions of the embodiments of this application, the drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0050] Figure 1 is a structural schematic diagram of the vehicle provided in an embodiment of this application;

[0051] Figure 2 is a structural schematic diagram of the suspension system in the vehicle shown in Figure 1;

[0052] Figure 3 is an enlarged structural schematic diagram of the connection position between the motor housing and the end cover in the suspension system shown in Figure 2;

[0053] Figure 4 is a schematic diagram of the first sealing structure in the motor shown in Figure 3;

[0054] Figure 5 is a cross-sectional view of the first sealing structure shown in Figure 4.

[0055] Figure 6 is an enlarged schematic diagram of the connection position between the motor housing and the end cover in the suspension system shown in Figure 2.

[0056] Figure 7 is another enlarged structural schematic diagram of the connection position between the motor housing and the end cover in the suspension system shown in Figure 2.

[0057] Figure 8 is a schematic diagram of the connection relationship between the motor's sensing components and the housing in the suspension system shown in Figure 2.

[0058] Figure 9 is an enlarged structural schematic diagram of the connection position between the sensing component and the housing shown in Figure 8;

[0059] Figure 10 is a schematic diagram showing the relationship between the pressure plate and the second sealing structure at the connection position between the sensing component and the housing shown in Figure 8.

[0060] Figure 11 is a schematic diagram of the structure of the motor sensing component in the suspension system shown in Figure 2 when the sensing element and the housing are sealed by the third sealing ring.

[0061] Figure 12 is a top view of the connection relationship between the pressure plate of the sensing element and the housing in the suspension system shown in Figure 2.

[0062] Figure 13 is a perspective view of the iron core block according to an embodiment of this application;

[0063] Figure 14 is a top view of the iron core block according to an embodiment of this application;

[0064] Figure 15 is a cross-sectional view of AA in Figure 14;

[0065] Figure 16 is a perspective view of the iron core according to an embodiment of this application;

[0066] Figure 17 is a cross-sectional view of the iron core according to an embodiment of this application;

[0067] Figure 18 is a comparison of the magnetic properties of composite soft magnetic material SMC and pure iron material DT4;

[0068] Figure 19 shows a comparison of the no-load thrust fluctuation of the pure iron core under the theoretical scheme and the tolerance scheme.

[0069] Figure 20 is a histogram comparing the thrust fluctuation of the pure iron core under the theoretical scheme and the tolerance scheme;

[0070] Figure 21 is a comparison of the thrust of the hybrid stator and other stators under high-speed motion of 2 m / s;

[0071] Figure 22 shows the loss reduction rate of the hybrid stator compared to the pure iron stator under high-speed motion of 2 m / s;

[0072] Figure 23 is a comparison of thrust fluctuations for three types of iron cores under the cumulative negative stator tolerance.

[0073] Figure 24 shows the results of linear analysis using the response surface methodology for B1 / B2 and A1 / A2.

[0074] Figure 25 shows the results of linear analysis using the C1 / C2 and A1 / A2 response surface methodology.

[0075] Figure 26 is a schematic diagram showing the actual fit between the formula and the data;

[0076] Figure 27 is a top view of a second component provided in an embodiment of this application;

[0077] Figure 28 is a cross-sectional view at point BB in Figure 27;

[0078] Figure 29 is an enlarged view of point D1 in Figure 28;

[0079] Figure 30 is a top view of another structural diagram of the second component provided in an embodiment of this application;

[0080] Figure 31 is a cross-sectional view at CC in Figure 30;

[0081] Figure 32 is an enlarged view of point D2 in Figure 31;

[0082] Figure 33 is a schematic diagram of the first end core block 32b according to an embodiment of this application;

[0083] Figure 34 is a cross-sectional view of the first end core block 32b according to an embodiment of this application;

[0084] Figure 35 is a top view of the first end core block 32b according to an embodiment of this application;

[0085] Figure 36 shows the variation of the suppression rate and stress of the central axis with X2 / X1 in an embodiment of this application;

[0086] Figure 37 is a graph showing the variation of the maximum thrust of the motor with D2, D1, H2, and H1 (unit: N) according to an embodiment of this application.

[0087] Figure 38 is a graph showing the variation of motor thrust fluctuation with D2, D1, H2, and H1 in an embodiment of this application (unit: N);

[0088] Figure 39 is a graph showing the variation of the central axis deviation suppression rate with D2, D1, H2, and H1 in an embodiment of this application;

[0089] Figure 40 is a graph showing the variation of the maximum stress of the first end core block 32b with D2, D1, H2, and H1 (unit: MPa) according to an embodiment of this application.

[0090] Figure 41 shows the variation of the maximum stress of the shoulder of the embodiment of this application with D2, D1, H2, and H1 (unit: MPa);

[0091] Figure 42 is a schematic diagram of a motor provided in an embodiment of this application;

[0092] Figure 43 is a schematic diagram of the casing in Figure 42;

[0093] Figure 44 is a schematic diagram of the structure of the central axis in Figure 42;

[0094] Figure 45 is a schematic diagram of the sensor component in Figure 42;

[0095] Figure 46 is a schematic diagram of the coil structure in Figure 42;

[0096] Figure 47 is a partial structural diagram of the cooperation between the sensor and the housing in Figure 42;

[0097] Figure 48 is a schematic diagram of the structure in which the signal component and the first central shaft in Figure 42 cooperate;

[0098] Figure 49 shows the radial magnetic flux density diagrams of motors with and without shielding components.

[0099] Figure 50 shows the axial magnetic flux density diagrams of motors with and without shielding components.

[0100] Figure 51 shows the displacement signal fluctuation of a motor without shielding components;

[0101] Figure 52 shows the displacement signal fluctuation of a motor with shielding components;

[0102] Figure 53 is another structural diagram of the motor provided in the embodiment of this application;

[0103] Figure 54 is an enlarged structural diagram of D3 in Figure 53 provided in the embodiment of this application;

[0104] Figure 55 is an enlarged structural diagram of D4 in Figure 53 provided in the embodiment of this application.

[0105] Reference numerals: 1000, vehicle; 100, wheel; 200, body; 300, suspension system; 10, motor; 20, tower top assembly; 20A, mounting base; 20B, support component; 20C, air valve; 30, air spring; 30A, inner cavity; 30B, outer bladder; 30C, inner bladder; 40, fourth sealing structure; 50, third sealing structure; 1, first assembly; 11, housing; 11A, mounting cavity; 11B, mounting hole; 11C, connecting hole; 11D, cable outlet hole; 11E, third receiving groove; 12, magnetic component; 13, end cap; 131, first receiving groove; 132, main body; 133, limiting part; 14. First sealing structure; 141A. First sealing gasket; 141B. First rib; 141C. First recess; 142. First sealing ring; 143. Second sealing ring; 15. Guide component; 151. Base; 151A. Second receiving groove; 152. Guide rod; 16. First gap; 16A. First end face; 16B. Second end face; 2. Second assembly; 21. Central shaft; 21C. Wiring channel; 22A. Winding structure; 22. Coil; 23. Iron core; 3. Cavity; 4. Sensing assembly; 41. Sensing element; 411. Sensing element body; 412. Pressure plate; 42. Signal element; 5. Second sealing structure; 51. Third sealing ring.1a. Core block; 11a. Core block body; 111a. Body part; 112a. Protrusion; 12a. First adjusting magnetic block; 121a. First inner surface; 122a. First outer surface; 13a. Limiting ring; 14a. First center hole; 2a. Second adjusting magnetic block; 21a. Second center hole; 22a. Second inner surface; 23a. Second outer surface; 11b. First central shaft; 12b. Second central shaft; 20b. Shoulder; 21b. Sub-shoulder; 32b. First end core block; 321b. Clearance space; 33b. Support part; 36b. Second end core block; 40b. Sleeve; 50b. Locking element; 1121c, Recessed groove; 113c, Pressure plate; 211c, Coil section; 212c, Connecting wire; 2211c, Receiving groove; 2212c, Sealing component; 411c, Long-period magnet assembly; 4111c, First long magnet; 4112c, Second long magnet; 412c, Short-period magnet assembly; 4121c, First short magnet; 4122c, Second short magnet; 421c, First sensing element; 422c, Second sensing element; 50c, Shielding assembly; 51c, First shielding component; 52c, Second shielding component; 53c, Third shielding component; 11d, Liquid storage space; 12d, Air gap; 131d, Top wall; 132d, Side wall; 133d, Bottom wall; 134d, Clearance oil tank; 135d Upper chamber; 136d, lower chamber; 2011d, guide hole; 20d, oil passage; 21d, first oil passage; 211d, first oil inlet channel; 212d, first oil guide channel; 213d, first oil outlet channel; 22d, second oil passage; 221d, second oil inlet channel; 222d, second oil guide channel; 223d, second oil outlet channel; 30d, bearing; 31d, first bearing; 311d, oil guide groove; 32d, second bearing. Detailed Implementation

[0106] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0107] 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. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, unless otherwise stated, "a plurality of" means two or more.

[0108] 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.

[0109] This application provides a vehicle. The vehicle 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 can also be a sedan, a truck, a bus, a lorry, a trailer, etc. This application does not specifically limit the type of vehicle.

[0110] Please refer to Figure 1, which is a structural schematic diagram of a vehicle provided in an embodiment of this application. The vehicle 1000 may include wheels 100, a body 200, and a suspension system 300. The suspension system 300 is connected between the body 200 and the wheels 100, and is used to buffer the impact force transmitted to the body 200 from uneven road surfaces, so as to ensure the smoothness of the vehicle 1000's ride and improve the driving comfort of the vehicle 1000.

[0111] Please refer to Figure 2, which is a structural schematic diagram of the suspension system 300 in the vehicle 1000 shown in Figure 1. The suspension system 300 may include a motor 10. During the driving of the vehicle 1000, affected by road bumps, the motor 10 can adjust the distance between the body 200 and the wheels 100 to ensure the stability of the body 200.

[0112] In some embodiments, referring to FIG2, the motor 10 may specifically be a linear motor 10. Specifically, the motor 10 includes a first component 1 and a second component 2. The second component 2 and the first component 1 are movable relative to each other along a first direction (direction W shown in FIG2) to extend or shorten the motor 10. The first direction may be consistent with the height direction of the vehicle 1000 or may be inclined relative to the height direction of the vehicle 1000; this application does not specifically limit this.

[0113] In this embodiment, one of the first component 1 and the second component 2 is a stator assembly, and the other of the first component 1 and the second component 2 is a mover assembly. The stator assembly is connected to the vehicle body, and the mover assembly is connected to the wheel. This application uses the first component 1 as the mover assembly and the second component 2 as the stator assembly as an example for illustration, which should not be considered as a specific limitation on the composition of this application.

[0114] In some embodiments, referring to FIG2, the suspension system 300 further includes a tower mount assembly 20. The tower mount assembly 20 is fixedly connected to the second component 2 of the motor 10, and the tower mount assembly 20 is connected to the vehicle body 200 or the wheel 100.

[0115] In other words, the second component 2 can be connected to the vehicle body 200 via the tower top component 20, in which case the first component 1 is connected to the wheel 100. Alternatively, the second component 2 can be connected to the wheel 100 via the tower top component 20, in which case the first component 1 is connected to the vehicle body 200.

[0116] This application is a further description based on the premise that the second component 2 is adapted to connect to the vehicle body 200 and the first component 1 is adapted to connect to the wheel 100, and this should not be considered as a specific limitation on the application.

[0117] In some embodiments, referring to FIG2, the suspension system 300 further includes an air spring 30. One end of the air spring 30 is connected to the tower mount assembly 20, and the opposite end of the air spring 30 is connected to the first assembly 1 of the motor 10. The air spring 30 is used to buffer the transmission of force between the wheel 100 and the vehicle body 200.

[0118] In some embodiments, an air spring surrounds the first component 1, and both the tower top component 20 and the first component 1 are sealed to the air spring.

[0119] In this way, when the second component 2 supports the body 200 at a suitable height, the distance between the tower top component 20 and the first component 1 will change as the first component 1 and the second component 2 move relative to each other. This causes the air spring to extend and retract as the second component 2 and the first component 1 move relative to each other, so as to keep the body 200 stable and achieve a good vibration reduction effect.

[0120] It should be noted that the air spring is a structure with an inner cavity 30A formed by an air bladder. The inner cavity 30A of the air spring is filled with gas. During the expansion and contraction of the air spring as the second component 2 and the first component 1 move relative to each other, the volume of the inner cavity 30A of the air spring will change, which will cause the pressure of the gas in the inner cavity 30A to change, thereby adjusting the damping performance of the air spring to better absorb the impact generated by the road surface and improve the driving comfort of the vehicle.

[0121] In some embodiments, referring to FIG2, the tower top assembly 20 may include a mounting base 20A and a support member 20B. The mounting base 20A is fixedly connected to the second assembly 2, and the mounting base 20A is adapted to connect to the vehicle body 200 or the wheel 100. This application describes the example of the mounting base 20A being connected to the vehicle body 200.

[0122] For example, the mounting bracket 20A and the second component 2 can be connected by means of screwing, snap-fitting, welding, etc., and this application does not make specific limitations in this regard. The mounting bracket 20A and the vehicle body 200 can also be connected by means of screwing, snap-fitting, welding, etc., and this application does not make specific limitations in this regard.

[0123] The support member 20B is connected between the fixed base 20A and the air spring. The fixed base 20A supports the support member 20B, thereby supporting the air spring and ensuring its stability.

[0124] In some embodiments, the support member 20B surrounds the second component 2. For example, the support member 20B may have a cylindrical structure.

[0125] Furthermore, the support member 20B, the second component 2, the first component 1, and the fixed seat 20A form a cavity 3; the cavity 3 is connected to the inner cavity 30A of the air spring.

[0126] In this way, the gas filling the inner cavity 30A of the air spring can also enter the cavity 3, so that the inner cavity 30A and the cavity 3 of the air spring together serve as the filling chamber for the gas. This increases the volume of the filling chamber and allows for a wider range of gas pressure changes during the extension and contraction of the air spring. This allows for better adjustment of the damping performance of the air spring, thereby further improving the driving comfort of the vehicle 1000.

[0127] In some examples, the inner cavity 30A of the air spring has a second opening at the end facing the tower top assembly 20. For example, the air spring includes an outer bladder 30B and an inner bladder 30C. The inner bladder 30C surrounds and is fixedly connected to the first assembly 1, and the outer bladder 30B surrounds and is spaced apart from the inner bladder 30C. The end of the outer bladder 30B facing away from the tower top assembly 20 is connected to the end of the inner bladder 30C facing away from the tower top assembly 20, thereby forming an inner cavity 30A with a second opening at the end facing the tower top assembly 20 between the outer bladder 30B and the inner bladder 30C.

[0128] The outer skin 30B is fixedly connected to the support member 20B at one end facing the tower top assembly 20. There are gaps between the support member 20B and the second assembly 2, and between the support member 20B and the first assembly 1, so that the inner cavity 30A can communicate with the cavity 3.

[0129] In some examples, both the outer capsule 30B and the inner capsule 30C can be made of rubber.

[0130] In some embodiments, the outer sheath 30B surrounds the support member 20B and contacts the outer peripheral surface of the support member 20B, and then the outer sheath 30B is pressed and fixed onto the support member 20B by a first clamp. Because the outer sheath 30B is flexible, a sealed connection can be made between the outer sheath 30B and the support member 20B.

[0131] The inner lining 30C surrounds the first component 1 and contacts the outer peripheral surface of the first component 1. The inner lining 30C is then pressed and fixed onto the first component 1 by a second clamp. Because the inner lining 30C is flexible, a sealed connection can be achieved between the inner lining 30C and the first component 1.

[0132] In some embodiments, to prevent gas in the inner cavity 30A and cavity 3 from leaking through the gap between the support member 20B and the fixed seat 20A, referring to FIG2, the suspension system 300 includes a fourth sealing structure 40. The fourth sealing structure 40 is disposed between the support member 20B and the fixed seat 20A. The fourth sealing structure 40 is used to seal the gap between the support member 20B and the fixed seat 20A to prevent gas in the inner cavity 30A and cavity 3 from leaking through the gap between the support member 20B and the fixed seat 20A, thereby ensuring the damping performance of the air spring.

[0133] In some examples, the fourth sealing structure 40 can be a sealing ring. In other examples, the fourth sealing structure 40 can also be other components capable of sealing the gap between the support 20B and the fixing seat 20A, such as sealant, lip seal, etc.

[0134] In some embodiments, referring to FIG2, the suspension system 300 further includes a third sealing structure 50. The third sealing structure 50 is disposed between the tower top assembly 20 and the second assembly 2. Specifically, the third sealing structure 50 is disposed between the mounting base 20A and the second assembly 2.

[0135] The third sealing structure 50 is used to seal the gap between the fixed seat 20A and the second component 2 to prevent gas in the inner cavity 30A and the cavity 3 from leaking from the gap between the fixed seat 20A and the second component 2, thereby ensuring the damping performance of the air spring.

[0136] In some examples, the third sealing structure 50 can be a sealing ring. In other examples, the third sealing structure 50 can also be other components capable of sealing the gap between the retainer 20A and the second component 2, such as sealant, lip seal, etc.

[0137] In some embodiments, please continue referring to Figure 2, the support member 20B is also provided with an inflation channel, which communicates with the cavity 3 and is used to inflate gas into the inner cavity 30A of the airbag. An air pressure valve 20C is provided within the inflation channel, which is used to open or close the inflation channel.

[0138] After the air spring has been used for a period of time, the air pressure inside will decrease. You can open the air pressure valve 20C to replenish air into the inner cavity 30A through the inflation channel to maintain the air pressure within the inner cavity 30A and ensure the damping performance of the air spring. After inflation is complete, close the air pressure valve 20C to prevent gas leakage from the inner cavity 30A.

[0139] By placing the inflation channel and pressure valve 20C on the support member 20B, compared to placing the inflation channel and pressure valve 20C on the bladder of the air spring, the inflation channel and pressure valve 20C can be prevented from being continuously squeezed and shaken as the air spring extends and retracts, thereby reducing the damage to the inflation channel and pressure valve 20C.

[0140] The structure of motor 10 will be further described below.

[0141] In some embodiments of this application, please continue to refer to FIG2. The motor 10 includes a first component 1 and a second component 2. The first component 1 and the second component 2 are capable of moving relative to each other along a first direction. Specifically, the first component 1 and the second component 2 are capable of reciprocating motion along the first direction.

[0142] The motor 10 includes a magnetic element 12 and a winding structure 22A. One of the magnetic element 12 and the winding structure 22A surrounds the other, and the magnetic element 12 and the winding structure 22A cooperate to allow relative movement between them along a first direction. One of the magnetic element 12 and the winding structure 22A forms a first assembly, and the other forms a second assembly. The magnetic element 12 may be formed by stacking multiple magnets along the first direction. The winding structure may include an iron core and a coil disposed within the iron core.

[0143] For example, the motor may also include a housing 11 and a central shaft 21, a portion of which is located within the housing 11 and is movable relative to the housing 11 in a first direction. One of the central shaft 21 and the housing 11 is used to connect to the vehicle body, and the other is used to connect to the wheel. Here, the connection of the central shaft 21 to the vehicle body and the connection of the housing 11 to the wheel are illustrated by way of example.

[0144] The magnetic component 12 can be connected to the housing 11, and the winding structure 22A can be connected to the central shaft 21. The magnetic component 12 is arranged around the winding structure 22A. In this case, the magnetic component 12 and the housing 11 form a first assembly 1, and the winding structure 22A and the central shaft 21 form a second assembly 2. The first assembly 1 can be a mover assembly, and the second assembly 2 can be a stator assembly. If the length of the magnetic component along the first direction is greater than the length of the winding structure, the motor is a motor with a long mover and a short stator and external magnets. If the length of the magnetic component along the first direction is less than the length of the winding structure, the motor is a motor with a short mover and an external magnet and a long stator.

[0145] The winding structure 22A can be connected to the housing 11, and the magnetic element 12 can be connected to the central shaft 21. The winding structure 22A is arranged around the magnetic element 12. At this time, the winding structure 22A and the housing 11 form the first component 1, and the magnetic element 12 and the central shaft 21 form the second component 2. The first component 1 can be a mover component, and the second component 2 can be a stator component. If the length of the winding structure along the first direction is greater than the length of the magnetic element, the motor is a motor with an inner magnet, a long mover, and a short stator. If the length of the winding structure along the first direction is less than the length of the magnetic element, the motor is a motor with an inner magnet, a short mover, and a long stator.

[0146] The relationship between the maximum thrust F of motor 10 and the electromagnetic volume V of motor 10 satisfies: F = kV, where k is the thrust-volume ratio of the motor, in Newtons per liter, 1000 ≤ k ≤ 3500, and V = πR. 2 *L and R are the outer diameters of either the magnetic component or the winding structure, in decimeters. L is the shorter of the lengths of the magnetic component and the winding structure in the first direction, in decimeters. F is the maximum thrust of the motor 10, in Newtons. V is the electromagnetic volume of the motor 10, in liters.

[0147] For example, when the motor is an external magnet motor with a long mover and a short stator, R is the outer diameter of the magnet, and L is the length of the winding structure. When the motor is an external magnet motor with a short mover and a long stator, R is the outer diameter of the magnet, and L is the length of the magnetic element 12 in the first direction. When the motor is an internal magnet motor with a long mover and a short stator, R is the outer diameter of the winding structure, i.e., the outer diameter of the iron core, and L is the length of the magnetic element 12 in the first direction. When the motor is an internal magnet motor with a short mover and a long stator, R is the outer diameter of the winding structure, i.e., the outer diameter of the iron core, and L is the length of the winding structure (i.e., the iron core) in the first direction.

[0148] By ensuring that the thrust-volume ratio k of the motor satisfies the condition 1000≤k≤3500, the thrust range of the motor 10 can be larger while keeping the electromagnetic volume of the motor 10 constant. This means that the maximum thrust of the motor 10 can be larger, thus meeting the requirement of high thrust of the motor 10. As a result, the motor 10 can better adjust the stability of the vehicle body, making the vehicle suitable for more working conditions, even some harsh working conditions such as off-road conditions, jumping over steps, jumping over potholes, side tilting, undulating roads, etc., thereby improving the performance of the vehicle.

[0149] The thrust-volume ratio k of the motor can be adjusted by the design of the motor 10, for example, by using Haier's shell magnetization method to magnetize the magnets, adding soft magnetic materials to the iron core, and setting the air gap between the mover assembly and the stator assembly within a suitable range.

[0150] By designing the structure of motor 10, the thrust-volume ratio k of motor 10 can be made to satisfy the following condition: when 1000≤k≤3500, the maximum thrust of motor 10 is 2800N≤F≤8100N.

[0151] In some embodiments, the thrust-volume ratio k of the motor 10 satisfies: 1000≤k≤3000. For example, the thrust-volume ratio k of the motor 10 can be 1000, 1200, 1500, 1800, 2000, 2200, 2500, 2800, 3000, etc.

[0152] In some embodiments, 1500≤k≤3000. For example, the thrust-volume ratio k of the motor 10 can be 1500, 1600, 1900, 2000, 2100, 2400, 2700, 2900, 3000, etc.

[0153] In some embodiments, 2000≤k≤3500. For example, the thrust-volume ratio k of the motor 10 can be 2000, 2300, 2500, 2700, 2900, 3000, 3300, 3500, etc.

[0154] In some embodiments, 2000≤k≤3000. For example, the thrust-volume ratio k of the motor 10 can be 2000, 2300, 2500, 2700, 2800, 3000, etc.

[0155] In some embodiments, 2500≤k≤3500. For example, the thrust-volume ratio k of the motor 10 can be 2500, 2600, 2800, 3000, 3100, 3300, 3500, etc.

[0156] By ensuring that the thrust-volume ratio k of motor 10 satisfies the following conditions: 1000≤k≤3000, or 1500≤k≤3000, or 2000≤k≤3500, or 2000≤k≤3000, or 2500≤k≤3500, the thrust of motor 10 can be guaranteed to be large, making the vehicle suitable for more working conditions.

[0157] In some embodiments, the maximum thrust F of the motor 10 is positively correlated with the modulation ratio X of the motor 10, where X = Pm / Pa, Pm is the number of pole pairs of the magnetic element 12, and Pa is the number of pole pairs of the winding structure 22A. In this way, the maximum thrust of the motor 10 can be adjusted by regulating the modulation ratio of the motor 10, i.e., adjusting the ratio of the number of pole pairs of the magnetic element 12 to the number of pole pairs of the winding structure 22A, so that the vehicle can be adapted to more operating conditions and its performance can be improved.

[0158] It should be noted that the number of pole pairs of magnetic component 12 is the number of pairs of magnetic poles in the magnetic field generated by magnetic component 12. For example, if one N and S pole of magnetic component 12 is a pair of magnetic poles, and the number of N and S poles of magnetic component 12 is 10, then the number of pole pairs of magnetic component 12 is 10. The number of pole pairs of the winding structure can be referenced to the number of pole pairs of magnetic component 12, and is not specifically limited here.

[0159] In some examples, the number of pole pairs of the magnetic component can be 10, and the number of pole pairs of the winding structure can be 2. In this case, the modulation ratio of the motor 10 is 5.

[0160] In some embodiments, the relationship between the maximum thrust F of the motor 10 and the modulation ratio X of the motor 10 satisfies: F = 2450.7lnX + 1000V + 231.2. Where X = Pm / Pa, Pm is the number of pole pairs of the magnetic element 12, and Pa is the number of pole pairs of the winding structure 22A. In this way, the magnitude of the maximum thrust F can increase with the increase of the modulation ratio X. Therefore, the maximum thrust of the motor 10 can be adjusted by regulating the modulation ratio of the motor 10, i.e., by adjusting the ratio of the number of pole pairs of the magnetic element 12 to the number of pole pairs of the winding structure 22A, so that the vehicle can be adapted to more operating conditions and its performance can be improved. Furthermore, the modulation ratio of the motor 10 can be set within a suitable range according to the maximum thrust requirement of the motor 10 to avoid the motor 10 becoming too large and to facilitate its placement within the vehicle. For example, the range of X can be: 3 ≤ X ≤ 5, such as X being 3, 4, 5, etc. Setting the value of X within this range allows the maximum thrust of the motor to be within a larger range while ensuring that the volume of the linear motor 10 is not too large.

[0161] The following description of this application exemplifies the use of a first component 1 comprising a housing 11 and a magnetic element 12, and a second component 2 comprising a central shaft 21 and a winding structure 22A. For example, the housing 11 has a mounting cavity 11A. The housing 11 has a mounting hole 11B at one end along a first direction (direction W shown in FIG. 2). The mounting hole 11B extends along the first direction and communicates with the mounting cavity 11A of the housing 11.

[0162] A portion of the central shaft 21 is housed within the mounting cavity 11A of the housing 11. Specifically, the central shaft 21 passes through the mounting hole 11B, and the central shaft 21 is slidably connected to the housing 11 along the axial direction of the central shaft 21. That is, a portion of the central shaft 21 is located within the mounting cavity 11A of the housing 11, while the other portion of the central shaft 21 is located outside the housing 11.

[0163] The first direction is the direction of movement of the first component 1 relative to the second component 2. The axial direction of the central shaft 21 is consistent with the first direction.

[0164] The winding structure 22A is fixed to the central shaft 21 and housed within the mounting cavity 11A of the housing 11. The winding structure 22A drives the first component 1 to move relative to the winding structure 22A, thereby causing the first component 1 and the second component 2 to move relative to each other. Specifically, the winding structure 22A is connected to the portion of the central shaft 21 located within the mounting cavity 11A.

[0165] For example, the housing 11 is a cylindrical structure. When the housing 11 is a cylindrical structure, the central shaft 21 can be a cylindrical structure or a rod structure, and the winding structure 22A can be a disc structure. The cylindrical structure can be cylindrical, polygonal, etc.

[0166] In some examples, the winding structure 22A includes an iron core 23 and a coil 22. The number of iron cores 23 can be at least one. At least one iron core 23 is fixed to a central shaft 21, and the coil 22 is disposed on at least one iron core 23. Exemplarily, the iron core 23 is connected to a portion of the central shaft 21 located within the mounting cavity 11A. A winding space is formed on the iron core 23; the coil 22 is housed within the winding space.

[0167] Specifically, the iron core 23 is annular, with the central shaft 21 passing through and fixedly connected to the iron core 23. Coil slots are provided on the outer peripheral wall of the iron core 23, forming a winding space. The coil 22 is located within the coil slots and is wound around the iron core 23 circumferentially.

[0168] The magnetic component 12 is disposed inside the housing 11 and fixed to the housing 11. The coil 22 cooperates with the magnetic component 12 to drive the first component 1 and the second component 2 to move relative to each other.

[0169] For example, the magnetic element 12 is disposed on the inner peripheral surface of the housing 11. The magnetic element 12 is located between the housing 11 and the coil 22.

[0170] In this way, after the coil 22 is energized, the coil 22 will generate a magnetic field, and the magnetic component 12 will also generate a magnetic field. The magnetic field generated by the coil 22 and the magnetic field generated by the magnetic component 12 can interact with each other and generate an axial force along the central axis 21. This will generate an axial interaction force between the central axis 21 and the housing 11, thereby pushing the central axis 21 and the housing 11 to move relative to each other along the central axis 21, so as to realize the relative movement of the first component 1 and the second component 2.

[0171] For example, the magnetic component 12 can be a permanent magnet, an electromagnet, an energized coil, etc.

[0172] For example, when the housing 11 has a cylindrical structure, the magnetic component 12 has a ring-shaped structure. In this case, the central shaft 21, the iron core 23, and the coil 22 are all inserted inside the magnetic component 12.

[0173] In some examples, coil 22 includes multiple coils spaced apart axially along central axis 21. There are also multiple winding spaces, with at least one coil disposed within a winding space. There are also multiple magnetic elements 12 spaced apart axially along central axis 21.

[0174] In some embodiments, please refer to Figures 13-26. The iron core 23 may include a plurality of iron core blocks stacked along a first direction, with a winding space formed between two adjacent iron core blocks, and the coil is disposed in the winding space.

[0175] In some embodiments, referring to Figures 13-15, the core block 1a includes a core block body 11a and a first magnetic adjustment block 12a. The first magnetic adjustment block 12a is disposed on the core block body 11a. The material of the first magnetic adjustment block 12a is at least partially different from that of the core block body 11a, and the resistivity of the first magnetic adjustment block 12a is higher than that of the core block body 11a. Therefore, by disposing of the first magnetic adjustment block 12a with higher resistivity on the core block body 11a, the resistance of the magnetic circuit can be locally adjusted, optimizing the magnetic field. After the core blocks 1a are stacked to form the core 23, the magnetic field can be more uniformly distributed in the core 23, effectively reducing the heat generated by eddy currents, lowering magnetic flux leakage and eddy current losses, and improving the performance of the core block 1a.

[0176] In related technologies, iron core blocks are usually made from a single material such as pure iron. However, iron core blocks made from a single material have excessive eddy current losses, resulting in excessive eddy current losses for the entire iron core.

[0177] According to the embodiment of this application, by setting a first magnetic adjustment block 12a with a high resistivity on the iron core block 11a, the resistance of the magnetic circuit can be locally adjusted, which helps to optimize the magnetic field distribution and make the magnetic field more uniformly distributed in the iron core block 1a. By increasing the resistivity of the iron core block 1a, magnetic flux leakage and eddy current loss can be effectively reduced, thereby improving the performance of the iron core block 1a.

[0178] In some embodiments of this application, referring to Figures 13-15, the tensile strength of the material of the core block body 11a is greater than the tensile strength of the material of the first magnetic adjustment block 12a. In other words, the mechanical properties of the material of the core block body 11a are superior to those of the material of the first magnetic adjustment block 12a. Therefore, the first magnetic adjustment block 12a is embedded in the core block body 11a and does not serve as a load-bearing component. The core block body 11a, as the main load-bearing part of the core block 1a, has higher tensile strength, which enhances the overall structural strength of the core block 1a, helping to resist various mechanical stresses and vibrations, thereby improving the stability and reliability of the core block 1a. By selecting a material with higher tensile strength as the core block body 11a, the amount and thickness of material used can be reduced while ensuring the structural strength of the core block body 11a, thus reducing the overall weight of the core block 1a and lowering its manufacturing cost.

[0179] It should be noted that the tensile strength mentioned above includes the ultimate tensile strength and the tensile yield strength. In addition to the ultimate tensile strength and the tensile yield strength, mechanical properties may also include Young's modulus, Poisson's ratio, etc. For example, the Young's modulus of the material of the core block body 11a is also greater than the Young's modulus of the material of the first magnetic adjustment block 12a.

[0180] In some embodiments, the core block body 11a may be made of pure iron material, such as DT4, DT4A, DT8, YT2, or other pure iron materials. The first adjusting magnetic block 12a may be made of composite soft magnetic material, such as SMC, metal magnetic powder core composite material, soft magnetic ferrite composite material, or other composite soft magnetic materials. Specifically, using both pure iron material and composite soft magnetic material to make the core block 1a results in higher strength and retains more volume of composite soft magnetic material, which can effectively reduce iron loss. When the core blocks 1a are stacked to form the core 23 and applied to the motor 10, compared to a core block made entirely of pure iron material, using the core block 1a of this application can significantly improve the thrust of the motor 10 under high-speed conditions and improve the working efficiency of the motor 10. Compared to a core block made entirely of composite soft magnetic material, using the core block 1a of this application can reduce production costs, and the first adjusting magnetic block 12a has a simple shape, is easier to process and improves precision, and the assembly of the first adjusting magnetic block 12a and the core block body 11a is simple and convenient.

[0181] It should be noted that "the materials of the first adjusting magnetic block 12a and the iron core block body 11a are at least partially different" can mean that the material of the first adjusting magnetic block 12a is a mixture, the material of the iron core block body 11a is a mixture, and at least a portion of the components in the mixture of the first adjusting magnetic block 12a and the iron core block body 11a are different. It can also mean that the material of the first adjusting magnetic block 12a is a pure first material, and the material of the iron core block body 11a is a pure second material, and the first material and the second material are different. Of course, it can also mean that the material of the first adjusting magnetic block 12a is a mixture, the material of the iron core block body 11a is a pure second material, or it can mean that the material of the first adjusting magnetic block 12a is a pure first material, and the material of the iron core block body 11a is a mixture.

[0182] To more intuitively demonstrate the beneficial effects of the core block 1a of this application, the following description will take the example of the core block body 11a being made of pure iron material DT4 and the first magnetic adjustment block 12a being made of composite soft magnetic material SMC. The pure iron material DT4 has a tensile strength exceeding 360 MPa, a tensile yield strength exceeding 200 MPa, and a Young's modulus exceeding 160 GPa. The composite soft magnetic material SMC has a tensile strength of 12 MPa, a tensile yield strength of 6.1 MPa, and a Young's modulus of 17.62 GPa. Therefore, the mechanical properties of the pure iron material DT4 are superior to those of the composite soft magnetic material SMC, resulting in the mechanical properties of the core block body 11a being superior to those of the first magnetic adjustment block 12a.

[0183] In related technologies, pure iron material DT4 has good mechanical properties. After being made into iron core blocks, the overall accuracy of the iron core blocks can be ensured through precision machining. However, due to the low resistivity of pure iron material, the iron core blocks will generate large eddy current losses (leading to heat generation) when the motor moves at high speed, generating eddy current resistance, thereby reducing the thrust output of the motor and reducing the working efficiency of the motor in the high-speed range, which cannot meet the working requirements of the motor for high thrust.

[0184] Referring to Figure 18, which compares the magnetic properties of pure iron material DT4 and composite soft magnetic material SMC, the x-axis represents magnetic field strength and the y-axis represents magnetic flux density. It can be observed that, under the same magnetic field strength, the magnetic flux density of pure iron material DT4 is greater than that of composite soft magnetic material SMC. Therefore, the magnetic properties of pure iron material DT4 are superior to those of composite soft magnetic material SMC.

[0185] In related technologies, composite soft magnetic material SMC is made by pressing iron powder to coat insulating material. It has the characteristic of high resistivity, which can effectively reduce the loss of iron core blocks. However, due to the material itself and the pressing process, the magnetic properties of composite soft magnetic material SMC, such as saturation magnetic flux density and magnetic permeability, are weaker than those of commonly used iron core materials such as pure iron. Compared with pure iron materials, composite soft magnetic material SMC has weaker tensile strength but stronger compressive strength. Its mechanical properties are relatively poor compared with pure iron materials, and it cannot withstand high impact loads. The pressed finished product is brittle and will crack under high-precision processing. This results in large tolerances after the iron core block is manufactured, and it is impossible to control the thrust fluctuation during the iron core block assembly process by direct assembly or selection.

[0186] Compared to a core block made entirely of pure iron, the core block 1a according to the embodiments of this application, by using pure iron material DT4 for the core block body 11a and composite soft magnetic material SMC for the first adjusting magnetic block 12a, increases the resistivity of the core block 1a, effectively reducing iron loss. In some embodiments of this application, referring to Figures 13-15, the core block body 11a is provided with an embedding groove, and the first adjusting magnetic block 12a is embedded in the embedding groove. Thus, by embedding the first adjusting magnetic block 12a in the embedding groove of the core block body 11a, a firm connection between the first adjusting magnetic block 12a and the core block body 11a is achieved, improving the overall structural stability of the core block 1a and preventing loosening or detachment.

[0187] Optionally, the first adjusting magnetic block 12a can be fixed to the embedding groove by interference fit, by adhesive, or by other optional fixing methods.

[0188] In some embodiments of this application, referring to Figures 13-15, the embedding groove is an arc-shaped groove, which is arranged around the axis of the iron core block body 11a, and the first adjusting magnetic block 12a is an arc-shaped block. In other words, the arc-shaped groove is arranged around the axis of the iron core block body 11a, and the matching first adjusting magnetic block 12a is also arc-shaped.

[0189] Optionally, the aforementioned "arc-shaped groove surrounding the axis of the core block body 11a" can be a complete annular groove circumferentially surrounding the axis of the core block body 11a, or it can be multiple arc-shaped groove segments spaced circumferentially around the axis of the core block body 11a. When the arc-shaped groove is a complete annular groove, the first magnetic adjusting block 12a is a complete annular block. The complete annular structure can symmetrically influence the magnetic field in the axial direction, and can uniformly adjust the parameters of the magnetic field. At the same time, the complete annular structure will not experience excessive local stress when subjected to external forces such as centrifugal force and electromagnetic force, and the stress is more uniform, thereby ensuring the integrity and stability of the core block 1a.

[0190] It is understood that the embedded groove can also be multiple rectangular grooves, multiple circular grooves or other groove shapes. Similarly, the first adjusting magnetic block 12a corresponds to the shape of the embedded groove, which will not be listed here.

[0191] In some embodiments of this application, referring to Figures 13-15, the core block body 11a includes a body portion 111a and a protrusion 112a. The protrusion 112a protrudes outward relative to the body portion 111a along the axial direction of the core block 1a. The outer diameter of the body portion 111a is larger than the outer diameter of the protrusion 112a. An embedding groove is disposed on one end face of the body portion 111a near the protrusion 112a. Specifically, the embedding groove is disposed on the end face of the body portion 111a near the axial end of the protrusion 112a, as shown in Figure 15. The protrusion 112a protrudes upward relative to the body portion 111a along the axial direction of the core block 1a, and the embedding groove is disposed on the upper end face of the body portion 111a. The design of the body portion 111a and the protrusion 112a enhances the structural strength of the core block body 11a, helps to resist mechanical stress and vibration during the movement of the core block body 11a, thereby improving the durability and reliability of the core block 1a. By using precise molds and tooling, the protrusion 112a can be formed more easily and the embedded groove can be machined, simplifying the manufacturing process of the core block 1a and reducing manual operations and assembly time. This helps to improve the production efficiency of the core block 1a and reduce manufacturing costs.

[0192] Furthermore, as shown in Figures 15 and 17, after multiple iron core blocks 1a are stacked in the same direction along the axial direction, the body portion 111a of two adjacent iron core blocks 1a is separated by a protrusion 112a, so that a winding space for the coil 22 to be wound is formed between the body portions 111a of two adjacent iron core blocks 1a.

[0193] In some embodiments of this application, referring to FIG15, the first adjusting magnetic block 12a has a first inner side 121a and a first outer side 122a. The first outer side 122a is located radially outside the first inner side 121a. The radial distance between the first inner side 121a and the first outer side 122a is A1. The radial outward protrusion of the body portion 111a relative to the protrusion 112a is A2, satisfying: 0 < A1 / A2 < 1. In other words, the radial distance A1 between the first inner side 121a and the first outer side 122a is less than the radial outward protrusion A2 of the body portion 111a relative to the protrusion 112a, and the radial distance A1 between the first inner side 121a and the first outer side 122a of the first adjusting magnetic block 12a is greater than 0. Therefore, the first adjusting magnetic block 12a does not occupy the entire radial space of the body portion 111a, improving the overall tensile strength of the core block 1a, helping to resist various mechanical stresses and vibrations, thereby improving the stability and reliability of the motor 10.

[0194] In some embodiments of this application, referring to FIG15, the axial dimension of the first adjusting magnetic block 12a is B1, and the axial dimension of the body portion 111a is B2, satisfying: 0 < B1 / B2 < 1. In other words, the axial dimension B1 of the first adjusting magnetic block 12a is smaller than the axial dimension B2 of the body portion 111a, and the axial dimension B1 of the first adjusting magnetic block 12a is greater than 0. Therefore, the first adjusting magnetic block 12a does not occupy the entire axial space of the body portion 111a, improving the overall tensile strength of the core block 1a, helping to resist various mechanical stresses and vibrations, thereby improving the stability and reliability of the motor 10.

[0195] In some embodiments of this application, referring to Figures 13-15, the core block 1a further includes a limiting ring 13a. The limiting ring 13a is located on the outer periphery of the body portion 111a. Axially, the limiting ring 13a extends from one end of the body portion 111a near the protrusion 112a towards the protrusion 112a, forming a winding area between the limiting ring 13a and the protrusion 112a. Specifically, the limiting ring 13a and the protrusion 112a provide precise positioning for the winding area, which guides the coil 22 to be accurately wound in a predetermined position, avoiding the problem of coil 22 shifting or loosening. The limiting ring 13a also limits the radially outer side of the coil 22, reducing the probability of the coil 22 coming off the winding area.

[0196] In some embodiments, as shown in Figures 16 and 17, a plurality of iron core blocks 1a are arranged in the same direction, and the body portions 111a of two adjacent iron core blocks 1a are separated by protrusions 112a, so that a winding space for winding the coil 22 is formed between the body portions 111a of two adjacent iron core blocks 1a.

[0197] Referring to Figure 19, it is a comparison of the no-load thrust fluctuation of the pure iron core under the theoretical scheme and the tolerance scheme. In the theoretical scheme, the core is made entirely of pure iron and the total stacked length tolerance of the core blocks is 0. The stator tolerance is as follows: maximum +0.26 means the core is made entirely of pure iron and the total stacked length tolerance of the core blocks is +0.26. Minimum -0.26 means the core is made entirely of pure iron and the total stacked length tolerance of the core blocks is -0.26. The x-axis represents the displacement change of the core relative to the magnetic component, and the y-axis represents the motor thrust of the three schemes under different displacements.

[0198] Referring to Figure 20, which is a bar chart comparing the thrust fluctuation of a pure iron core under the theoretical scheme and the tolerance scheme, the pure iron core represents an iron core made entirely of pure iron. The theoretical scheme is an iron core made entirely of pure iron with a total stacked length tolerance of 0. The stator total length +0.26 represents an iron core made entirely of pure iron with a total stacked length tolerance of +0.26. The stator total length -0.26 represents an iron core made entirely of pure iron with a total stacked length tolerance of -0.26. The blue bars represent the thrust fluctuation of the motor at 0A current, and the red bars represent the thrust fluctuation of the motor at 40A current.

[0199] The influence of the total superimposed tolerance length and theoretical length of the iron core blocks on thrust fluctuation under pure iron material is shown in Figure 20. At a current of 40A, the thrust fluctuation of the motor under the theoretical scheme is 170N for pure iron material, while the thrust fluctuation is 239.7N under the stator tolerance of -0.26. It can be seen that a length difference of only 0.26 can bring a 41% increase in thrust fluctuation, illustrating the necessity of tolerance precision control for the iron core. However, for composite soft magnetic materials, due to their characteristics, precision machining is impossible. Simply stacking multiple iron core blocks axially will lead to greater tolerance accumulation, resulting in increased thrust fluctuation, a problem that needs to be addressed.

[0200] According to the embodiment of this application, the iron core 23 has an iron core block body 11a made of a material with superior mechanical properties, such as pure iron, which allows the iron core block body 11a to be precision machined and reduces tolerance accumulation when multiple iron core blocks are axially stacked. At the same time, the first magnetic adjustment block 12a of the iron core block 1a is made of a material with high resistivity, such as composite soft magnetic material, which allows the first magnetic adjustment block 12a to locally adjust the resistance of the magnetic circuit, which helps to optimize the magnetic field distribution and make the magnetic field more uniformly distributed in the iron core 23. By increasing the resistivity of the iron core block 1a, magnetic flux leakage and eddy current loss can be effectively reduced, thereby improving the performance of the motor 10.

[0201] In some embodiments of this application, referring to Figures 13-17, the core block 1a has a first central hole 14a, and the first central holes 14a of multiple core blocks 1a are interconnected to form a core hole. The core 23 also includes a second magnetic adjustment block 2a, which is installed on the hole wall of the core hole. The second magnetic adjustment block 2a has a second central hole 21a through which the central shaft passes. The material of the second magnetic adjustment block 2a is at least partially different from that of the core block body 11a, and the resistivity of the second magnetic adjustment block 2a is higher than that of the core block body 11a. Specifically, the resistivity of the second adjusting magnetic block 2a is higher than that of the iron core block body 11a, and the second adjusting magnetic block 2a is installed between the iron core block 1a and the central shaft 21. This makes the second adjusting magnetic block 2a further increase the resistivity of the iron core 23, thereby reducing the eddy current loss generated by the iron core 23, reducing magnetic flux leakage and eddy current loss, improving the performance of the iron core 23, thereby increasing the thrust output of the motor 10 and improving the working efficiency of the motor 10 in the high-speed range.

[0202] It should be noted that "the materials of the second adjusting magnetic block 2a and the iron core block body 11a are at least partially different" can mean that the material of the second adjusting magnetic block 2a is a mixture, the material of the iron core block body 11a is a mixture, and at least a portion of the components in the mixture of the second adjusting magnetic block 2a and the iron core block body 11a are different. It can also mean that the material of the second adjusting magnetic block 2a is a pure first material, and the material of the iron core block body 11a is a pure second material, and the first material and the second material are different. Of course, it can also mean that the material of the second adjusting magnetic block 2a is a mixture, the material of the iron core block body 11a is a pure second material, or it can mean that the material of the second adjusting magnetic block 2a is a pure first material, and the material of the iron core block body 11a is a mixture.

[0203] In some embodiments of this application, referring to Figures 13-17, the tensile strength of the material of the core block body 11a is greater than the tensile strength of the material of the second magnetic adjustment block 2a. In other words, the mechanical properties of the material of the core block body 11a are superior to those of the material of the second magnetic adjustment block 2a. Therefore, the second magnetic adjustment block 2a, installed on the wall of the core hole, does not serve as a load-bearing component. The core block body 11a, as the main load-bearing part of the core block 1a, has higher tensile strength, which enhances the overall structural strength of the core block 1a, helping to resist various mechanical stresses and vibrations, thereby improving the stability and reliability of the core block 1a.

[0204] Optionally, the second adjusting magnetic block 2a may be made of a composite soft magnetic material, such as SMC, metal magnetic powder core composite material, soft magnetic ferrite composite material, or other composite soft magnetic materials. In the following embodiments, the second adjusting magnetic block 2a using the composite soft magnetic material SMC will be used as an example.

[0205] Optionally, the second adjusting magnetic block 2a and the first adjusting magnetic block 12a can be made of the same material or different materials.

[0206] Optionally, the second adjusting block 2a can be installed on the wall of the iron core hole by adhesive bonding or by interference fit.

[0207] Optionally, the second adjusting magnetic block 2a is integrally pressed. This ensures that the precision of the second adjusting magnetic block 2a is significantly improved compared to the assembly method of segmented pressing followed by axial stacking, eliminating the possibility of tolerance accumulation.

[0208] In some embodiments of this application, referring to Figure 17, the number of iron core blocks 1a is N, the axial length of a single iron core block 1a is P, the axial length of the second adjusting magnetic block 2a is Q, P×(N-1)<Q≤P×N, N≥2 and N is an integer. Specifically, the second adjusting magnetic block 2a is connected to the iron core block body 11a of any iron core block 1a, and the axial length Q of the second adjusting magnetic block 2a is less than or equal to the total axial length P×N of the multiple iron core blocks 1a. This avoids the second adjusting magnetic block 2a from exceeding the axial orientation of the multiple iron core blocks 1a and causing damage due to stress, while ensuring that the second adjusting magnetic block 2a is effectively connected to all iron core blocks 1a, increasing the resistivity of the iron core 23, reducing the eddy current losses generated by the iron core 23, thereby increasing the thrust output of the motor 10 and improving the working efficiency of the iron core 23 in the high-speed range.

[0209] In some embodiments of this application, referring to FIG17, the core block body 11a includes a body portion 111a and a protrusion portion 112a. The protrusion portion 112a protrudes outward relative to the body portion 111a along the axial direction of the core block 1a. The second magnetic adjustment block 2a has a second inner side surface 22a and a second outer side surface 23a. The second outer side surface 23a is located radially outside the second inner side surface 22a. The radial distance between the second inner side surface 22a and the second outer side surface 23a is C1. In the radial direction of the core 23, the radial distance between the second inner side surface 22a and the outer side surface of the protrusion portion 112a is C2, satisfying: 0 < C1 / C2 < 1. Specifically, the radial distance C1 between the second inner side surface 22a and the second outer side surface 23a is less than the radial distance C2 between the second inner side surface 22a and the outer side surface of the protrusion portion 112a, and C1 is greater than 0. Therefore, by adjusting the ratio of C1 and C2 according to the actual needs of the iron core 23, the position and thickness of the second magnetic adjustment block 2a in the radial direction of the iron core 23 can be precisely controlled, thereby more accurately increasing the resistivity of the iron core 23, reducing the eddy current loss generated by the iron core 23, and thus improving the thrust output of the motor 10 and the working efficiency of the motor 10 in the high-speed range.

[0210] Specifically, when the second adjusting magnetic block 2a is embedded between the central shaft and the core block body 11a, since the axial length Q of the second adjusting magnetic block 2a is less than or equal to the total axial length P×N of the multiple core blocks 1a, the second adjusting magnetic block 2a does not act as the load-bearing body, and the core block body 11a can withstand more impacts, increasing the mechanical strength of the core 23. The first adjusting magnetic block 12a is embedded in the body part 111a and does not act as the load-bearing body. Therefore, the comprehensive mechanical properties of the core 23 in this application are significantly stronger than the comprehensive mechanical properties of the core made entirely of composite soft magnetic materials.

[0211] Specifically, the contact body between the iron core 23 and external components is the iron core block body 11a. By precision machining the axial cross-section of the iron core block body 11a and then selecting appropriate components, the axial dimension of the iron core 23 can be made close to the theoretical model. Compared with the assembly of an iron core where all parts are composite soft magnetic materials, the iron core 23 of this application can greatly reduce thrust fluctuation and ensure the NVH performance of the entire machine. The thrust fluctuation histogram obtained by accumulating negative tolerances for the three types of iron cores according to the optimal tolerances and then selecting appropriate components is shown in Figure 23. In this figure, the pure iron stator represents an iron core where all materials are pure iron, the composite soft magnetic material stator represents an iron core where all materials are composite soft magnetic materials, and the hybrid stator is the iron core 23 of this application. The blue bars represent the thrust fluctuation of each iron core under a current of 0A, and the red bars represent the thrust fluctuation of each iron core under a current of 40A. It can be seen that the composite soft magnetic material stator is more difficult to select due to insufficient machining accuracy, and the hybrid stator has a significantly lower thrust fluctuation compared to the composite soft magnetic material stator.

[0212] In some embodiments, referring to Figure 21, a comparison of the thrust output of three types of iron cores is shown. In the motors containing the three types of iron cores, each iron core has 2 pole pairs, the magnetic components have 10 pole pairs, the number of iron core slots is 12, and the number of turns per slot is 30. The C2 of all three types of iron cores is 5.6 mm, B2 is 6.15 mm, and A2 is 22.5 mm. The C1 of the hybrid stator is 3.0 mm, B1 is 3.0 mm, and A1 is 18.5 mm. Figure 21 shows that CT4 is an iron core made entirely of pure iron material, SMC is an iron core made entirely of composite soft magnetic material, and the hybrid stator is the iron core 23 of this application. The x-axis represents the current connected to the iron core, the left side of the y-axis represents the thrust of the motors using DT4, SMC, and the hybrid stator at the corresponding current, and the right side of the y-axis represents the percentage increase in thrust of the hybrid stator compared to DT4. The maximum RMS current of the motors used in the experiment can reach 120A. By mounting the three motors on a linear motion test bench and having the bench drive the motors in a linear motion of 2m / s while applying the maximum current to the motors, the maximum thrust value of the motors under high-speed conditions can be obtained. It can be found that although the thrust output of the hybrid stator is lower than that of the integral composite soft magnetic material core, compared with the pure iron core, at high speed and high current of 2m / s, such as at a current of 110A, the output thrust increases by 40%. At high speed and low current, such as at a current of 20A, the output thrust can even reach 450% of that of pure iron (not shown in the figure).

[0213] Referring to Figure 22, it shows the loss reduction rate of the hybrid stator compared to the pure iron stator under different currents at a high speed of 2 m / s. The hybrid stator is the core 23 of this application, while the pure iron stator is a core made entirely of pure iron. The x-axis represents the current magnitude, and the y-axis represents the loss reduction rate. It can be seen that under high currents such as 110 A, the hybrid stator can achieve a loss reduction rate of at least 35%, while under high-speed, low-current conditions such as 20 A, the loss can even be reduced by 80%. This demonstrates that the core 23 of this application has a significant optimization effect on thrust and loss.

[0214] In some embodiments of this application, referring to Figures 13-17, in the radial direction of the core block 1a, the first adjusting magnetic block 12a has a first inner side surface 121a and a first outer side surface 122a. The first outer side surface 122a is located radially outside the first inner side surface 121a, and the radial distance between the first inner side surface 121a and the first outer side surface 122a is A1. In the radial direction of the core block 1a, the body portion 111a protrudes radially outward relative to the protrusion portion 112a by a dimension of A2. The adjusting magnetic block 2a has a second inner surface 22a and a second outer surface 23a. The second outer surface 23a is located radially outside the second inner surface 22a. The radial distance between the second inner surface 22a and the second outer surface 23a is C1. In the radial direction of the iron core 23, the radial distance between the second inner surface 22a and the outer surface of the protrusion 112a is C2. In the axial direction of the iron core block 1a, the axial dimension of the first adjusting magnetic block 12a is B1, and the axial dimension of the body portion 111a is B2, satisfying the following:

[0215] 0.7>0.4364×B1 / B2+0.2956×A1 / A2+0.09597×C1 / C2-0.1246488≥0.2;

[0216] 0 < A1 / A2 < 1;

[0217] 0 < B1 / B2 < 1;

[0218] 0 < C1 / C2 < 1.

[0219] Specifically, by adding the first adjusting magnetic block 12a and the second adjusting magnetic block 2a, and adjusting the ratios of B1 / B2, A1 / A2, and C1 / C2, the thrust of the iron core 23 is increased by more than 20% compared to the iron cores using pure iron materials in the prior art. This increases the driving force of the iron core 23 in this application, enhances the torque output capability of the motor 10, thereby increasing the output power of the motor 10 and improving the working efficiency of the iron core 23.

[0220] Specifically, by selecting different values ​​for B1, B2, A1, A2, C1, and C2, the thrust of the iron core 23 and the pure iron core of this application were experimentally measured, thereby obtaining the actual thrust increase rate. Response surface analysis was performed on the above values ​​using Design-Expert software to obtain the formula for the thrust increase rate M of the iron core 23 and the pure iron core of this application:

[0221] M=0.4364×B1 / B2+0.2956×A1 / A2+0.09597×C1 / C2-0.1246488

[0222] Meanwhile, Figures 24-26 show the results of linear analysis using the response surface methodology. In Figure 24, the ratio of the radial distance C1 between the second inner side 22a and the second outer side 23a to the radial distance C2 between the second inner side 22a and the outer side of the protrusion 112a remains constant, i.e., C1 / C2 remains constant. The A-axis is the ratio of the radial distance A1 between the first inner side 121a and the first outer side 122a of the first magnetic adjustment block 12a to the radially outward protrusion A2 of the body part 111a relative to the protrusion 112a, i.e., A1 / A2. The B-axis is the ratio of the axial dimension B1 of the first magnetic adjustment block 12a to the axial dimension B2 of the body part 111a, i.e., B1 / B2. The vertical axis represents the change in thrust lift rate M under different ratios of A1 / A2 and B1 / B2. In Figure 25, the ratio of the axial dimension B1 of the first adjusting magnetic block 12a to the axial dimension B2 of the body portion 111a remains unchanged, i.e., B1 / B2 remains unchanged. The A-axis is the ratio of the radial distance A1 between the first inner side surface 121a and the first outer side surface 122a of the first adjusting magnetic block 12a to the radial outward protrusion dimension A2 of the body portion 111a relative to the protrusion portion 112a, i.e., A1 / A2. The C-axis is the ratio of the radial distance C1 between the second inner side surface 22a and the second outer side surface 23a to the radial distance C2 between the second inner side surface 22a and the outer side surface of the protrusion portion 112a, i.e., C1 / C2. The vertical axis represents the change in thrust lift rate M under different ratios of A1 / A2 and C1 / C2. Figure 26 compares the actual fit between the formula and the data. A reference line y = x is present in the figure, representing the ideal situation where the derived thrust increase rate equals the actual measurement result. The positional relationship between the data points marked with different colors and the reference line y = x reflects the actual situation of the formula derivation and the actual measurement result. If the data point is on the line, it means the actual thrust increase rate is consistent with the derived thrust increase rate; if the data point is above the line, it means the actual thrust increase rate is greater than the derived thrust increase rate; and if the data point is below the line, it means the actual thrust increase rate is less than the derived thrust increase rate. As can be seen from Figure 26, the difference between the derived formula result and the actual thrust increase rate is small.

[0223] The thrust increase rate of the hybrid stator relative to pure iron can be calculated using the above formula for different sizes, thus providing direction for hybrid stator design. Under the premise of achieving low thrust fluctuation through selective fitting, this application requires a significant increase in thrust. To meet the load-bearing requirements of passenger cars, M needs to be increased by at least 20%, i.e., M ≥ 20%. Since B1 / B2 < 1, A1 / A2 < 1, and C1 / C2 < 1, M < 0.7. In summary, the thrust increase rate needs to satisfy the following:

[0224] 0.7>0.4364×B1 / B2+0.2956×A1 / A2+0.09597×C1 / C2-0.1246488≥0.2.

[0225] Optionally, based on C2 being 5.6mm, B2 being 6.15mm, and A2 being 22.5mm, the ratios can be: B1 / B2 = 0.325, A1 / A2 = 0.867, and C1 / C2 = 0.617; B1 / B2 = 0.488, A1 / A2 = 0.822, and C1 / C2 = 0.511; or B1 / B2 = 0.407, A1 / A2 = 0.778, and C1 / C2 = 0.617, etc. If a thrust increase rate of exactly 0.2 is required, i.e., M = 0.2, then B1 / B2 can be 0.0813, A1 / A2 0.778, and C1 / C2 0.617.

[0226] It should be understood that the values ​​of A1 / A2, B1 / B2, and C1 / C2 mentioned above are not limitations on the present invention. Other values ​​that meet the requirements of B1 / B2<1, A1 / A2<1, and C1 / C2<1 and 0.7>M≥0.2 can all be used as embodiments of this application, and will not be listed one by one here.

[0227] According to the second component 2 of the present application embodiment, the iron core block 1a of the iron core 23 can locally adjust the resistance of the magnetic circuit by setting a first magnetic adjustment block 12a with high resistivity on the iron core block body 11a, which helps to optimize the magnetic field distribution and make the magnetic field more evenly distributed in the iron core 23. By increasing the resistivity of the iron core block 1a, magnetic flux leakage and eddy current loss can be effectively reduced, thereby improving the performance of the motor 10.

[0228] In some embodiments, as shown in Figures 27-35, the central shaft 21 of the second component 2 includes a first central shaft body 11b and a second central shaft body 12b. The first central shaft body 11b and the second central shaft body 12b are arranged and fixedly connected along the axial direction of the central shaft 21, and a shoulder 20b is formed on the radially outer side of the first central shaft body 11b. The core 23 includes a plurality of core blocks 1a, which are arranged along the axial direction of the central shaft 21. The core blocks 1a are all assembled on the second central shaft 12b. Among the core blocks 1a, there is a first end core block 32b adjacent to the first central shaft 11b. The first end core block 32b has a support portion 33b. The support portion 33b abuts against the shoulder 20b to limit the relative position of the first end core block 32b and the first central shaft 11b. A clearance space 321b is formed at the end of the first end core block 32b facing the first central shaft 11b. The clearance space 321b is opposite to the first central shaft 11b along the axial direction of the central shaft 21 so that the first end core block 32b and the first central shaft 11b are spaced apart.

[0229] The second component 2 includes a central shaft 21 and an iron core 23. The central shaft 21 includes a first central shaft body 11b and a second central shaft body 12b, which are arranged along the axial direction of the central shaft 21 and are fixedly connected. The first and second central shaft bodies 11b and 12b can be integrally formed or welded together. The connection method is not specifically limited, as long as they are fixedly connected. The second central shaft body 12b is used to mount the iron core 23 and to position the iron core 23. As shown in Figures 29 and 32, the cross-sectional area of ​​the first central shaft body 11b is larger than that of the second central shaft body 12b, and the second central shaft body 12b is positioned at the midpoint corresponding to the first central shaft body 11b. The central axis of the first central axis 11b coincides with the central axis of the second central axis 12b, or it can be understood that the central axis of the first central axis 11b and the central axis of the second central axis 12b are collinear.

[0230] A shoulder 20b is formed on the radially outer side of the first central shaft 11b. The shoulder 20b extends radially away from the first central shaft 11b and is disposed adjacent to the end face of the first central shaft 11b facing the second central shaft 12b along the axial direction of the central shaft 21. As an example, the shoulder 20b can be formed on the outer wall of the first central shaft 11b, and the shoulder 20b can be integrally formed with the first central shaft 11b. As another example, the outer side of the first central shaft 11b can be fitted onto a sleeve 40b, and the sleeve 40b and the first central shaft 11b are fixedly connected. The outer wall of the sleeve 40b facing away from the first central shaft 11b can be formed with a shoulder 20b, and the shoulder 20b can be integrally formed with the sleeve 40b.

[0231] The iron core 23 includes multiple iron core blocks 1a. There can be two, three, four, five, or more iron core blocks 1a, and the number of iron core blocks 1a can be reasonably selected according to actual conditions. The multiple iron core blocks 1a are arranged sequentially along the axial direction of the central shaft 21, and are stacked sequentially. A second central shaft 12b can simultaneously pass through multiple iron core blocks 1a. Each iron core block 1a can have a first central hole 14a, and the second central shaft 12b simultaneously passes through the first central holes 14a of multiple iron core blocks 1a. A locking member 50b is installed at the end of the second central shaft 12b opposite to the first central shaft 11b. The locking member 50b abuts against the second end core block 36b of the core 23 opposite to the first central shaft 11b, thereby positioning the core 23 between the shoulder 20b and the locking member 50b. The second end core block 36b refers to the core block 1a of the core 23 that is farthest from the first central shaft 11b along the axial direction of the central shaft 21. The locking member 50b can be a nut, and the outer wall of the second central shaft 12b can be formed with external threads. The external threads can be adjacent to the end of the second central shaft 12b opposite to the first central shaft 11b. By turning the locking member 50b, the locking member 50b and the first central shaft 11b can be disassembled and assembled, thereby facilitating the disassembly and assembly of the core 23 and the central shaft 21.

[0232] Along the axial direction of the central axis 21, among the plurality of core blocks 1a, there is a first end core block 32b adjacent to the first central shaft body 11b. The first end core block 32 has a support portion 33b. As one example, the support portion 33b can be integrally formed with the first end core block 32. As another example, the support portion 33b can be a separate part from the first end core block 32, with the support portion 33b fixed to the first end core block 32. This application describes the example of the support portion 33b being integrally formed with the first end core block 32. The support portion 33b abuts against the shoulder 20b, which can limit the relative position of the first end core block 32 and the first central shaft body 11b along the axial direction of the central axis 21, thereby fixing the relative position of the first end core block 32 and the first central shaft body 11b. The end of the first end core block 32 facing the first central shaft 11b has a clearance space 321b. The clearance space 321b is opposite to the first central shaft 11b along the axial direction of the central shaft 21, which can separate the first end core block 32 and the first central shaft 11b.

[0233] When the iron core 23 is installed on the second central shaft 12b, the support 33b abuts against the shoulder 20b, and the clearance space 321b is opposite to the first central shaft 11b along the axial direction of the central shaft 21. This allows the first end iron core block 32 and the first central shaft 11b to be spaced apart along the axial direction of the central shaft 21, with a certain distance between them. The first end iron core block 32 refers to the first end iron core block 32b of the iron core 23 that is closest to the first central shaft 11b along the axial direction of the central shaft 21.

[0234] It should be noted that due to the machining accuracy of the central shaft, the shoulder cannot be perfectly perpendicular to the first central shaft body. There is an angular deviation of less than 0.1° between the shoulder and the first central shaft body. However, the cross-sectional area of ​​the first central shaft body is larger than that of the second central shaft body, and the first central shaft body has greater rigidity. After the iron core is installed on the second central shaft body, the first end iron core block 32b abuts against the end face of the first central shaft body facing the second central shaft body, and the first end iron core block 32b abuts against the shoulder. During the installation and locking process of the iron core, since the shoulder cannot be perfectly perpendicular to the first central shaft body, the second central shaft body is subjected to a force along the axial direction of the central shaft and a radial force applied by the iron core. The second central shaft body is prone to deformation and skew, resulting in a decrease in the coaxiality of the central shaft, which in turn increases the resistance of the motor throughout its stroke and affects the motor's working performance.

[0235] In this application, the support portion 33b abuts against the shoulder 20b, fixing the relative positions of the first end core block 32 and the first central shaft 11b. The support portion 33b is spaced apart from the first central shaft 11b. A clearance space 321b is formed at the end of the first end core block 32 facing the first central shaft 11b. The clearance space 321b is opposite to the first central shaft 11b along the axial direction of the central shaft 21, thus separating the first central shaft 11b and the first end core block 32. The core 23 is mounted on the second central shaft 1. After step 2b, the first end iron core block 32 and the first central shaft 11b are spaced apart along the axial direction of the central shaft 21. The first end iron core block 32 does not abut against the first central shaft 11b, but abuts against the shoulder 20b. During the installation and locking process of the iron core 23, the shoulder 20b and the first end iron core block 32 deform, reducing the risk of deformation and misalignment of the second central shaft 12b. This helps to improve the coaxiality of the central shaft 21, thereby helping to reduce the full-stroke resistance of the motor and thus improve the working performance of the motor.

[0236] Therefore, by having the support 33b abut against the shoulder 20b and the clearance space 321b opposite to the first central shaft 11b, the first end iron core block 32 and the first central shaft 11b are separated. During the installation of the locking member 50b at the end of the second central shaft 12b away from the first central shaft 11b, the risk of deformation or skew of the second central shaft 12b is reduced. This is beneficial to improving the coaxiality of the central shaft 21 and also to reducing the full-stroke resistance of the motor, thereby improving the working performance of the motor.

[0237] In some embodiments of the present invention, as shown in Figures 29 and 32, the support portion 33b is located on the side of the shoulder 20b facing the second central shaft 12b, and the end face of the support portion 33b abuts against the shoulder 20b.

[0238] In this configuration, along the axial direction of the central axis 21, the support portion 33b is located on the side of the shoulder 20b facing the second central shaft 12b. The support portions 33b are arranged opposite each other along the axial direction of the central axis 21, with the end face of the support portion 33b facing the shoulder 20b and the end face of the shoulder 20b facing the support portion 33b abutting against each other. By positioning the support portion 33b on the side of the shoulder 20b facing the second central shaft 12b, the support portion 33b and the shoulder 20b can be reliably abutted against each other. During the installation and locking process of the iron core 23, the risk of the support portion 33b and the shoulder 20b disengaging is reduced, as is the risk of the first end iron core block 32 deforming and abutting against the first central shaft 11b. This further reduces the risk of deformation and skewness of the second central shaft 12b.

[0239] In some embodiments of the present invention, as shown in Figures 29, 32, and 33, the support portion 33b is adjacent to the outer edge of the first end core block 32b along the radial direction of the first end core block 32b. This affixing of the support portion 33b to the outer edge of the first end core block 32 along the radial direction can also be understood as the support portion 33b being adjacent to the circumferential edge of the first end core block 32, with the support portion 33b positioned at the edge of the first end core block 32. Since a shoulder 20b is formed on the radially outer side of the first central shaft 11b, the support portion 33b can directly abut against the shoulder 20b after the core 23 is installed on the second central shaft 12b, facilitating the engagement and contact between the support portion 33b and the shoulder 20b, thus ensuring a reasonable positioning of the support portion 33b.

[0240] In some embodiments of the present invention, along the axial direction of the central axis 21, the end of the first end core block 32b facing the first central axis 11b is formed with a recessed clearance space 321b in the direction away from the first central axis 11b, so as to form a support portion 33b on the radially outer side of the clearance space 321b.

[0241] As shown in Figures 29 and 33, along the axial direction of the central axis 21, a recessed clearance space 321b is formed at the end of the first end core block 32 facing the first central shaft body 11b. The clearance space 321b can be formed by removing part of the structure from the first end core block 32. The end of the clearance space 321b facing the first central shaft body 11b is open. After removing part of the structure from the first end core block 32, a support portion 33b is formed radially outside the clearance space 321b. The support portion 33b is the sidewall of the clearance space 321b. The clearance space 321b and the first central hole 14a are adjacent to and connected along the axial direction of the central shaft 21. The second central shaft 12b passes through the clearance space 321b and the first central hole 14a. By setting the clearance space 321b, the structural strength of the first end iron core block 32 can be reduced. During the installation and locking process of the iron core 23, it is beneficial to deform the first end iron core block 32, which can further reduce the risk of deformation and skew of the second central shaft 12b. In addition, it can also reduce the weight of the first end iron core block 32, which is beneficial to the lightweight design of the second component 2.

[0242] The clearance space 321b and the first central shaft 11b correspond to each other along the axial direction of the central shaft 21. The orthographic projection of the first central shaft 11b can be located within the clearance space 321b along the axial direction of the central shaft 21. After the iron core 23 is installed on the second central shaft 12b, the clearance space 321b has a clearance function, which can separate the first end iron core block 32 and the first central shaft 11b.

[0243] In some embodiments of the present invention, as shown in FIG29, the cross-sectional dimension of the clearance space 321b is larger than the cross-sectional dimension of the first central shaft body 11b, and the orthographic projection of the first central shaft body 11b is located within the clearance space 321b along the axial direction of the central shaft 21.

[0244] In this configuration, the cross-sectional dimension of the clearance space 321b is larger than that of the first central shaft 11b in the axial direction perpendicular to the central axis 21. The orthographic projection of the first central shaft 11b is located within the clearance space 321b in the axial direction of the central axis 21, and the projected outline of the first central shaft 11b is located inside the inner wall of the clearance space 321b. Because the cross-sectional dimension of the clearance space 321b is larger than that of the first central shaft 11b, after the iron core 23 is installed on the second central shaft 12b, it is beneficial to ensure that the orthographic projection of the first central shaft 11b in the axial direction of the central axis 21 is located within the clearance space 321b. This is beneficial to separate the first end iron core block 32 from the first central shaft 11b. Furthermore, during the installation and locking process of the iron core 23, the risk of the first end iron core block 32 deforming and abutting against the first central shaft 11b can be further reduced, thereby further reducing the risk of deformation and skewness of the second central shaft 12b.

[0245] In some embodiments of the present invention, as shown in Figures 29 and 34, a clearance space 321b is formed at the middle position of the first end core block 32b. Specifically, the clearance space 321b is formed at the exact center of the first end core block 32, and the central axis of the clearance space 321b coincides with the central axis of the first central shaft 11b. By forming the clearance space 321b at the middle position of the first end core block 32, after the core 23 is installed on the second central shaft 12b, it is convenient for the clearance space 321b and the first central shaft 11b to be correspondingly arranged along the axial direction of the central axis 21. This facilitates ensuring that the orthogonal projection of the first central shaft 11b along the axial direction of the central axis 21 is located within the clearance space 321b.

[0246] In some embodiments of the present invention, the cross-section of the clearance space 321b is circular, the cross-section of the first central shaft 11b is circular, the maximum diameter of the first central shaft 11b is D1, and the diameter of the clearance space 321b is D2, satisfying the relationship: 1.02≤D2 / D1≤1.05.

[0247] In this embodiment, the cross-sections of both the clearance space 321b and the first central shaft 11b are circular. Alternatively, the cross-sections of both the clearance space 321b and the first central shaft 11b are similarly circular. Or, one of the cross-sections of both the clearance space 321b and the first central shaft 11b is circular, and the other is similarly circular. This application uses the example of both the cross-sections of the clearance space 321b and the first central shaft 11b being circular for illustration. The maximum diameter of the first central shaft 11b is D1 mm, and the diameter of the clearance space 321b is D2 mm. D2 / D1 can be values ​​such as 1.02, 1.03, 1.031, 1.04, 1.05, etc., and D2 / D1 can be any value between 1.02 and 1.05.

[0248] Since the material of the central shaft 21 is generally stainless steel and the material of the iron core 23 is generally pure iron, and the yield strength of stainless steel is greater than 205 MPa and the yield strength of pure iron is greater than 180 MPa, the strength factor should be considered when designing the dimensions of the first central shaft 11b and the clearance space 321b. This includes considering the maximum thrust of the motor, the thrust fluctuation of the motor, and the deviation suppression rate of the central shaft 21. By setting 1.02≤D2 / D1≤1.05, the maximum thrust of the motor can be effectively reduced while ensuring sufficient strength of the first end iron core block 32. This also effectively reduces the thrust fluctuation of the motor, improves the deviation suppression rate of the central shaft 21, and improves the maximum stress of the first end iron core block 32 and the maximum stress of the shoulder 20b. During the installation and locking process of the iron core 23, this facilitates the deformation of the first end iron core block 32, further reducing the risk of deformation and skewness of the second central shaft 12b, and improving the coaxiality of the central shaft 21.

[0249] In some embodiments of the present invention, along the axial direction of the central axis 21, the thickness of the first end core block 32b is H1, and the depth of the clearance space 321b is H2, satisfying the relationship: 0.25≤H2 / H1≤0.55.

[0250] As shown in Figure 34, along the axial direction of the central shaft 21, the thickness of the first end iron core block 32 is H1 mm, and the depth of the clearance space 321b is H2 mm. H2 / H1 can be any value between 0.25, 0.251, 0.255, 0.35, 0.45, and 0.55. By ensuring that 0.25 ≤ H2 / H1 ≤ 0.55, the first end iron core block 32 has sufficient strength, which effectively reduces the maximum thrust of the motor and its thrust fluctuations. It also improves the deviation suppression rate of the central shaft 21, reduces the maximum stress of the first end iron core block 32 and the maximum stress of the shoulder 20b, and facilitates deformation of the first end iron core block 32 during the installation and locking process of the iron core 23. This further reduces the risk of deformation and skewness of the second central shaft 12b and improves the coaxiality of the central shaft 21.

[0251] In some embodiments of the present invention, by combining 1.02≤D2 / D1≤1.05 with 0.25≤H2 / H1≤0.55, the maximum thrust of the motor can be further reduced while ensuring sufficient strength of the first end core block 32. This also further reduces the thrust fluctuation of the motor, improves the deviation suppression rate of the central shaft 21, and improves the maximum stress of the first end core block 32 and the maximum stress of the shoulder 20b. During the installation and locking process of the core 23, the first end core block 32 is more likely to deform than the second central shaft 12b, further reducing the risk of deformation and skew of the second central shaft 12b, and further improving the coaxiality of the central shaft 21.

[0252] It should be noted that, compared with the prior art, after the second component 2 of this application is installed on the motor, as shown in Figure 37, the maximum thrust of the motor is reduced to 98.4% of that in the prior art. As shown in Figure 38, the thrust fluctuation of the motor is also reduced, up to 82.9% of that in the prior art. As shown in Figure 39, the deviation suppression rate of the central shaft 21 can be suppressed by up to 47.8%. The maximum stress of the first end core block 32 varies with D2, D1, H2, and H1 as shown in Figure 40. The maximum stress of the shoulder 20b varies with D2, D1, H2, and H1 as shown in Figure 41.

[0253] In some embodiments of the present invention, along the axial direction of the central shaft 21, the length dimension of the second central shaft body 12b is X1, and the thickness dimension of the shoulder 20b is X2, satisfying the relationship: 0.02≤X2 / X1≤0.07.

[0254] Along the axial direction of the central shaft 21, the length of the second central shaft body 12b is X1 mm, the thickness of the shoulder 20b is X2 mm, and X2 / X1 can be any value between 0.02, 0.03, 0.04, 0.05, 0.06, 0.07, etc.

[0255] A high deviation suppression rate for the central shaft 21 also implies a higher maximum stress value for the shoulder 20b. Considering that the shoulder 20b still has some margin, its thickness can be reduced to decrease its stiffness, thereby improving the deviation suppression rate of the central shaft 21. The following explanation uses D2 / D1 = 1.05 and H2 / H1 = 0.55 as examples, where 1.02 ≤ D2 / D1 ≤ 1.05 and 0.25 ≤ H2 / H1 ≤ 0.55. Values ​​1.05 and 0.55 represent the range with the highest deviation suppression rate for the central shaft 21, the highest stress on the central shaft 21, and the highest stress on the first end core block 32. Furthermore, values ​​1.05 and 0.55 are the optimal combination for reducing thrust fluctuations and ensuring maximum thrust. The required range for the thickness of the shoulder 20b can be calculated using D2 / D1 = 1.05 and H2 / H1 = 0.55.

[0256] Figure 36 shows the variation of the deviation suppression rate and the maximum stress of the central shaft 21 (considering only elasticity, not yield strength) with X2 / X1. It can be seen that when X2 / X1 < 0.02, the maximum stress of the central shaft 21 approaches the yield strength, and the stress increases sharply. However, when 1.02 ≤ D2 / D1 ≤ 1.05 and 0.25 ≤ H2 / H1 ≤ 0.55, the stress of the central shaft 21 is already the maximum value within the range of D2 / D1 and H2 / H1. Therefore, from a conservative strength assessment perspective, X2 / X1 ≥ 0.02 should be determined. When X2 / X1 > 0.07, the deviation suppression rate and the maximum stress of the central shaft 21 gradually stabilize. Further increasing the thickness of the shoulder 20b yields little benefit and will further compress the length of the second central shaft 12b, affecting the motor stroke. Therefore, by setting 0.02≤X2 / X1≤0.07, the deformation and skewness of the second central shaft 12b are reduced, which helps to ensure that the shoulder 20b has sufficient strength to meet the usage requirements. It also helps to set a longer second central shaft 12b, which in turn helps to increase the motor stroke.

[0257] In some embodiments of the present invention, a boss structure (not shown in the figure) is formed on the end face of the first end core block 32b facing the first central shaft 11b. The boss structure protrudes from the end face of the first end core block 32 facing the first central shaft 11b. The boss structure is constructed as a support portion 33b. The boss structure is directly provided on the end face of the first end core block 32 facing the first central shaft 11b. The boss structure can be integrally formed with the first end core block 32, or it can be constructed as a separate part from the first end core block 32. The boss structure is fixed to the first end core block 32. In this embodiment, it is not necessary to dig a groove at the end face of the first end core block 32, which facilitates the formation of the support portion 33b and thus facilitates the manufacturing of the first end core block 32. Furthermore, the boss structure extends circumferentially along the first end core block 32b to define a clearance space 321b. The boss structure can be a ring structure, so that the boss structure and the first end core block 32 jointly define the clearance space 321b. The boss structure can also be a semi-ring structure, so that the boss structure and the first end iron core block 32 together define the clearance space 321b.

[0258] In some embodiments of the present invention, as shown in FIG32, the shoulder 20b may include a plurality of sub-shoulders 21b, which are arranged sequentially at intervals along the axial direction of the central axis 21. The shoulder 20b may include two, three, or four sub-shoulders 21b. This application describes a shoulder 20b including two sub-shoulders 21b as an example. The two sub-shoulders 21b are arranged at intervals along the axial direction of the central axis 21, forming a buffer space between adjacent sub-shoulders 21b, reducing the stiffness of the shoulder 20b. When the sub-shoulders 21b are under stress, this facilitates their deformation. After the iron core 23 is installed on the second central shaft 12b, the first end iron core block 32 and the sub-shoulders near the second central shaft 12b... The shoulder 21b abuts against the iron core 23 during installation and locking, which helps to deform the sub-shoulder 21b near the second central shaft 12b. The deformation of the sub-shoulder 21b can abut against the adjacent sub-shoulder 21b, thereby deforming the adjacent sub-shoulder 21b. This is more conducive to the deformation of the sub-shoulder 21b and the first end iron core block 32, further reducing the risk of deformation and skew of the second central shaft 12b, and further improving the coaxiality of the central shaft 21. This helps to reduce the full-stroke resistance of the motor and thus improve the working performance of the motor.

[0259] In some embodiments of the present invention, the support portion 33b extends circumferentially along the first end core block 32b, and the shoulder 20b is arranged circumferentially along the first central shaft 11b.

[0260] The support portion 33b extends circumferentially along the first end core block 32. The support portion 33b can be arc-shaped, meaning it is formed on a portion of the circumferential direction of the first end core block 32. Alternatively, it can be a closed loop, meaning it is formed along the entire circumferential direction of the first end core block 32. The shoulder 20b is arranged circumferentially along the first central shaft 11b. As an example, when the shoulder 20b is arc-shaped, it extends circumferentially along the first central shaft 11b, forming a portion of the circumferential direction. As another example, when the shoulder 20b is a closed loop, it forms along the entire circumferential direction of the first central shaft 11b. As yet another example, when there are multiple shoulders 20b, they are arranged sequentially at intervals along the circumferential direction of the first central shaft 11b. By having the support portion 33b extend circumferentially along the first end core block 32 and the shoulder 20b arranged circumferentially along the first central axis 11b, it is beneficial to increase the contact area between the support portion 33b and the shoulder 20b, thereby making the contact between the support portion 33b and the shoulder 20b more reliable. In addition, it can make the first end core block 32 and the shoulder 20b bear force evenly, reducing the risk of damage to the first end core block 32 and the shoulder 20b due to concentrated force, and also reducing the risk of the first end core block 32 deflecting.

[0261] It should be noted that this application takes into account the actual assembly problems in the mass production of the second component 2. From the perspective of optimizing the overall coaxiality of the second component 2, without changing the overall stiffness distribution of the central shaft 21, the axial stiffness of the central shaft 21 is too strong and the coaxiality problem caused by the machining tilt of the shoulder 20b is optimized by designing the first end iron core block 32 and optimizing the thickness of the shoulder 20b, thereby suppressing the coaxiality difference of the central shaft 21.

[0262] Furthermore, by designing the individual first end core block 32, the thrust of the motor is maintained while the electromagnetic scheme of the motor core is changed, and the electromagnetic thrust fluctuation is optimized. This application, through the design of the first end core block 32 and the shoulder 20b, avoids weakening the channel wall on the central shaft 21 due to coaxiality suppression requirements, while ensuring the overall strength of the central shaft 21 and the core, preventing strength risks arising from the design of the clearance space 321b. In addition, the second component 2 of this application is easy to modify with molds, facilitating mass production.

[0263] In some embodiments, the air spring surrounds the housing 11 of the first component 1 and is sealed to the housing 11.

[0264] In some embodiments, referring to FIG2, the housing 11 is also provided with a communicating hole 11C. The communicating hole 11C communicates with the mounting cavity 11A and also communicates with the inner cavity 30A of the air spring.

[0265] In this way, the inner cavity 30A of the air spring can be connected to the mounting cavity 11A of the housing 11 through the connecting hole 11C. Thus, the gas filling the inner cavity 30A of the air spring can also enter the mounting cavity 11A of the housing 11 through the connecting hole 11C. Therefore, the inner cavity 30A of the air spring and the mounting cavity 11A together serve as the gas filling chamber, thereby increasing the volume of the gas filling chamber. During the extension and contraction of the air spring, the pressure change range of the gas is larger, which allows for better adjustment of the damping performance of the air spring and further improves the driving comfort of the vehicle 1000.

[0266] In some examples, the connecting hole 11C is located at the end of the housing 11 facing the tower top assembly 20. In this way, the connecting hole 11C can communicate with the cavity 3, thereby communicating with the inner cavity 30A of the air spring through the cavity 3, so as to avoid interference between the connection position of the air spring and the first assembly 1 and the connecting hole 11C.

[0267] In some embodiments, referring to FIG2, the mounting cavity 11A of the housing 11 has a first opening. The first opening is located at the end of the housing 11 opposite to the tower top assembly 20, that is, the first opening is disposed opposite to the mounting hole 11B.

[0268] The first component 1 also includes an end cap 13. The end cap 13 covers the first opening and is connected to the housing 11. When the tower top component 20 is connected to the vehicle body 200, the end cap 13 is connected to the wheel 100. This application provides an illustrative example with the tower top component 20 connected to the vehicle body 200 and the end cap 13 connected to the wheel 100.

[0269] In some examples, the end cap 13 is connected to the housing 11 by fasteners such as bolts and screws. In other examples, the end cap 13 and the housing 11 may also be connected by snap-fit, welding, or other methods.

[0270] The housing 11, end cap 13 and first sealing structure 14 form the first component 1.

[0271] This application illustrates by way of example the connection between the end cap 13 and the housing 11 via fasteners.

[0272] A first gap 16 is formed between the end cap 13 and the housing 11. Specifically, after the inner cavity 30A of the air spring 30 is connected to the mounting cavity 11A of the housing 11 through the connecting hole 11C, the gas in the inner cavity 30A of the air spring 30 can enter the mounting cavity 11A through the connecting hole 11C, thereby causing a significant increase in the air pressure in the mounting cavity 11A of the housing 11, with the maximum air pressure reaching 2MPa.

[0273] After the housing 11 and end cover 13 are fastened together with fasteners, under ideal conditions (i.e., according to theoretical design requirements), the contact surfaces of the housing 11 and end cover 13 are both flat, and they can fit tightly together without gaps, meaning no airflow channel is formed between the contact surfaces of the housing 11 and end cover 13. However, in actual manufacturing, there are manufacturing errors, which may result in the contact surfaces of the housing 11 and end cover 13 not being completely smooth. Therefore, even after the contact surfaces of the housing 11 and end cover 13 are fitted together, gaps may still exist between them, forming airflow channels. Consequently, the gas entering the mounting cavity 11A of the housing 11 from the inner cavity 30A of the air spring 30 will leak from the gap between the housing 11 and end cover 13, thus affecting the damping performance of the air spring 30.

[0274] Based on this, please refer to Figure 3, which is an enlarged structural schematic diagram of the connection position between the housing 11 and the end cover 13 of the motor 10 in the suspension system 300 shown in Figure 2. The first component 1 also includes a first sealing structure 14. The first sealing structure 14 is used to block the fluid communication between the mounting cavity 11A and the external space through the first gap 16.

[0275] By blocking the fluid communication between the mounting cavity 11A and the external space through the first gap 16 by the first sealing structure 14, the gas entering the mounting cavity 11A of the housing 11 from the inner cavity 30A of the air spring 30 can be prevented from leaking out through the first gap 16 between the housing 11 and the end cover 13, so as to ensure the gas pressure in the air spring 30, ensure the damping performance of the air spring 30, and improve the reliability of the suspension system 300.

[0276] Furthermore, the first sealing structure 14 blocks the fluid communication between the mounting cavity 11A and the external space through the first gap 16, and also prevents external impurities from entering the mounting cavity 11A of the housing 11 from the gap between the housing 11 and the end cover 13, thereby affecting the components in the mounting cavity 11A, such as the winding structure, so as to ensure the working performance of the first component 1, thereby ensuring the working performance of the motor 10 and improving the reliability of the suspension system 300.

[0277] In some embodiments, the second component 2 is disposed in the mounting cavity 11A and can move relative to the housing 11 in a first direction within the mounting cavity 11A; the housing 11 has a cylindrical structure, and in the first direction, one of the housing 11 and the end cover 13 includes a first end face 16A and the other includes a second end face 16B, and a first gap 16 is provided between the first end face 16A and the second end face 16B, the first gap 16 connecting the mounting cavity 11A and the external space.

[0278] Since the gas in the inner cavity 30A of the air spring 30 enters the mounting cavity 11A of the housing 11, the gas pressure in the mounting cavity 11A can reach a maximum of 2MPa, which is a high gas pressure. Therefore, the sealing requirements between the housing 11 and the end cover 13 are also high, that is, the sealing requirements between the first end face 16A and the second end face 16B are high. Conventional sealing structures may not be able to meet the sealing requirements between the housing 11 and the end cover 13.

[0279] Based on this, in some embodiments, please refer to Figure 4, which is a schematic diagram of the first sealing structure 14 in the motor 10 shown in Figure 3. The first sealing structure 14 can be a first sealing gasket, which is disposed between the housing 11 and the end cover 13, that is, within the first gap. The first sealing gasket is used to seal the gap between the end cover 13 and the housing 11.

[0280] Compared to conventional O-rings, the first sealing gasket has a sheet-like structure. After the first sealing gasket is installed between the housing 11 and the end cover 13, the contact area between the first sealing gasket and the housing 11, as well as the contact area between the first sealing gasket and the end cover 13, are both larger, thereby improving the sealing effect and preventing gas leakage.

[0281] Furthermore, compared to an O-ring, the first sealing gasket has a relatively smaller thickness in the first direction. This reduces the space occupied by the first sealing gasket in the first direction, thereby facilitating the miniaturization of the suspension system 300. The first direction is aligned with the axial direction of the central axis 21. The first direction is perpendicular to the plane containing the first opening.

[0282] Furthermore, there is no need to cut grooves on the end cap 13 or the housing 11 to accommodate part of the first sealing structure 14 in the groove, thereby reducing the space occupied by the first sealing structure 14 in the first direction, which facilitates the processing of the housing 11 and the end cap 13, as well as the assembly of the first sealing structure 14.

[0283] When the end cover 13 and the housing 11 are fixed by fasteners, the end cover 13 and the housing 11 can compress the first sealing structure 14, thereby deforming the first sealing structure 14 and sealing the gap between the end cover 13 and the housing 11.

[0284] In some embodiments, the first sealing structure 14 is a first metal sealing structure. For example, the first sealing structure 14 can be made of metal materials such as copper, aluminum, or iron. The first metal sealing structure has good deformation uniformity. When the end cover 13 and the housing 11 compress the first metal sealing structure, even if the force on different positions of the first metal sealing structure is uneven, the degree of deformation of each part of the first metal sealing structure is small, thereby ensuring good sealing at all positions of the first metal sealing structure and improving the sealing performance between the end cover 13 and the housing 11.

[0285] In some embodiments, the first sealing structure 14 is an annular structure, meaning the first sealing structure 14 surrounds the first opening.

[0286] In some embodiments, please refer to FIG5, which is a cross-sectional view of the first sealing structure 14 shown in FIG4. The first sealing structure 14 includes an integrally connected first sealing gasket 141A and a first rib 141B. In a first direction, the first rib 141B partially abuts against the first end face 16A, and the portion of the first rib 141B abutting against the first end face 16A protrudes beyond the first surface of the first sealing gasket 141A. The second surface of the first sealing gasket 141A at least partially abuts against the second end face 16B. The first surface and the second surface of the first sealing gasket 141A are disposed opposite to each other in the first direction.

[0287] The first rib 141B is disposed on the first surface and surrounds the first opening.

[0288] With the first rib 141B provided, when the end cover 13 and the housing 11 squeeze the first sealing structure 14, the first rib 141B can contact the end cover 13 or the housing 11 and be squeezed and deformed. As a result, after the first rib 141B is deformed, the first sealing structure 14 fits more tightly with the end cover 13 and with the housing 11, thereby improving the sealing effect.

[0289] In some embodiments, the first surface portion of the first sealing gasket 141A abuts against the first end face 16A. In this way, after the first rib 141B deforms, the first rib 141B fits tightly against the first end face 16A, and the first surface of the first sealing gasket 141A also abuts against the first end face 16A. That is, the first surface fits tightly against the first end face 16A, thereby increasing the contact area between the first end face 16A and the first sealing structure 14 and improving the sealing effect.

[0290] In some embodiments, in a second direction (i.e., radially from the central axis), the first rib 141B is located on one side of the first sealing gasket 141A, and the second direction is perpendicular to the first direction. That is, the first rib 141B is connected to the outer edge or inner edge of the first sealing gasket 141A.

[0291] Thus, when the first rib 141B is squeezed, only the side facing the first sealing pad 141A will be resisted by the first sealing pad 141A, while the other side will not be resisted, which makes it easier for the first rib 141B to deform and improves the sealing effect of the first sealing structure 14.

[0292] In some embodiments, the first sealing gasket 141A includes a first edge portion and a second edge portion. The first edge portion may surround the second edge portion. That is, the first sealing gasket 141A has an annular structure, the first edge portion is the outer edge of the first sealing gasket 141A, and the second edge portion is the inner edge of the first sealing gasket 141A.

[0293] The first rib 141B is located between the first edge portion and the second edge portion. That is, the first rib 141B can be located in the middle of the first sealing gasket 141A.

[0294] In this way, after the first rib 141B is squeezed and deformed, the sealing position of the first rib 141B is also relatively closer to the middle position of the first end face 16A and the second end face 16B, which can increase the sealing effect.

[0295] In some examples, in the second direction, the size of the first edge portion is equal to the size of the second edge portion, and the second direction is perpendicular to the first direction. That is, in the second direction, the portion of the first sealing gasket 141A located on one side of the first rib 141B has the same size as the portion located on the other side of the first rib 141B. In other words, the first rib 141B is located at the exact center of the first sealing gasket 141A.

[0296] In some embodiments, referring to FIG5, the first sealing structure 14 further includes a first recess 141C, which extends from the second surface into the first rib 141B and surrounds the first opening. That is, the first recess 141C is recessed from the second surface of the first sealing gasket 141A toward the first rib 141B and extends along its recessing direction into the interior of the first rib 141B.

[0297] In this way, by setting the first recess 141C, the wall thickness of the first rib 141B can be reduced, so that when the end cover 13 and the housing 11 squeeze the first rib 141B, the first rib 141B is easier to deform, thereby further improving the sealing effect of the first sealing structure 14 on the gap between the end cover 13 and the housing 11.

[0298] Furthermore, by setting the first recess 141C, the deformation of the first rib 141B when it is squeezed will be greater, so that after the first sealing structure 14 is installed between the end cover 13 and the housing 11, the height of the first rib 141B after deformation in the first direction is close to the thickness of the first sealing gasket 141A, thereby reducing the space occupied by the first gasket in the first direction, so as to facilitate the miniaturization of the suspension system 300.

[0299] In some embodiments, the first sealing structure 14 further includes a first flexible member that at least partially covers the surface of the first rib 141B. Exemplarily, the first flexible member may be a rubber sheet, a latex sheet, a silicone sheet, etc.

[0300] By covering at least part of the surface of the first rib 141B with a first flexible element, after the first rib 141B is squeezed and deformed, the first flexible element will also be squeezed and deformed, and the deformed first flexible element can fit more tightly with the end cover 13 or the housing 11, thereby further improving the sealing effect of the first sealing structure 14 on the gap between the end cover 13 and the housing 11.

[0301] In some embodiments, the first sealing structure 14 further includes a second flexible member that at least partially covers the inner wall surface of the first recess 141C. Exemplarily, the second flexible member may be a rubber sheet, a latex sheet, a silicone sheet, etc.

[0302] By covering at least part of the inner wall surface of the first recess 141C with a second flexible element, after the first rib 141B is squeezed and deformed, the second flexible element will also be squeezed and deformed and squeezed out from the first recess 141C, so that the deformed second flexible element fits more tightly with the end cover 13 or the housing 11, thereby further improving the sealing effect of the first sealing structure 14 on the gap between the end cover 13 and the housing 11.

[0303] In some embodiments, the first flexible member covers the surface of the first rib 141B, and the second flexible member covers the inner wall surface of the first recess 141C. Thus, after the first rib 141B is compressed and deformed, one of the first and second flexible members can fit tightly against the housing 11, and the other of the first and second flexible members can fit tightly against the end cap 13, thereby further improving the sealing effect of the first sealing structure 14 on the gap between the end cap 13 and the housing 11.

[0304] In some embodiments, please refer to FIG6, which is another enlarged structural schematic diagram of the connection position between the housing 11 and the end cover 13 of the motor 10 in the suspension system 300 shown in FIG2. The first sealing structure 14 further includes at least one first sealing ring 142, which is disposed in the first gap, that is, between the housing 11 and the end cover 13.

[0305] By setting the first sealing ring 142, after the first sealing ring 142 is installed between the end cover 13 and the housing 11, the end cover 13 and the housing 11 can be squeezed when they are fixed by fasteners, so as to deform the first sealing ring 142 and seal the gap between the end cover 13 and the housing 11.

[0306] The number of first sealing rings 142 can be one or more. When there are multiple first sealing rings 142, they are sequentially fitted along the radial direction of the central axis 21, for example, the multiple first sealing rings 142 are arranged in concentric circles. Multiple first sealing rings 142 can provide multiple seals for the gap between the end cover 13 and the housing 11, thereby improving the sealing effect.

[0307] In some embodiments, referring to FIG6, to reduce the space occupied by the first sealing ring 142 in the first direction, a first receiving groove 131 can be provided on the end cover 13 and / or the housing 11, the first receiving groove 131 surrounding the first opening. A portion of the first sealing ring 142 is disposed within the first receiving groove 131 to reduce the space occupied by the first sealing ring 142 in the first direction. Furthermore, the first receiving groove 131 can also limit the position of the first sealing ring 142 to ensure its sealing effect.

[0308] In some embodiments, referring to FIG2, the first component 1 further includes a guide 15, which is located within the mounting cavity 11A and fixedly connected to the end cap 13. The guide 15 is adapted to cooperate with the second component 2 for guidance. Specifically, the guide 15 cooperates with the central axis 21 of the second component 2 for guidance.

[0309] By guiding the second component 2 in conjunction with the guide component 15, the relative movement of the second component 2 and the first component 1 can be made more stable, thereby improving the stability of the suspension system 300.

[0310] In some embodiments, referring to FIG2, the central shaft 21 is provided with a wiring channel 21C. The lead wires of the coil 22 are led out to the outside of the housing 11 through the wiring channel 21C. The lead wires are used to connect an external power supply or a motor controller to energize the coil 22 and control its operation. The lead wires may include signal lines.

[0311] Since the coil 22 is located inside the mounting cavity 11A, the wiring channel 21C needs to be connected to the mounting cavity 11A so that the lead wire of the coil 22 can be led out to the outside of the housing 11 through the wiring channel 21C.

[0312] Based on this, to prevent gas in the inner cavity 30A of the air spring and the mounting cavity 11A from leaking through the wiring channel 21C, a seal can be provided inside the wiring channel 21C. The seal is used to seal the gap between the lead wire and the inner wall of the wiring channel 21C.

[0313] For example, the sealant can be a sealant. By injecting sealant into the wiring channel 21C, the gap between the lead wire and the inner wall of the wiring channel 21C can be sealed. Alternatively, the sealant can be a rubber plug, which is secured within the wiring channel 21C, with the lead wire passing through a through-hole in the rubber plug. The lead wire and the inner wall of the through-hole are press-fitted, thereby sealing the gap between the lead wire and the inner wall of the wiring channel 21C.

[0314] In some embodiments, the guide 15 includes a base 151 and a guide rod 152 connected to the base 151. The base 151 is fixedly connected to the end cap 13, and the guide rod 152 is adapted to cooperate with the second component 2 for guidance.

[0315] For example, the central shaft 21 is provided with a guide hole. The guide hole extends axially along the central shaft 21, and the guide member 15 is accommodated in the guide hole. When the second component 2 and the first component 1 move relative to each other, the guide rod 152 moves in the guide hole so as to guide the central shaft 21 and the housing 11 through the cooperation of the guide rod 152 with the central shaft 21, thereby guiding the second component 2 and the first component 1 to improve the stability and smoothness of the relative movement of the second component 2 and the first component 1.

[0316] For example, the guide member 15 can be a rod-shaped structure, a plate-shaped structure, an irregular structure, etc., which will not be described in detail here.

[0317] In some embodiments, please refer to Figures 2 and 7. Figure 7 is another enlarged structural schematic diagram of the connection position between the housing 11 of the motor 10 and the end cover 13 in the suspension system 300 shown in Figure 2. The end cover 13 includes a main body 132 and a limiting part 133. The limiting part 133 is connected to the side of the main body 132 facing the housing 11 and surrounds the base 151, which is fixedly connected to the main body 132.

[0318] By using the limiting part 133 to surround the base 151, when the guide 15 is connected to the end cover 13, the limiting part can position the guide 15, thereby facilitating the connection between the guide 15 and the end cover 13.

[0319] In some examples, the limiting part 133 is an annular protrusion.

[0320] The limiting part 133 can be connected to the housing 11 by fasteners. In some examples, the first sealing structure 14 can be provided between the limiting part 133 and the housing 11. In some examples, the first sealing ring 142 can be provided between the limiting part 133 and the housing 11.

[0321] In some embodiments, referring to FIG7, the first sealing structure 14 further includes at least one second sealing ring 143. The second sealing ring 143 is disposed between the inner wall surface of the mounting cavity 11A and the base 151. And / or, the second sealing ring 143 is disposed between the limiting portion 133 and the base 151.

[0322] In other words, at least one second sealing ring 143 can be provided between the inner wall surface of the mounting cavity 11A and the base 151. At least one second sealing ring 143 can also be provided between the limiting part 133 and the base 151. Alternatively, the second sealing ring 143 can be provided simultaneously between the inner wall surface of the mounting cavity 11A and the base 151, and between the limiting part 133 and the base 151.

[0323] By providing a second sealing ring 143 between the inner wall of the mounting cavity 11A and the base 151, and / or between the limiting part 133 and the base 151, the gap between the end cover 13 and the housing 11 can also be sealed to prevent external impurities from entering the mounting cavity 11A of the housing 11, and to prevent the gas in the inner cavity 30A of the air spring and the mounting cavity 11A from leaking from the gap between the end cover 13 and the housing 11.

[0324] Furthermore, providing a second sealing ring 143 between the inner wall of the mounting cavity 11A and the base 151, and / or between the limiting part 133 and the base 151, can reduce the space occupied by the second sealing ring 143 in the first direction.

[0325] However, providing a second sealing ring 143 between the inner wall of the mounting cavity 11A and the base 151, and / or between the limiting part 133 and the base 151, would result in the second sealing ring 143 occupying a large space in the radial direction of the central axis 21. Based on this, referring to Figure 7, a second receiving groove 151A can be provided on the base 151, extending circumferentially along the central axis 21, with a portion of the second sealing ring 143 disposed within the second receiving groove 151A, thereby reducing the space occupied by the second sealing ring 143 in the radial direction of the central axis 21.

[0326] Alternatively, a second receiving groove 151A can be provided on the inner circumferential surface of the housing 11 and / or the inner circumferential surface of the limiting part 133, and a portion of the second sealing ring 143 can be placed in the second receiving groove 151A to reduce the space occupied by the second sealing ring 143 in the radial direction of the central shaft 21.

[0327] In some embodiments, along the first direction, the two side surfaces of the base 151 are respectively located on both sides of the first gap; the first sealing structure 14 further includes at least two second sealing rings 143, and the second sealing rings 143 are provided between the inner wall surface of the mounting cavity 11A and the base 151, and between the limiting part 133 and the base 151.

[0328] In this way, the inner wall of the mounting cavity 11A and the base 151, as well as the limiting part 133 and the base 151, can be sealed, thereby further improving the sealing effect.

[0329] In some embodiments, referring to FIG2, the motor 10 further includes a sensing component 4. The sensing component 4 is disposed on the first component 1 and / or the second component 2, and is adapted to generate a displacement signal characterizing the relative position of the first component 1 and the second component 2. The sensing component 4 is used to detect the relative displacement between the second component 2 and the first component 1.

[0330] In some embodiments, the sensing component includes a first part and a second part, one of the first part and the second part being disposed in the first component 1, and the other of the first part and the second part being disposed in the second component 2; the first part and the second part cooperate to detect the relative displacement between the second component 2 and the first component.

[0331] In some embodiments, the first part includes a sensing element 41, and the second part includes a signaling element 42. One of the sensing element 41 and the signaling element 42 is disposed in the first component 1, and the other of the sensing element 41 and the signaling element 42 is disposed in the second component 2. The sensing element 41 and the signaling element 42 cooperate to detect the relative displacement between the second component 2 and the first component 1.

[0332] For example, the signal element 42 can be a magnetic grating ruler, and the sensing element 41 can be a magnetic head. The magnetic head reads the change in the magnetic field on the magnetic grating ruler to detect the relative displacement between the second component 2 and the first component 1. That is, the sensing component 4 is a magnetic grating ruler displacement sensing component 4.

[0333] For example, the signal element 42 can be a grating ruler, and the sensing element 41 can read the change of light signal in the grating ruler to detect the relative displacement of the second component 2 and the first component 1, that is, the sensing component 4 is a grating ruler displacement sensing component 4.

[0334] This application is illustrated by way of example, with the sensing element 41 disposed in the first component 1 and the signal element 42 disposed in the second component 2.

[0335] In some embodiments, the sensor 41 is connected to the side of the housing 11 opposite to the end cover 13. The signal element 42 is connected to the peripheral wall of the central shaft 21. The sensor 41 and the housing 11 can be connected by fasteners such as bolts and screws, or by snap-fitting. The signal element 42 can be connected to the central shaft 21 by snap-fitting, screwing, or other methods.

[0336] In some embodiments, please continue to refer to Figures 2, 8, 9 and 10. Figure 8 is a schematic diagram of the connection relationship between the sensing component 4 of the motor 10 and the housing 11 in the suspension system 300 shown in Figure 2. Figure 9 is an enlarged structural schematic diagram of the connection position between the sensing component 4 and the housing 11 shown in Figure 8. Figure 10 is a schematic diagram of the relationship between the pressure plate and the second sealing structure at the connection position between the sensing component 4 and the housing 11 shown in Figure 8.

[0337] The sensor 41 needs to be connected to an external power supply or controller via connecting wires. These connecting wires include signal lines. To facilitate the installation of the connecting wires, the housing 11 has a through-hole 11D. The through-hole 11D extends through the housing 11 in a first direction.

[0338] The sensor 41 is connected to the side of the housing 11 opposite to the end cap 13 of the first component 1, and covers the wire outlet 11D. The connecting wire of the sensor 41 is led out to the outside of the housing 11 through the wire outlet 11D.

[0339] The sensor 41's connecting wire is provided through the outlet hole 11D along the first direction through the housing 11, so that the connecting wire of the sensor 41 passes through the outlet hole 11D and is led out to the outside of the housing 11. The outlet hole 11D can protect the connecting wire and prevent interference between the outlet hole 11D and the air spring.

[0340] Since the air spring surrounds the first component 1, and the inner cavity 30A of the air spring, together with the support member 20B, the second component 2, the first component 1, and the fixed base 20A, forms a cavity 3 that is connected, the gap between the sensing element 41 and the housing 11 is connected to the inner cavity 30A of the air spring. Thus, the gas inside the inner cavity 30A of the air spring can leak through the gap between the sensing element 41 and the housing 11 to the outlet hole 11D, thereby causing the gas inside the inner cavity 30A of the air spring to leak out.

[0341] Based on this, a second gap 17 is formed between the sensing element 41 and the housing 11. The second gap 17 connects the mounting cavity 11A of the housing 11 and the external space, and also connects the air spring 30 and the external space.

[0342] Referring to Figures 8 and 9, the motor 10 also includes a second sealing structure 5. The second sealing structure 5 is used to block fluid communication between the mounting cavity 11A and the external space, and between the air spring 30 and the external space through the second gap 17.

[0343] By setting the second sealing structure 5, the fluid communication between the mounting cavity 11A and the external space, as well as between the air spring 30 and the external space, through the second gap 17 can be blocked, so as to prevent the gas in the inner cavity 30A of the air spring from leaking from the gap between the sensing element 41 and the housing 11, thereby further ensuring the damping performance of the air spring.

[0344] In some embodiments, the second sealing structure 5 is disposed between the sensor 41 and the housing 11 and surrounds the wire outlet hole 11D; in the first direction, one of the sensor 41 and the housing 11 includes a third end face 17A and the other includes a fourth end face 17B, and a second gap 17 is provided between the third end face 17A and the fourth end face 17B.

[0345] In this way, by placing the second sealing structure 5 between the sensor 41 and the housing 11 and surrounding the wire outlet hole 11D, the second sealing structure 5 can be deformed by the sensor 41 and the housing 11, thus achieving the sealing of the second gap 17.

[0346] In some embodiments, the second sealing structure 5 includes a second sealing gasket. The second sealing structure is used to seal the gap between the sensor 41 and the housing 11.

[0347] Compared to O-rings, the second gasket has a relatively smaller thickness in the first direction. This reduces the space occupied by the second gasket in the first direction, thus facilitating the miniaturization of the suspension system 300.

[0348] Furthermore, there is no need to cut grooves on the sensing element 41 or the housing 11 to accommodate part of the second sealing structure in the groove, thereby reducing the space occupied by the second sealing structure in the first direction, which facilitates the processing of the housing 11 and the sensing element 41, as well as the assembly of the second sealing structure.

[0349] When the sensor 41 and the housing 11 are fixed by fasteners, the sensor 41 and the housing 11 can compress the second sealing structure to deform the second sealing structure, thereby sealing the gap between the sensor 41 and the housing 11.

[0350] In addition, by setting the second sealing structure, the connecting wire of the sensing element 41 is not limited to a circular wire, but can also be arranged in a flat wire. In this way, not only can the circumferential space be fully utilized, but the radial space can also be reduced.

[0351] In some embodiments, the second sealing structure is a second metal sealing structure. For example, the second sealing structure can be made of materials such as copper, aluminum, or iron. The second metal sealing structure has good deformation uniformity. When the sensor 41 and the housing 11 compress the second metal sealing structure, even if the force is uneven at different positions of the second metal sealing structure, the degree of deformation of each part of the second metal sealing structure is small, thereby ensuring good sealing at all positions of the second metal sealing structure and improving the sealing performance between the sensor 41 and the housing 11.

[0352] In some embodiments, the second sealing structure includes a second sealing gasket and a second rib.

[0353] In the first direction, the second rib abuts against the third end face 17A, and the portion of the second rib abutting against the third end face 17A protrudes from the third surface of the second sealing gasket. The fourth surface of the second sealing gasket at least partially abuts against the fourth end face. The third surface of the second sealing gasket and the fourth surface of the second sealing gasket are arranged opposite to each other in the first direction. The second rib surrounds the wire outlet hole 11D.

[0354] By setting the second rib, when the sensor 41 and the housing 11 squeeze the second sealing structure, the second rib can come into contact with the sensor 41 or the housing 11 and be squeezed and deformed. As a result, after the second rib is deformed, the second sealing structure fits more tightly with the sensor 41 and with the housing 11, thereby improving the sealing effect.

[0355] In some embodiments, the second sealing structure further includes a second recess, which extends from the fourth surface into the second rib and surrounds the outlet hole 11D. That is, the second recess extends from the fourth surface toward the second rib and extends along its recessed direction into the interior of the second rib.

[0356] In this way, by setting the second recess, the wall thickness of the second rib can be reduced, so that when the sensor 41 and the housing 11 squeeze the second rib, the second rib is easier to deform, thereby further improving the sealing effect of the second sealing structure on the gap between the sensor 41 and the housing 11.

[0357] Furthermore, by setting the second recess, the deformation of the second rib when it is squeezed will be greater, so that after the second sealing structure is installed between the sensor 41 and the housing 11, the height of the second rib after deformation in the first direction is close to the thickness of the second sealing gasket, thereby reducing the space occupied by the second gasket in the first direction, so as to facilitate the miniaturization of the suspension system 300.

[0358] In some embodiments, the second sealing structure 5 further includes a third flexible member that at least partially covers the surface of the second rib. Exemplarily, the third flexible member may be a rubber sheet, a latex sheet, a silicone sheet, etc.

[0359] By covering at least part of the surface of the second rib with a third flexible element, the third flexible element will also be deformed after the second rib is squeezed and deformed. The deformed third flexible element can fit more tightly with the sensor 41 or the housing 11, thereby further improving the sealing effect of the second sealing structure on the gap between the sensor 41 and the housing 11.

[0360] In some embodiments, the second sealing structure 5 further includes a fourth flexible member that at least partially covers the inner wall surface of the second recess. Exemplarily, the fourth flexible member may be a rubber sheet, a latex sheet, a silicone sheet, etc.

[0361] By covering at least part of the inner wall surface of the second recess with a fourth flexible element, after the second rib is squeezed and deformed, the fourth flexible element will also be squeezed and deformed and squeezed out from the second recess, so that the deformed fourth flexible element fits more tightly with the sensor 41 or the housing 11, thereby further improving the sealing effect of the second sealing structure on the gap between the sensor 41 and the housing 11.

[0362] In some embodiments, the third flexible member covers the surface of the second rib, and the fourth flexible member covers the inner wall surface of the second recess. Thus, after the second rib is compressed and deformed, one of the third and fourth flexible members can fit tightly against the housing 11, and the other of the third and fourth flexible members can fit tightly against the sensing element 41, thereby further improving the sealing effect of the second sealing structure on the gap between the sensing element 41 and the housing 11.

[0363] In some embodiments, please refer to FIG11, which is a structural schematic diagram of the sensor element 41 of the sensing component 4 of the motor 10 in the suspension system 300 shown in FIG2 when the housing 11 is sealed by a third sealing ring. The second sealing structure 5 includes at least one third sealing ring 51.

[0364] By setting the third sealing ring 51, after the sensor 41 and the housing 11 are connected by fasteners, the sensor 41 and the housing 11 can squeeze the third sealing ring 51 to deform it, thereby sealing the gap between the sensor 41 and the housing 11.

[0365] The number of third sealing rings 51 can be one or more. When there are multiple third sealing rings 51, they are sequentially fitted along the radial direction of the outlet hole 11D, for example, the multiple third sealing rings 51 are arranged in concentric circles. Multiple third sealing rings 51 can provide multiple seals for the gap between the sensor 41 and the housing 11, thereby improving the sealing effect.

[0366] In some embodiments, to reduce the space occupied by the third sealing ring 51 in the first direction, a third receiving groove 11E can be provided on the sensing element 41 and / or the housing 11, the third receiving groove 11E surrounding the wire outlet hole 11D. A portion of the third sealing ring 51 is disposed within the third receiving groove 11E to reduce the space occupied by the third sealing ring 51 in the first direction. Furthermore, the third receiving groove 11E can also limit the position of the third sealing ring 51 to ensure its sealing effect.

[0367] In some embodiments, the housing of the sensing element 41 of the sensing assembly 4 is typically manufactured using an injection molding process. Therefore, the structural strength of the sensing element 41 is relatively poor. When the second sealing structure 5 is compressed by the sensing element 41 and the housing 11, the deformation of the second sealing structure 5 may be poor, affecting the sealing effect of the second sealing structure 5.

[0368] Based on this, please refer to Figures 9, 10, and 12. Figure 12 is a top view showing the connection relationship between the pressure plate of the sensing element 41 of the sensing component 4 in the suspension system 300 shown in Figure 2 and the housing 11. The sensing element 41 includes a sensing element body 411 and a pressure plate 412. The pressure plate 412 is fixed to the sensing element body 411 and is located between the sensing element body 411 and the second sealing structure.

[0369] The pressure plate 412 increases the structural strength of the sensor 41. Furthermore, the pressure plate 412 is located between the sensor body 411 and the second sealing structure. When the sensor 41 and the housing 11 compress the second sealing structure 5, the compression is achieved through the pressure plate 412 and the housing 11, resulting in better deformation of the second sealing structure 5 and improved sealing performance.

[0370] In some embodiments, the pressure plate 412 is a metal sheet. For example, the pressure plate 412 is a copper sheet, an aluminum sheet, an iron sheet, etc. By making the pressure plate 412 a metal sheet, the deformation effect of the second sealing structure 5 can be further improved when the pressure plate 412 and the housing 11 compress the second sealing structure 5, thereby improving the sealing performance of the second sealing structure 5.

[0371] In some examples, the pressure plate 412 is arranged around the outlet hole 11D. In this way, the pressure plate 412 can surround the connecting wire of the sensor 41 to allow the connecting wire to be led out through the outlet hole 11D to the outside of the housing 11.

[0372] In some embodiments, referring to FIG42, the motor 10 includes a first component 1, a second component 2, a sensing component 4, and a shielding component 50c. The first component 1 includes a magnetic element 12; the second component 2 includes a coil 22, which generates a magnetic field when energized to cooperate with the magnetic element 12, so that the first component 1 and the second component 2 move relative to each other along the axial direction of the motor 10; the sensing component 4 is disposed on the first component 1 and / or the second component 2, and is adapted to generate a displacement signal characterizing the relative position of the first component 1 and the second component 2; the shielding component 50c is disposed on the first component 1 and / or the second component 2, and is adapted to reduce the influence of the magnetic field generated by the coil 22 after current is applied on the displacement signal.

[0373] In the technical solution of this application, the motor 10 includes a first component 1, a second component 2, a sensing component 4, and a shielding component 50c. The first component 1 and the second component 2 are adapted to move relative to each other along the axial direction of the motor 10. The sensing component 4 is adapted to generate a displacement signal characterizing the relative position of the first component 1 and the second component 2. The shielding component 50c is adapted to reduce the influence of the displacement signal of the sensing component 4. By providing the shielding component 50c in the motor 10, the shielding component 50c can shield the interference signals generated by the first component 1 and the second component 2, avoiding interference from the first component 1 and the second component 2 to the sensing component 4, so that the sensing component 4 can accurately measure the relative displacement signal of the first component 1 and the second component 2, thereby improving the accuracy of the motor 10.

[0374] Specifically, in this application, motor 10 is a linear motor.

[0375] In some embodiments, a bearing is provided between the first component and the second component, the bearing being fixed to one of the first and second components, and the other of the first and second components slidingly engaging with the bearing along a first direction. The bearing arrangement allows for smoother relative movement between the first and second components.

[0376] In some embodiments, referring to FIG42, the motor 10 includes a housing 11, a magnetic component 12, a coil 22, and a central shaft 21. The central shaft 21 is sleeved inside the housing 11. One of the magnetic component 12 and the coil 22 is located on the inner sidewall of the housing 11, and the other is located on the central shaft 21. The bearing includes a first bearing. A gap is formed between the first central shaft body 11b of the central shaft 21 and the housing 11. The first bearing is located within the gap. The first bearing can reduce the friction between the first component 1 and the second component 2. At the same time, placing the first bearing in the gap will increase the axial length of the motor 10 to a certain extent.

[0377] Furthermore, the housing 11 is provided with a mounting cavity, the central shaft 21 is located in the mounting cavity of the housing 11, the magnetic component 12 and the coil 22 are located in the mounting cavity, the coil 22 is sleeved on the central shaft 21, as the central shaft 21 moves, the magnetic component 12 is located on the housing 11, and a gap is formed between the coil 22 and the magnetic component 12 so that the central shaft 21 and the housing 11 can slide relative to each other, thereby realizing the movement of the motor 10.

[0378] Specifically, in this embodiment, the motor 10 is driven by electromagnetic force to achieve movement. When the coil 22 is energized, the magnetic field generated in the coil 22 interacts with the magnetic component 12 to generate a force that drives the housing 11 or the central shaft 21 to move, thereby realizing the movement of the motor 10.

[0379] In this embodiment, referring to Figures 42, 43, and 44, the first component 1 includes a housing 11 and a magnetic component 12. The magnetic component 12 is disposed inside the housing 11 and fixedly connected to the housing 11. More specifically, the magnetic component 12 is disposed on the inner sidewall of the housing 11. The second component 2 is movably disposed inside the housing 11 and can move along the axial direction of the motor 10. That is, the first component 1 is fixed, and the second component 2 moves along the axial direction of the motor 10. Specifically, the second component 2 includes a central shaft 21 and a coil 22. The central shaft 21 includes a first central shaft body 11b and a second central shaft body 12b connected together. The first central shaft body 11b extends out of or enters the housing 11 when the second component 2 moves relative to the first component 1. The second central shaft body 12b always moves inside the housing 11. The coil 22 is fixedly disposed on the second central shaft body 12b and is located in the housing 11.

[0380] Furthermore, in this embodiment, when the coil 22 is energized, the magnetic field generated interacts with the magnetic field of the magnetic component, causing the first component 1 and the second component 2 to move relative to each other along the axial direction of the motor; more specifically, when the coil 22 is energized, an air gap magnetic field is formed between the coil 22 and the magnetic component 12, and the change of the air gap magnetic field generates an electromagnetic force, thereby driving the first component 1 and the second component 2 to move relative to each other, thereby realizing the movement of the motor 10.

[0381] To detect the relative positional relationship between the first component 1 and the second component 2, in this embodiment, the motor 10 is further provided with a sensing component 4. The sensing component 4 includes a sensing element 41 and a signal element 42. The signal element 42 is used to detect and provide displacement information of the motor 10, and the sensing element 41 is used to collect information from the signal element 42 and generate displacement information. One of the sensing element 41 and the signal element 42 is located in the first component 1, and the other is located in the second component 2, depending on the actual situation.

[0382] It should be noted that when the coil 22 is energized, the coil 22 generates a radiated magnetic field based on the magnetic effect of the current. The electromagnetic field interferes with the sensing component 4, resulting in a large error in the detection result of the sensing component 4. In some embodiments, in order to improve the accuracy of the sensing component 4, a shielding component 50c is provided in the motor 10. The shielding component 50c can block the interference of the current magnetic field of the coil 22, thereby reducing the influence of the magnetic induction lines of the coil 22 on the displacement signal.

[0383] In some embodiments, the signal element 42 is disposed on the central shaft 21 and moves together with the central shaft 21. The sensing element 41 is disposed on the housing 11 and generates a displacement signal by detecting the position of the signal element 42, thereby obtaining the movement status of the motor 10.

[0384] As shown in Figure 46, the coil 22 is wound into a hollow disk shape. The coil 22 includes multiple coil sections 211c and connecting lines 212c. The multiple coil sections 211c are spaced apart along the axial direction of the motor 10, and adjacent coil sections 211c are connected by a connecting line 212c. More specifically, the multiple coil sections 211c are wrapped around the central shaft 21. When current passes through the coil sections 211c, a magnetic field is generated. The magnetic field cuts the magnetic induction lines of the magnetic component 12, thereby driving the central shaft 21 to move. When the multiple coil sections 211c are energized, a radiated magnetic field is also generated. The radiated magnetic field radiates on the central shaft 21 and the housing, thereby interfering with the sensing component 4, causing inaccurate position calculation of the sensing component 4, and thus affecting the stable operation of the motor 10.

[0385] It should be noted that the directions of the radiated magnetic field are not the same. Some of the radiated magnetic field radiates along the axial direction of the central axis 21, some radiates along the radial direction of the central axis 21, and some radiates along various angles.

[0386] In some embodiments, please refer to Figures 42 and 43, the shielding component 50c includes a first shield 51c, which is disposed between the sensing component 4 and the coil 22. The first shield 51c can block part of the radiated magnetic field and prevent the radiated magnetic field from radiating to the sensing component 4.

[0387] Please refer to Figures 42 and 43. The coil 22 is mounted on the central shaft 21, which is installed inside the housing 11. To ensure the travel of the central shaft 21, a certain space is reserved between the coil 22 and the end of the housing 11, allowing the central shaft 21 to move axially along the housing 11. During the movement of the central shaft 21, the radiated magnetic field can pass through the reserved space and interfere with the sensing component 4. Therefore, a first shield 51c is placed on the first component 1, located at the end of the coil 22 near the sensing component 4. The first shield 51c can shield the radiated magnetic field, preventing it from interfering with the sensing component 4 through the reserved space. More specifically, in the direction from the inside to the outside of the first component 1, the first shield 51c guides the magnetic induction lines generated by the coil 22, causing the direction of the magnetic induction lines to change and radiate away from the sensing component 4, thereby preventing interference from the radiated magnetic field.

[0388] In some embodiments, referring to FIG43, one end of the housing 11 is the output end of the motor 10, that is, one end of the central shaft 21 extends out of the housing 11 to form the output end of the motor 10. More specifically, the coil 22 is located in the mounting cavity of the housing 11, and the coil 22 moves within the housing 11 along with the central shaft 21. The first shield 51c is installed on the housing 11. The first shield 51c is used to guide the magnetic induction lines generated by the coil 22, so that the direction of the magnetic induction lines generated by the coil 22 is changed, radiating away from the sensing component 4, thereby avoiding interference of the radiated magnetic field with the sensing component 4.

[0389] It should be noted that the specific location of the first shielding member 51c is not limited. It can be set on the inner side of the housing 11 or on the outer side of the housing 11, depending on the actual situation. As a preferred embodiment, the first shielding member 51c is set on the inner side of the housing 11, which can effectively block the radiated magnetic field and prevent the emitted magnetic field from passing through the side wall of the housing 11, thereby affecting the sensing component 4.

[0390] In some embodiments, the motor 10 has a longest stroke and a shortest stroke. When the motor 10 is at its longest stroke, the portion of the central shaft 21 extending out of the housing 11 is at its longest, and at this time, the coil 22 is closest to the housing 11. Specifically, the coil 22 has a first end close to the sensing component 4 and a second end away from the sensing component 4. The housing 11 has a third end and a fourth end, with the third end being the output end. When the motor 10 is at its longest stroke, the third end is flush with the first end. To ensure a shielding effect, in this embodiment, the end of the first shield 51c close to the coil 22 extends at least to the third end. Further, to improve the shielding effect, the end of the first shield 51c close to the coil 22 extends beyond the third end.

[0391] Please refer to Figure 43. In some embodiments, the signal element 42 is disposed on the central shaft 21. As the central shaft 21 moves, the sensing element 41 is disposed on the housing 11 and is fixed relative to the housing 11.

[0392] In some embodiments, the sensor 41 is mounted on the outer side of the housing, and the first shield is mounted on the inner side of the housing. In other embodiments, the sensor 41 is mounted on the top surface of the housing 11 (i.e., the sensor 41 is mounted on the fourth end, that is, the sensor 41 is mounted on the side of the housing 11 opposite to the end cover 13), and the first shield 51c is mounted on the top of the inner side of the housing (i.e., the inner side of the fourth end). To ensure the stability of the connection, at least a portion of the sensor 41 is overlapped with at least a portion of the housing 11, thereby ensuring the stability of the connection of the sensor 41. In this embodiment, the sensor 41 has one end close to the coil 22 and one end away from the coil 22. The orthographic projection of the end of the sensor close to the coil 22 on the housing 11 is the first boundary line, and the end of the first shield 51c away from the coil 22 needs to be at least flush with the first boundary line, thereby achieving the purpose of shielding the radiated magnetic field. Further, to provide a shielding effect, the end of the first shield 51c away from the coil 22 extends to the fourth end.

[0393] Please refer to Figure 43. In this embodiment, the positional relationship of the coil 22, housing 11, first shield 51c, and sensor 41 is as follows: the coil 22 is disposed within the mounting cavity of the housing 11 and can move along the axial direction of the housing 11; the first shield 51c is disposed on the inner side of the housing 11; and the sensor 41 is disposed on the top surface of the housing 11. That is, the first shield 51c is located between the coil 22 and the sensor 41 in the axial direction of the motor 10.

[0394] In some embodiments, the radiated magnetic field may radiate radially along the motor 10, penetrate the sidewall of the first component 1, and spread to the sensing component 4, causing interference to the sensing component 4. For example, when the motor 10 is applied to some objects or machines, the radiated magnetic field radiates radially along the motor 10, penetrates the sidewall of the housing 11, radiates onto the machine, and is then reflected by the machine. Part of the radiated magnetic field may be reflected onto the sensing component 4, thereby affecting the sensing component 4. Specifically, referring to Figures 42 and 43, the shielding component 50c includes a second shield 52c, which is installed on the first component 1. The second shield 52c can guide and change the radiation direction of the radiated magnetic field, thereby avoiding interference with the sensing component 41.

[0395] Referring to Figure 43, in some embodiments, the second shield 52c is used to guide the magnetic induction lines of the coil 22 along the direction from the inner side of the first component 1 to the outer side of the first component 1.

[0396] Please continue to refer to Figure 43. In some embodiments, the first shield 51c and the second shield 52c cooperate to change the direction of the radiated magnetic field radiating toward the sensor 41. The direction of the radiated magnetic field radiating toward the sensor 41 is changed to a direction away from the sensor 41, as shown in Figure 43. When the radiated magnetic field comes into contact with the first shield 51c, the radiated magnetic field will change. When the radiated magnetic field comes into contact with the second shield 52c, the radiated magnetic field will change again. At this time, the radiated magnetic field is emitted in a direction away from the sensor 41, thereby avoiding interference of the radiated magnetic field with the sensor 41.

[0397] Please refer to Figure 43. In some embodiments, the second shielding element 52c is installed on the housing 11. It should be noted that a magnetic element 12 is provided inside the housing 11. The magnetic element 12 is fixedly installed inside the housing 11. The magnetic element 12 itself has a magnetic field. When the coil 22 is energized, it interacts with the magnetic field generated by the coil 22, so that the motor 10 can move. Therefore, in order to avoid the second shielding element 52c interfering with the magnetic element 12, the second shielding element 52c is installed on the outer side of the housing 11, and the magnetic element 12 is installed on the inner side of the housing 11.

[0398] In some embodiments, in order to improve the shielding effect and prevent the radiated magnetic field from radiating out from the connection position of the first shield 51c and the second shield 52c, in this embodiment, the first shield 51c and the second shield 52c are partially overlapped in the direction of movement of the motor 10. Specifically, the end of the second shield 52c near the output end is flush with the end of the first shield 51c near the output end.

[0399] Further, please continue to refer to Figure 43. A recessed groove 1121c is formed on the outer side of the housing 11, and the second shielding member 52c is filled in the recessed groove 1121c.

[0400] It should be noted that the length of the second shield 52c is not limited and can be set according to the actual situation. In this embodiment, the motor 10 has a longest stroke and a shortest stroke. During the longest stroke, the central shaft 21 moves away from the housing 11 until the coil 22 on the central shaft 21 abuts against the housing 11. At this time, the motor 10 has moved the longest stroke and the coil 22 is located at the position closest to the sensor 41. Therefore, the second shield 52c only needs to ensure that it can shield the radiated magnetic field when the motor 10 is in the longest stroke.

[0401] In this embodiment, during the active stroke of the motor 10, the length of the coil 22 is half the length of the housing 11. Therefore, when the coil 22 moves to its longest stroke, the length of the coil 22 is half the length of the housing 11, and the second shield 52c only needs to cover half of the housing 11. Specifically, the length of the second shield 52c is greater than the length of the coil 22.

[0402] Furthermore, the length of the second shielding component 52c is half the length of the housing 11. This arrangement ensures both shielding effectiveness and material savings. Of course, to guarantee shielding effectiveness, the second shielding component 52c can also completely cover the outer surface of the housing 11, meaning the length of the second shielding component 52c is the same as the length of the housing 11.

[0403] It should be noted that the sensing component 4 includes a sensing element 41 and a signal element 42. One of the sensing element 41 and the signal element 42 is located on the central shaft 21 and moves with the central shaft 21. The other is located on the housing 11. The specific arrangement is not limited and can be selected according to the actual situation.

[0404] In this embodiment, the sensor 41 is adapted to acquire the signal of the signal element 42 to generate a displacement signal. The sensor 41 is disposed on the central shaft 21 and moves together with the central shaft 21. Specifically, the sensor 41 is adapted to move between a first position away from the coil 22 and a second position close to the coil 22. When the sensor 41 is in the second position, the central shaft 21 moves to the longest stroke of the motor 10. At this time, the second shield 52c covers the coil 22 in the axial direction of the motor 10.

[0405] Furthermore, to ensure the shielding effect, the first shield 51c and the second shield 52c overlap axially in the motor 10. This arrangement prevents the radiated magnetic field from radiating out from the connection between the first shield 51c and the second shield 52c, thus avoiding interference with the sensor 41.

[0406] In some embodiments, the central shaft 21 includes a first central shaft body 11b and a second central shaft body 12b connected together. The second central shaft body 12b is disposed inside the housing 11. A coil 22 is disposed around the second central shaft body 12b and is fixedly connected to the second central shaft body 12b. The first central shaft body 11b extends out of the housing 11 and is used to connect to an external component to drive the external component to move. Specifically, a signal element 42 is disposed on the first central shaft body 11b.

[0407] Please refer to Figures 42, 44, and 46. When current flows through the coil section 211c, a magnetic field is generated. This magnetic field cuts the magnetic induction lines of the magnetic component 12, thereby driving the central shaft 21 to move. When multiple coil sections 211c are energized, a radiated magnetic field is also generated. This radiated magnetic field radiates on the central shaft 21 and the housing, thereby interfering with the sensing component 4, causing inaccurate position calculation of the sensing component 4, and thus affecting the stable operation of the motor 10. Some of the radiated magnetic field will affect the signal component 42 along the radiation of the central shaft 21. When the radiated magnetic field enters the first central shaft body 11b, it will interfere with the signal component 42 on the first central shaft body 11b, thereby affecting the operation of the sensing component 41. In this embodiment, the shielding component 50c includes a third shielding component 53c, which is disposed on the central shaft 21. The third shielding component 53c is adapted to guide the magnetic induction lines generated by the coil 22 along the axial direction of the second component 2, thereby preventing the radiated magnetic field from interfering with the sensing component 41.

[0408] Furthermore, in some embodiments, the third shield 53c is coaxially arranged with the coil 22. This arrangement allows for better axial guidance of the magnetic induction lines generated by the coil 22, thereby preventing interference from the radiated magnetic field to the sensor 41.

[0409] It should be noted that the connection method between coil 22 and central shaft 21 is not limited, as long as it can achieve fixation. Considering the issue of space utilization, in this embodiment, coil 22 and central shaft 21 are coaxially arranged. Furthermore, coil 22 is located on the second central shaft body 12b, and coil 22 surrounds the second central shaft body 12b.

[0410] It should be noted that the position of the third shielding component 53c is not limited and can be selected according to the actual situation. The third shielding component 53c is set on the inner side of the first central shaft 11b because the interference magnetic field would be guided to the sensing component 41 if it were on the outer side. Specifically, the signal component 42 is installed on the outer side of the first central shaft 11b, and the third shielding component 53c is installed on the inner side of the first central shaft 11b. This arrangement can save space and improve space utilization.

[0411] Optionally, to ensure shielding effectiveness, the third shield 53c overlaps with the signal element 42 in the radial direction of the second component 2. In this way, the third shield 53c can better guide the magnetic induction lines generated by the coil 22 in the axial direction, thereby avoiding interference of the radiated magnetic field with the sensing element 41.

[0412] It should be noted that the length of the third shielding member 53c is not limited, as long as it can cover the signal member 42. Specifically, taking the first central shaft 11b as an example, the end of the first central shaft 11b closer to the second central shaft 12b is the first end, and the end farther from the second central shaft 12b is the second end. In some embodiments, the end of the third shielding member 53c closer to the first end is flush with the end of the signal member 42 closer to the first end, and the end of the third shielding member 53c closer to the second end is flush with the end of the signal member 42 closer to the second end, that is, the length of the third shielding member 53c is the same as the length of the signal member 42, and the third shielding member 53c is completely aligned with the signal member 42.

[0413] In some embodiments, to ensure shielding effectiveness, the length of the third shielding member 53c is greater than the length of the signal member 42. Specifically, the end of the third shielding member 53c near the first end extends beyond the end of the signal member 42 near the first end, and the end of the third shielding member 53c near the second end is flush with the end of the signal member 42 near the second end. Alternatively, in some embodiments, the end of the third shielding member 53c near the first end extends beyond the end of the signal member 42 near the first end, and the end of the third shielding member 53c near the second end extends beyond the end of the signal member 42 near the second end. In other embodiments, the third shielding member 53c covers the entire inner wall of the first central shaft 11b.

[0414] It should be noted that the arrangement of the first shielding element 51c, the second shielding element 52c, and the third shielding element 53c is not limited, and can be selected according to the actual situation. In some embodiments, the first shielding element 51c, the second shielding element 52c, and the third shielding element 53c are all coating structures. The arrangement and forming method of the coating structure can refer to the conventional settings in the art, and will not be described in detail here.

[0415] Furthermore, the coating structure is formed by a spraying process. Specific operating procedures and precautions for the spraying process can be found in standard practices in this field and will not be elaborated upon here.

[0416] In some embodiments, the first shield 51c, the second shield 52c, and the third shield 53c are all magnetically conductive structures. These magnetically conductive structures can guide the magnetic induction lines generated by the coil 22, thereby preventing interference from the radiated magnetic field to the sensing element 41.

[0417] In some embodiments, the first component 1 further includes a housing 11, which is a hollow structure. This not only reduces the material used in the first component 1 and lightens its weight, but also provides space to accommodate the magnetic element 12, the second component 2, and the coil 22, making the overall structure of the motor 10 more compact. More specifically, the housing 11 surrounds the outer side of the magnetic element 12, and the magnetic element 12 is fixedly connected to the housing 11.

[0418] Furthermore, the second component 2 also includes a central shaft 21, which is also a hollow structure. The hollow structure reduces the amount of material used in the second component 2 and lightens its weight. The hollow structure also increases the installation space for the third shield 53c, making the overall structure of the motor 10 more compact. More specifically, the coil 22 surrounds the outer side of the central shaft 21, and the coil 22 is fixedly connected to the central shaft 21.

[0419] Referring to Figure 45, the sensing component 4 includes a sensing element 41 and a signal element 42. One of the sensing element 41 and the signal element 42 is disposed on the first component 1 and moves with the first component 1, while the other is disposed on the second component 2. The specific arrangement is not limited and can be selected according to the actual situation. In this embodiment, the sensing element 41 is mounted on the first component 1, and the signal element 42 is mounted on the second component 2. The sensing element 41 is adapted to detect the magnetic signal of the signal element 42 to generate a displacement signal.

[0420] More specifically, in some embodiments, the sensor 41 is disposed on the housing 11, and the signal element 42 is disposed on the central shaft 21. Referring to Figure 47, the housing 11 is provided with a pressure plate 113c, and the sensor 41 is disposed on the pressure plate 113c. More specifically, a first through hole is formed on the sensor 41, and a second through hole corresponding to the first through hole is formed on the pressure plate 113c. The first through hole and the second through hole correspond to each other, and fasteners pass through the first through hole and the second through hole to fix the sensor 41 on the pressure plate 113c.

[0421] In some embodiments, please refer to FIG48, the signal element 42 is disposed on the first central shaft 11b, and a receiving groove 2211c is formed on the outer side of the first central shaft 11b. For ease of installation, the receiving groove 2211c has an opening at one end near the second central shaft 12b. The signal element 42 is installed into the receiving groove 2211c from the opening, and then the opening is sealed by the sealing element 2212c, thereby fixing the signal element 42 on the first central shaft 11b.

[0422] In one embodiment, the signal element 42 has a semi-circular cross-section. Specifically, the signal element 42 has a semi-circular cross-section, which ensures that during the operation of the motor 10, if a slight relative rotation occurs between the signal element 42 and the sensing element 41, the signal element 42 and the sensing element 41 can still cooperate to detect position information.

[0423] In one embodiment, the signal element 42 includes a long-period magnet group 411c and a short-period magnet group 412c arranged side by side; the long-period magnet group 411c and the short-period magnet group 412c are symmetrically arranged; the sensing element 41 includes a first sensing element 421c and a second sensing element 422c; the first sensing element 421c corresponds to the long-period magnet group 411c. Two pairs are provided to realize the absolute position measurement of the displacement sensing component 4, that is, based on the vernier principle, the absolute position is calculated using two signals with different periods.

[0424] Furthermore, the first sensor 421c is used to detect the magnetic signal of the long-period magnet group 411c to generate a first displacement signal. The second sensor 422c is used to detect the magnetic signal of the short-period magnet group 412c to generate a first displacement signal. Both the first and second sensors are connected to the controller. The controller receives the first and second displacement signals and obtains the displacement signal of the motor 10 based on the first and second displacement signals.

[0425] In some embodiments, both the long-period magnet group 411c and the short-period magnet group 412c extend along the extension direction of the central axis 21 and have the same length.

[0426] The long-period magnet assembly 411c includes multiple first long magnets 4111c and multiple second long magnets 4112c, which are alternately arranged; the magnetic poles of the first long magnets 4111c and the second long magnets 4112c are opposite. For example, the magnetic pole of the first long magnet 4111c is the N pole, and the magnetic pole of the second long magnet 4112c is the S pole. It should be noted that the dimensions of the first long magnets 4111c and the second long magnets 4112c are the same (i.e., the length, width, and height are the same).

[0427] The short-period magnet assembly 412c includes multiple first short magnets 4121c and multiple second short magnets 4122c, which are alternately arranged. The magnetic poles of the first short magnets 4121c and the second short magnets 4122c are opposite. For example, the magnetic pole of the first short magnet 4121c is the N pole, and the magnetic pole of the second short magnet 4122c is the S pole. It should be noted that the first short magnets 4121c and the second short magnets 4122c are the same size (i.e., the length, width, and height are the same).

[0428] It should be noted that since magnetic poles of the same length produce the same signal curve, if only the long-period magnet group 411c is used for measurement, it will be impossible to determine which first long magnet 4111c or second long magnet 4112c within the long-period magnet group 411c is located. Similarly, if only the short-period magnet group 412c is used for measurement, it will be impossible to determine which first short magnet 4121c or second short magnet 4122c within the short-period magnet group 412c is located. Therefore, it is necessary to use both the long-period magnet group 411c and the short-period magnet group 412c simultaneously, so that they work together for accurate measurement.

[0429] In some embodiments, both the first sensor 421c and the second sensor 422c include a Hall chip.

[0430] Please refer to Figures 49 and 50. Figure 49 shows the radial magnetic flux density diagrams of the motor 10 with and without shielding component 50c, and Figure 50 shows the axial magnetic flux density diagrams of the motor 10 with and without shielding component 50c. As can be seen from Figures 49 and 50, the use of shielding component 50c effectively shields the interference of the radiated magnetic field generated by the coil 22 of the motor 10 on the sensing component 4, improving the accuracy of the sensing component 4. Compared to the motor 10 without shielding component 50c, the motor 10 provided in this application, after adding shielding component 50c, reduces the axial magnetic flux density and its interference fluctuations by approximately half. This ensures a certain level of anti-interference capability for the signal processing of the sensing component 4, while the unshielded interference fluctuations have little impact on the sensor position signal. Therefore, the shielding component 50c of the motor 10 provided in this application can suppress more than 50% of interference, demonstrating excellent shielding performance.

[0431] Please refer to Figures 51 and 52. Figure 51 shows the displacement signal fluctuation of the motor 10 without shielding component 50c, and Figure 52 shows the displacement signal fluctuation of the motor 10 with shielding component 50c. From Figures 51 and 52, it can be concluded that shielding component 50c can effectively shield the magnetic induction lines generated by the coil 22 of the motor 10 from interfering with the sensing component 4, resulting in better signal stability of the sensing component 4 and completely avoiding fluctuations in the displacement signal under high current interference.

[0432] In some embodiments, please refer to Figures 53, 54 and 55. The motor 10 includes a first component 1 and a second component 2. The first component 1 can reciprocate relative to the second component 2 in a first direction. A bearing 30d is provided between the first component 1 and the second component 2. A liquid storage space 11d is provided in the first component 1. The first component 1 is also provided with an oil passage 20d, which connects the liquid storage space 11d and the bearing 30d so that oil can flow to the bearing 30d through the oil passage 20d.

[0433] In the motor 10 of this embodiment, the motor 10 includes a first component 1 and a second component 2. The first component 1 is reciprocating relative to the second component 2 in a first direction. A bearing 30d is provided between the first component 1 and the second component 2. A liquid storage space 11d is provided within the first component 1. The first component 1 also has an oil passage 20d, which connects the liquid storage space 11d and the bearing 30d so that oil can flow to the bearing 30d through the oil passage 20d. Thus, during the relative movement of the first component 1 and the second component 2, the oil passage 20d connects the liquid storage space 11d and the bearing 30d to transport the oil in the liquid storage space 11d to the bearing 30d, so that the oil can cool and lubricate the bearing 30d.

[0434] During the reciprocating motion of the first component 1 relative to the second component 2, the second component 2 can penetrate into the liquid storage space 11d to squeeze the oil in the liquid storage space 11d to flow along the oil passage 20d, so that the oil can be transported to the bearing 30d. The oil can cool and lubricate the bearing 30d to ensure the stability of the motor 10.

[0435] For example, when the first component 1 is connected to the wheel 100, the second component 2 can be connected to the vehicle body 200 through the tower top component of the suspension system 300. At this time, the first component 1 is the moving part component and the second component 2 is the stator component.

[0436] In this way, the motor 10 can be connected to the vehicle body 200 through the tower assembly of the suspension system 300. With the arrangement of the first assembly 1 and the second assembly 2, when the vehicle 1000 is bumped during driving and the wheels 100 are impacted and vibrate, the motor 10 can drive the first assembly 1 and the second assembly 2 to move relative to each other to adjust the distance between the vehicle body 200 and the wheels 100, thereby buffering the vehicle body 200, reducing the vibration of the vehicle body 200, and improving the comfort of the user driving the vehicle 1000.

[0437] In the embodiments of this application, for the design of the 20d dimension of the oil passage, a corresponding fluid dynamics model can be established, and the optimal structural design can be optimized according to common working conditions.

[0438] In this embodiment, the specific type of motor 10 is not limited to meet different needs. Specifically, in this embodiment, a linear motor 10 is used as an example for explanation. Furthermore, in this embodiment, the specific type of bearing 30d is not limited to meet different needs. For example, it can be a sliding bearing for the linear motor 10, or a ball screw linear motor bearing, etc.

[0439] In some embodiments, the first component 1 is sleeved on the outer periphery of the second component 2, and an air gap 12d is provided between the first component 1 and the second component 2. The air gap 12d is connected to the liquid storage space 11d, and the liquid storage space 11d and the air gap 12d are distributed along a first direction. When the second component 2 moves toward the liquid storage space 11d along the first direction, the air pressure in the liquid storage space 11d increases to drive the oil to flow through the oil passage 20d to the bearing 30d.

[0440] Thus, the air gap 12d can both avoid creating resistance to the relative movement of the first component 1 and the second component 2, and allow air inside the first component 1 to flow through the air gap 12d. At the same time, during the relative movement of the first component 1 and the second component 2, the gas in the liquid storage space 11d will also flow rapidly along the air gap 12d, thereby generating a pressure difference that drives the oil to flow in the oil passage 20d.

[0441] It can be understood that the first component 1 is fitted around the outer periphery of the second component 2, so that when the second component 2 moves back and forth relative to the first component 1 in the first direction, a pressure difference can be generated. The oil can be drawn in under the action of the pressure difference to achieve the function of timely lubrication of the bearing surface and heat dissipation.

[0442] In some embodiments, the first component 1 further includes a housing 11, and the second component 2 at least partially divides the internal space of the housing 11 into an upper chamber 135d and a lower chamber 136d, the lower chamber 136d being configured as a liquid storage space 11d.

[0443] For example, in this embodiment, the motor 10 can be a linear motor 10, the bearing 30d can be a thrust bearing, and the oil in the reservoir 11d can be cooling oil, stored at the bottom of the first component 1. That is, the reservoir 11d is located at the bottom of the housing 11 away from the second component 2. At this time, the oil passage 20d is at least partially disposed in the reservoir 11d and connects the reservoir 11d and the bearing 30d. During the up-and-down movement of the linear motor 10, due to the rapid change in the volume of the upper and lower air chambers of the motor 10, the narrow air gap 12d cannot immediately balance the air pressure of the upper and lower chambers, thereby squeezing the oil in the reservoir 11d into the oil passage 20d.

[0444] It should be noted that in one embodiment, the amount of oil in the storage space 11d is relatively small, and the second component 2 does not need to directly contact the oil in the storage space 11d; the oil can be squeezed into the oil passage 20d simply by air pressure. Of course, in other embodiments, the amount of oil in the storage space 11d is relatively large, and the second component 2 needs to directly contact the oil in the storage space 11d in order to squeeze the oil into the oil passage 20d.

[0445] In some embodiments, bearing 30d includes a first bearing 31d, which is disposed between housing 11 and second component 2.

[0446] In some embodiments, the oil passage 20d includes a first oil passage 21d, which is located inside the housing 11 and connects the liquid storage space 11d and the first bearing 31d.

[0447] In some embodiments, the first oil passage 21d includes a first oil inlet passage 211d, a first oil guide passage 212d, and a first oil outlet passage 213d. The inlet of the first oil inlet passage 211d is connected to the liquid storage space 11d, the first oil outlet passage 213d is located on the side of the first bearing 31d away from the liquid storage space 11d, and the first oil guide passage 212d is connected to the first oil inlet passage 211d and the first oil outlet passage 213d.

[0448] It should be noted that when oil is provided in the liquid storage space 11d, the inlet of the first oil inlet channel 211d is at least partially submerged in the oil to ensure that the oil can pass through the first oil channel 21d.

[0449] In some embodiments, the housing 11 includes a top wall 131d, a side wall 132d, and a bottom wall 133d, the top wall 131d and the bottom wall 133d being disposed opposite to each other along a first direction and connected to the two ends of the side wall 132d. The surface of the top wall 131d facing away from the bottom wall 133d is the top surface.

[0450] The first oil guide channel 212d is provided on the side wall 132d along the first direction, and the first oil outlet channel 213d is provided on the top wall 131d.

[0451] The first oil inlet channel 211d is provided on the side wall 132d, and the inlet of the first oil inlet channel 211d penetrates the inner wall surface of the side wall 132d to connect with the liquid storage space 11d.

[0452] Alternatively, the first oil inlet channel 211d is located on the bottom wall 133d, and the inlet of the first oil inlet channel 211d penetrates the inner wall surface of the bottom wall 133d to connect with the liquid storage space 11d.

[0453] Thus, the first oil passage 21d is located inside the housing 11, and without changing the original size of the motor 10, the oil in the reservoir 11d can be directed to the location of the first bearing 31d.

[0454] Specifically, the first oil guiding channel 212d is disposed inside the side wall 132d along the first direction, the liquid storage space 11d is located above the bottom wall 133d, the first oil inlet channel 211d is located at the lower end of the side wall 132d and the inlet of the first oil inlet channel 211d penetrates the surface of the side wall 132d, and the first oil outlet channel 213d is disposed on the top wall 131d. In this way, the first oil inlet channel 211d can be immersed in oil. When the second component 2 moves downward, the oil in the liquid storage space 11d can pass through the first oil inlet channel 211d, the first oil guiding channel 212d and the first oil outlet channel 213d in sequence, and then be introduced to the position of the first bearing 31d.

[0455] In some embodiments, the motor 10 further includes an annular limiting member (not shown in the figure), which is disposed between the top wall 131d and the second component 2. The annular limiting member is located on the side of the first bearing 31d away from the liquid storage space 11d and is used to abut against the first bearing 31d.

[0456] In some embodiments, the top wall 131d is formed with an oil clearance groove 134d, which is connected to the outlet of the first oil outlet channel 213d. The oil clearance groove 134d is formed by the outer annular surface of the top wall 131d in contact with the annular limiting member moving away from the second component 2.

[0457] In this way, avoiding the oil tank 134d allows the oil flowing out of the first oil outlet channel 213d to smoothly transition to the position of the first bearing 31d.

[0458] Specifically, an annular retaining member needs to be installed on the side of the first bearing 31d away from the liquid storage space 11d. The annular retaining member can hold the first bearing 31d in a predetermined position, ensuring the accurate positioning of the first bearing 31d to achieve its function. An oil clearance groove 134d is also provided on the side of the first bearing 31d away from the liquid storage space 11d. The oil clearance groove 134d can be formed by an inwardly recessed semi-circular section on the upper part of the housing 11, that is, a recess from the outer ring surface of the housing 11 that contacts the first bearing 31d and connects to the outlet of the first oil outlet channel 213d, thus avoiding the annular retaining member to ensure normal oil flow. The annular retaining member has gaps or notches that allow oil to pass through. Oil can flow from the oil clearance groove 134d through the annular retaining member to the first bearing 31d to cool and lubricate it, and then flow back to the internal space of the housing 11 through the oil guide groove 311d.

[0459] In some embodiments, an oil guide groove 311d is formed between the first bearing 31d and the second component 2, and the oil guide groove 311d connects the avoidance oil groove 134d and the upper chamber 135d.

[0460] Thus, the oil guide groove 311d is positioned between the first bearing 31d and the second component 2, allowing the oil reaching the first bearing 31d to lubricate the interface between the first bearing 31d and the second component 2 through the oil guide groove 311d. Simultaneously, the oil flowing out from the first oil passage 21d can return to the internal space of the housing 11 under its own gravity, and then return to the reservoir space 11d through the air gap 12d, achieving oil self-circulation.

[0461] Specifically, the clearance oil groove 134d can be located on the side of the first bearing 31d away from the liquid storage space 11d. To prevent the retaining spring at the upper end of the first bearing 31d from blocking the first oil outlet channel 213d, a circumferential arc-shaped clearance oil groove 134d is designed at the outlet of the first oil outlet channel 213d, allowing oil to flow out from the first bearing 31d and the oil guide groove 311d. The oil can flow back into the internal space of the housing 11 from the clearance oil groove 134d through the oil guide groove 311d.

[0462] In some embodiments, there are multiple first oil passages 21d, and the multiple first oil passages 21d are arranged circumferentially along the housing 11.

[0463] Thus, there are multiple first oil inlet channels 211d, first oil guide channels 212d, and first oil outlet channels 213d. Multiple first oil channels 21d can provide oil to the first bearing 31d at multiple points along the circumference, ensuring that the first bearing 31d is adequately lubricated and cooled, and preventing individual positions of the first bearing 31d from being unlubricated and uncooled.

[0464] In some embodiments, the second component 2 includes a central shaft 21, a portion of which is housed within the housing 11. A first bearing 31d is sleeved on the central shaft 21, and an oil guide groove 311d is formed between the outer wall surface of the central shaft 21 and the inner wall surface of the first bearing 31d.

[0465] In some embodiments, the second component 2 includes a central shaft 21, a portion of which is housed within the housing 11, a first bearing 31d is sleeved on the central shaft 21, and the central shaft 21 has a guide hole 2011d.

[0466] The first component 1 also includes a guide 15, which is at least partially inserted in the guide hole 2011d and is reciprocating relative to the central axis 21 in a first direction.

[0467] Bearing 30d also includes a second bearing 32d, which is disposed between guide member 15 and central shaft 21 and located in guide hole 2011d;

[0468] The oil passage 20d includes a second oil passage 22d, which is located inside the guide member 15 and connects to the liquid storage space 11d and the second bearing 32d.

[0469] Specifically, the central shaft 21 is slidably inserted into the first bearing 31d, and the guide member 15 and the second bearing 32d are both disposed within the guide hole 2011d and can slide relative to each other along the axial direction of the central shaft 21. Thus, when the first assembly 1 and the second assembly 2 move relative to each other, the central shaft 21 can move relative to the housing 11 along a first direction, thereby generating a pressure difference that causes the oil in the liquid storage space 11d to flow through the first oil passage 21d and the second oil passage 22d to the positions of the first bearing 31d and the second bearing 32d, thereby achieving lubrication and cooling of the first bearing 31d and the second bearing 32d.

[0470] In the embodiments of this application, the specific type, material, and model of the first bearing 31d and the second bearing 32d are not limited to meet different needs. For example, when the motor 10 is a linear motor 10, the material of the first bearing 31d and the second bearing 32d is CuSn12 tin bronze.

[0471] In some embodiments, the second oil passage 22d includes a second oil inlet passage 221d, a second oil guide passage 222d, and a second oil outlet passage 223d. The inlet of the second oil inlet passage 221d is connected to the liquid storage space 11d, and the second oil guide passage 222d is connected to the second oil inlet passage 221d and the second oil outlet passage 223d. The second oil outlet passage 223d is located on the side of the second bearing 32d away from the liquid storage space 11d.

[0472] Specifically, the first component 1 of the linear motor 10 proposed in this invention includes a guide 15 and a housing 11. The oil passage 20d includes a first oil passage 21d and a second oil passage 22d. The first oil passage 21d and the second oil passage 22d can be respectively arranged at the positions of the guide 15 and the housing 11, thereby lubricating and cooling the first bearing 31d and the second bearing 32d.

[0473] It should be noted that both the housing 11 and the guide member 15 are circumferentially symmetrical structures. Multiple first oil passages 21d and second oil passages 22d can be respectively arranged in the housing 11 and the guide member 15 to ensure sufficient oil is introduced into the first bearing 31d and the second bearing 32d.

[0474] In one embodiment, four first oil passages 21d and second oil passages 22d are evenly distributed circumferentially at the bottom of the housing 11 and guide member 15, thereby ensuring that the first oil outlet channel 213d and the second oil outlet channel 223d can be evenly distributed and discharge oil. The first bearing 31d and the second bearing 32d have an oil outlet point every 90 degrees. It should be noted that in this embodiment, the number of first oil passages 21d and second oil passages 22d is not limited to meet different needs. The number of first oil passages 21d and second oil passages 22d can be determined according to the actual cooling requirements of the first bearing 31d and the second bearing 32d, and the number of first oil passages 21d and second oil passages 22d can also be 2, 8, or other quantities.

[0475] In other embodiments, the first oil passage 21d and the second oil passage 22d may not be uniformly circumferentially grooved; the arrangement can be designed based on whether the motor 10 tilts during long-term operation and the rationality of the tilt angle. In such embodiments, areas with more oil after the liquid storage space 11d tilts can have fewer first oil passages 21d and second oil passages 22d, while areas with less oil after the liquid storage space 11d tilts can have more first oil passages 21d and second oil passages 22d, thereby ensuring that the oil obtained by the first bearing 31d and the second bearing 32d is relatively uniform. Furthermore, it is necessary to ensure that both the first oil inlet channel 211d and the second oil inlet channel 221d are submerged below the oil surface.

[0476] For example, after the motor 10 of this embodiment is installed on the suspension system 300 of the vehicle 1000, the axial direction of the motor 10 will have an installation tilt angle of 0-20° with respect to the vertical direction. For example, the installation tilt angle of the axial direction of the motor 10 with respect to the vertical direction can be 0°, 5°, 10°, 15°, 20°, etc. After the axial direction of the motor 10 is tilted with respect to the vertical direction, the oil level of the reservoir 11d will change due to the uphill, downhill, turning, and sudden stop of the vehicle 1000. At this time, it is important to avoid the situation where part of the first oil inlet channel 211d or the second oil inlet channel 221d is not submerged in oil. Therefore, during the circumferential arrangement of the first oil passage 21d and the second oil passage 22d, it is necessary to ensure that they match the oil level after the motor 10 is tilted. In one example, when the installation tilt angle between the axial direction and the vertical direction of the motor 10 is 20°, the number of the first oil passage 21d and the second oil passage 22d are both 8. The 8 first oil inlet channels 211d or second oil inlet channels 221d are not uniformly distributed, and it is ensured that the first oil inlet channel 211d or the second oil inlet channel 221d are all submerged in oil.

[0477] In some embodiments, at the first extreme position, the outlet end of the second oil outlet channel 223d is located on the side of the second bearing 32d away from the liquid storage space 11d. The first extreme position is the position where the first component 1 is far away from the second component 2 along the first direction to the extreme.

[0478] Thus, the first extreme position is when the guide 15 is pulled away from the guide hole 2011d to the farthest position. At this time, the second oil outlet channel 223d is still located above the first extreme position, which can ensure that the oil flows out from the second oil channel 22d to lubricate and cool the second bearing 32d.

[0479] Specifically, when the first component 1 and the second component 2 of the motor 10 move relative to each other, they have a first limit position and a second limit position. The first limit position is when the first component 1 moves away from the second component 2 to a limit along a first direction, and the second limit position is when the first component 1 moves closer to the second component 2 to a limit along the first direction. In this embodiment, regardless of how the second component 2 moves relative to the first component 1, the first oil outlet channel 213d and the second oil outlet channel 223d are both located above the first bearing 31d and the second bearing 32d, respectively. Similarly, the first oil inlet channel 211d and the second oil inlet channel 221d are always located below the oil in the reservoir 11d.

[0480] For example, the multiple second oil inlet channels 221d at the bottom of the guide member 15 extend radially inward, and the number of second oil guide channels 222d can be one. The oil from the multiple second oil inlet channels 221d converges at the second oil guide channel 222d at the center of the guide member 15 and extends upward to the top along the second oil guide channel 222d at the center of the guide member 15. The second oil outlet channel 223d can also be set at the center of the guide member 15. Both the second oil outlet channel 223d and the second oil guide channel 222d are arranged along the first direction. In this way, the oil can flow out from the center of the bottom surface of the cylindrical guide member 15 and lubricate and cool the second bearing 32d. Then, under the action of gravity, the oil returns to the liquid storage space 11d along the outer wall of the guide member 15, thereby realizing oil circulation.

[0481] It is understandable that when the first component 1 and the second component 2 of the motor 10 move relative to each other, the second component 2 will not directly contact the oil in the reservoir 11d regardless of its state. In other words, when the second component 2 is in the second limit position, it will not intrude into the reservoir 11d, thus avoiding the oil from entering the air gap 12d and causing an increase in the running resistance of the motor 10.

[0482] In some embodiments, the motor 10 further includes a filter screen, which is disposed inside the housing 11 and located at the communication position between the oil passage 20d and the liquid storage space 11d.

[0483] Specifically, filter screens are installed at the inlets of the first oil inlet channel 211d and the second oil inlet channel 221d. Metal debris on the surface of the filter screen can be attracted by a ring of magnets at the bottom of the housing 11 to prevent the narrow oil passage from being blocked and to prevent the metal debris generated during the operation of the motor 10 from reducing the service life of the bearing due to the wear of the bearing by the lubricating oil.

[0484] In some implementations, for the convenience of oil maintenance of the motor 10, an oil change and maintenance drain port and an oil filling port may be provided at the bottom of the lower fork arm and the top of the housing 11.

[0485] In some embodiments, the air gap 12d connects the upper chamber 135d and the lower chamber 136d, and the ratio of the area of ​​the air gap 12d in the first cross section to the area of ​​the lower chamber 136d along the first cross section is 1 / 40 to 1 / 20.

[0486] The first cross section is perpendicular to the first direction.

[0487] For example, the ratio of the area of ​​the air gap 12d in the first cross section to the area of ​​the lower chamber 136d along the first cross section can be 1 / 40, 1 / 39, 1 / 38, 1 / 37, 1 / 36, 1 / 35, 1 / 34, 1 / 33, 1 / 32, 1 / 31, 1 / 30, 1 / 29, 1 / 28, 1 / 27, 1 / 26, 1 / 25, 1 / 24, 1 / 23, 1 / 22, 1 / 21, or 1 / 20.

[0488] Of course, the air gap 12d between the first component 1 and the second component 2 will vary depending on the model of the motor 10 and the specific configuration, and is not limited here. In one embodiment, the ratio of the area of ​​the air gap 12d to the area of ​​the first component 1 along the first cross section can be 1 / 30.

[0489] For example, the liquid storage space 11d at the bottom of the motor 10 stores a suitable amount of oil, which can submerge the first oil inlet channel 211d and the second oil inlet channel 221d. The oil can be drawn in by the pressure difference when the motor 10 moves up and down to achieve lubricating oil circulation. The specific implementation principle is as follows: when the second component 2 moves downward, the volume of the upper air chamber inside the housing 11 decreases, and the volume of the lower air chamber inside the housing 11 increases. The pressure balance between the upper and lower air chambers (i.e., the upper chamber and the lower chamber) is achieved by the air flow in the air gap 12d outside the second component 2 to balance the air pressure of the upper and lower chambers. However, due to the narrow structure of the air gap 12d, the flow area of ​​the air gap 12d for air exchange between the upper and lower air chambers is only 1 / 30 of the bottom area. The air flow between the upper and lower air chambers is lagging, and the axial length of the air gap 12d is large, resulting in a large pressure difference. In summary, the downward movement of motor 10 increases the compressed air pressure in the lower air chamber and decreases the expanded air pressure in the upper air chamber, resulting in a pressure difference between the first oil inlet channel 211d and the first oil outlet channel 213d, and between the second oil inlet channel 221d and the second oil outlet channel 223d. Under the action of the pressure difference, the oil can flow from bottom to top along the flow channel to lubricate and cool the upper and lower bearings (i.e., the first bearing and the second bearing).

[0490] When the second component 2 moves upward, the lower air chamber is under expansion pressure, while the upper air chamber is under compression pressure. There is a negative pressure difference between the first oil inlet channel 211d and the first oil outlet channel 213d, and between the second oil inlet channel 221d and the second oil outlet channel 223d in the housing 11. Air from the upper air chamber can flow into the lower air chamber along the oil passage, which can balance the pressure of the upper and lower air chambers to a certain extent.

[0491] It is worth noting that as the speed of the motor 10 increases, the friction and heat generation of the upper and lower sliding bearings of the motor 10 become more intense. At this time, the faster the motor 10 moves, the faster the upper and lower air chambers are compressed or expanded, resulting in a greater pressure difference between the upper and lower air chambers and consequently a greater self-lubricating oil supply. The motor 10 of this embodiment can achieve self-adjusting self-lubrication and cooling effects, and the motor 10 of this embodiment has significant advantages and broad applicability.

[0492] The motor 10 of this application embodiment has a simple structure, requires no external accessories, has high reliability and strong adaptability, can achieve self-lubrication and cooling of lubricating oil under non-powered structure, and can achieve adaptive matching of changing working conditions; compared with traditional grease lubrication, it has better heat dissipation effect and longer service life; compared with the bearing active cooling scheme, the motor 10 of this application embodiment has a simple structure and lower cost.

[0493] In this embodiment, the motor 10 operates vertically, and the pressure difference between the upper and lower air chambers enables lubrication oil supply without power. The lubricating oil can return under gravity. This solution has a simple structure, requires no additional complex mechanical structures, and offers high reliability. It also eliminates the need for disassembly, simplifies lubrication oil replacement, and extends service life.

[0494] In summary, existing self-lubricating bearings rely on excessive solid grease filling. When the solid grease is gradually consumed over time, a spring pushes a push plate, causing the solid grease to move downwards to compensate and maintain lubrication. The present invention utilizes the pressure difference between the upper and lower air chambers created by the up-and-down movement of the motor 10 to supply lubricating oil in a non-powered environment. The lubricating oil can return under gravity. This solution has a simple structure, requires no additional complex mechanical structures, and offers high reliability and adaptability. It enables self-lubrication and cooling of the lubricating oil in a non-powered environment and can adaptively match changing operating conditions. Furthermore, lubricating oil replacement is simple without disassembling the main structure, resulting in a longer service life.

[0495] The above are merely specific embodiments of this application, but the scope of protection of this application 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 application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. An electric motor, comprising: A magnetic element (12) and a winding structure (22A) are provided, the winding structure (22A) including an iron core (23) and a coil (22) disposed within the iron core (23); one of the magnetic element (12) and the winding structure (22A) surrounds the other of the magnetic element (12) and the winding structure (22A), and the magnetic element (12) and the winding structure (22A) cooperate to enable the magnetic element (12) and the winding structure (22A) to move relative to each other in a first direction; The maximum thrust F of the motor and the electromagnetic volume V of the motor satisfy the following conditions: F = kV, where k is the thrust-to-volume ratio of the motor, in Newtons per liter, 1000 ≤ k ≤ 3500, and V = πR. 2 *L, R is the outer diameter of one of the magnetic element (12) and the winding structure (22A), in decimeters; L is the shorter of the length of the magnetic element (12) in the first direction and the length of the winding structure (22A) in the first direction, in decimeters; the maximum thrust F of the motor is in Newtons; and the electromagnetic volume V of the motor is in liters.

2. The motor according to claim 1, wherein the thrust-to-volume ratio of the motor satisfies: 1000≤k≤3000, or 1500≤k≤3000, or 2000≤k≤3500, or 2000≤k≤3000, or 2500≤k≤3500.

3. The motor according to claim 1, wherein the relationship between the maximum thrust F of the motor and the modulation ratio X of the motor satisfies: F = 2450.7lnX + 1000V + 231.2, where, X = Pm / Pa, where Pm is the number of pole pairs of the magnetic element (12) and Pa is the number of pole pairs of the winding structure (22A).

4. The motor according to any one of claims 1-3, wherein the iron core (23) comprises a plurality of iron core blocks (1a) stacked along the first direction, a winding space is formed between two adjacent iron core blocks (1a), and the coil (22) is disposed in the winding space.

5. The motor according to any one of claims 1-3, wherein the iron core (23) comprises a plurality of iron core blocks (1a) stacked along the first direction; The iron core block (1a) includes: Core block body (11a); and A first magnetic adjusting block (12a) is disposed on the iron core block body (11a); the material of the first magnetic adjusting block (12a) is at least partially different from that of the iron core block body (11a), and the resistivity of the first magnetic adjusting block (12a) is higher than that of the iron core block body (11a).

6. The motor according to any one of claims 1-3, wherein the iron core (23) comprises a plurality of iron core blocks (1a) stacked along the first direction; The iron core block (1a) includes: Core block body (11a); and A first magnetic adjustment block (12a) is disposed on the iron core block body (11a); the material of the first magnetic adjustment block (12a) is at least partially different from that of the iron core block body (11a), and the tensile strength of the material of the iron core block body (11a) is greater than that of the material of the first magnetic adjustment block (12a).

7. The motor according to any one of claims 4-6, wherein the magnetic element (12) surrounds the winding structure (22A), and the motor further includes a central shaft (21), the winding structure (22A) being connected to the central shaft (21); The core block (1a) has a first central hole (14a), and the first central holes (14a) of a plurality of core blocks (1a) are interconnected to form a core hole. The core (23) also includes a second magnetic adjustment block (2a), which is installed on the hole wall of the core hole. The second magnetic adjustment block (2a) has a second central hole (21a) through which the central shaft (21) passes. The second magnetic adjustment block (2a) is made of at least partially different material from the iron core block body (11a), and the resistivity of the second magnetic adjustment block (2a) is higher than that of the iron core block body (11a).

8. The motor according to claim 7, wherein the number of the iron core blocks (1a) is N, the axial length of a single iron core block (1a) is P, the axial length of the second magnetic adjusting block (2a) is Q, P×(N-1)<Q≤P×N, N≥2 and N is an integer.

9. The motor according to any one of claims 4-8, wherein the magnetic element (12) surrounds the winding structure (22A), and the motor further includes a central shaft (21), the winding structure (22A) being connected to the central shaft (21); The central shaft (21) includes a first central shaft body (11b) and a second central shaft body (12b). The first central shaft body (11b) and the second central shaft body (12b) are arranged and fixedly connected along the axial direction of the central shaft (21). A shoulder (20b) is formed on the radially outer side of the first central shaft body (11b). Multiple core blocks (1a) are assembled on the second central shaft (12b). Among the multiple core blocks (1a), there is a first end core block (32b) adjacent to the first central shaft (11b). The first end core block (32b) has a support portion (33b) that abuts against the shoulder (20b) to limit the relative position of the first end core block (32b) and the first central shaft (11b).

10. The motor according to claim 9, wherein the end of the first end core block (32b) facing the first central shaft (11b) has a clearance space (321b), the clearance space (321b) being opposite to the first central shaft (11b) along the axial direction of the central shaft (21) to space the first end core block (32b) and the first central shaft (11b) apart.

11. The motor according to claim 10, wherein along the axial direction of the central shaft (21), the end of the first end core block (32b) facing the first central shaft body (11b) has a recessed clearance space (321b) that is recessed in a direction away from the first central shaft body (11b), so that the support portion (33b) is formed on the radially outer side of the clearance space (321b).

12. The motor according to claim 10, wherein the cross-sectional dimension of the clearance space (321b) is larger than the cross-sectional dimension of the first central shaft (11b), and the orthographic projection of the first central shaft (11b) is located within the clearance space (321b) along the axial direction of the central shaft (21).

13. The motor according to claim 12, wherein the cross-section of the clearance space (321b) is circular, the cross-section of the first central shaft (11b) is circular, the maximum diameter of the first central shaft (11b) is D1, and the diameter of the clearance space (321b) is D2, satisfying the relationship: 1.02≤D2 / D1≤1.

05.

14. The motor according to any one of claims 10-13, wherein the thickness of the first end core block (32b) along the axial direction of the central shaft (21) is H1, and the depth of the clearance space (321b) is H2, satisfying the relationship: 0.25≤H2 / H1≤0.

55.

15. The motor according to any one of claims 1-14, comprising a first component (1) and a second component (2), the first component (1) comprising one of the magnetic element (12) and the winding structure (22A), the second component (2) comprising the first component (1) comprising the other of the magnetic element (12) and the winding structure (22A), the first component (1) and the second component (2) being movable relative to each other along the first direction; A bearing (30d) is provided between the first component (1) and the second component (2). The first component (1) is provided with a liquid storage space (11d) and an oil passage (20d). The oil passage (20d) connects the liquid storage space (11d) and the bearing (30d) so that the oil flows through the oil passage (20d) to the bearing (30d).

16. The motor according to claim 15, wherein the first component (1) is sleeved on the outer periphery of the second component (2), an air gap (12d) is provided between the first component (1) and the second component (2), the air gap (12d) is connected to the liquid storage space (11d), and the liquid storage space (11d) and the air gap (12d) are distributed along the first direction, and when the second component (2) moves toward the liquid storage space (11d) along the first direction, the air pressure in the liquid storage space (11d) increases to drive the oil to flow through the oil passage (20d) to the bearing (30d).

17. The motor according to claim 16, wherein the first component (1) further comprises a housing (11), one of the magnetic element (12) and the winding structure (22A) is disposed within the housing (11), and the second component (2) at least partially divides the internal space of the housing (11) into an upper chamber (135d) and a lower chamber (136d), the lower chamber (136d) being configured as the liquid storage space (11d); The bearing (30d) includes a first bearing (31d), which is disposed between the housing (11) and the second component (2); The oil passage (20d) includes a first oil passage (21d)(20d), which is located inside the housing (11) and connects the liquid storage space (11d) and the first bearing (31d).

18. The motor according to claim 17, wherein the second component (2) includes a central shaft (21), a portion of the central shaft (21) is housed within the housing (11), the first bearing (31d) is sleeved on the central shaft (21), and the central shaft (21) has a guide hole (2011d); The first component (1) further includes a guide (15) which is at least partially inserted in the guide hole (2011d) and is movable relative to the central axis (21) in the first direction; The bearing (30d) further includes a second bearing (32d), which is disposed between the guide member (15) and the central shaft (21) and located within the guide hole (2011d); The oil passage (20d) includes a second oil passage (22d)(20d), which is located inside the guide member (15) and connects the liquid storage space (11d) and the second bearing (32d).

19. The motor according to any one of claims 1-18, comprising a first component (1) and a second component (2), the first component (1) comprising one of the magnetic element (12) and the winding structure (22A), the second component (2) comprising the other of the magnetic element (12) and the winding structure (22A), the first component (1) and the second component (2) being movable relative to each other along the first direction; The motor further includes a sensing component (4), which is disposed on the first component (1) and / or the second component (2) and is adapted to generate a displacement signal characterizing the relative position of the first component (1) and the second component (2).

20. The motor according to claim 19 further includes a shielding component (50c), the shielding component (50c) being mounted on the first component (1) and / or the second component (2), and being adapted to reduce the influence of the magnetic field generated by the current flowing through the coil (22) on the displacement signal.

21. The motor according to claim 20, wherein the shielding assembly (50c) includes a first shielding member (51c), the first shielding member (51c) being disposed on the first assembly (1), and the first shielding member (51c) being used to change the direction of the magnetic induction lines generated by the coil (22).

22. The motor according to claim 21, wherein the first component (1) includes a housing (11) and a magnetic element (12) disposed in the housing (11), the second component (2) includes a winding structure (22A), a mounting cavity (11A) is formed in the housing (11), the winding structure (22A) is movably disposed in the mounting cavity (11A) along the first direction, and the first shielding element (51c) is mounted on the housing (11).

23. The motor according to any one of claims 20-22, wherein the sensing component (4) comprises a sensing element (41) and a signal element (42), the sensing element (41) being adapted to acquire a signal from the signal element (42) to generate the displacement signal, and the sensing element (41) being adapted to move between a first position away from the coil (22) and a second position close to the coil (22); The shielding component (50c) includes a second shield (52c), which is disposed on the first component (1). The second shield (52c) is used to change the direction of the magnetic induction lines generated by the coil (22). When the sensing element (41) is in the second position, the second shield (52c) covers the coil (22) in the axial direction of the motor.

24. The motor according to claim 23, wherein the first component (1) includes a housing (11) and the magnetic element (12), the magnetic element (12) is disposed on the inner side of the housing (11), the second shielding element (52c) is disposed on the outer side of the housing (11), and the second shielding element (52c) overlaps at least partially with the magnetic element (12) in the axial direction of the motor.

25. The motor according to any one of claims 20-22, wherein the shielding assembly (50c) includes a third shield (53c) adapted to change the direction of the magnetic induction lines generated by the coil (22) along the first direction.

26. The motor according to claim 25, wherein the second component (2) includes a central shaft (21) and a winding structure (22A), the winding structure (22A) being connected to the central shaft (21), the central shaft (21) being coaxially arranged with the coil (22), and the central shaft (21) including a first central shaft body (11b) and a second central shaft body (12b) connected to each other; in, The coil (22) is mounted and fixed on the second central shaft (12b), and the third shield (53c) is disposed on the first central shaft (11b).

27. The motor according to any one of claims 1-26, comprising a first component (1), the first component (1) comprising one of the magnetic element (12) and the winding structure (22A); The first component (1) further includes: The housing (11) has a mounting cavity (11A) and a communicating hole (11C) inside. The mounting cavity (11A) has a first opening. The communicating hole (11C) communicates with the mounting cavity (11A) and is adapted to communicate with the inner cavity (30A) of the air spring. End cap (13) covering the first opening and connected to the housing (11), forming a first gap (16) between the end cap (13) and the housing (11); A first sealing structure (14) is used to block the fluid communication between the mounting cavity (11A) and the external space through the first gap (16).

28. The motor according to claim 27, further comprising a second component (2) including the other of the magnetic element (12) and the winding structure (22A), wherein the first component (1) and the second component (2) are movable relative to each other in a first direction; The second component (2) is disposed in the mounting cavity (11A) and is movable relative to the housing (11) in the first direction within the mounting cavity (11A); The housing (11) is a cylindrical structure. In the first direction, one of the housing (11) and the end cover (13) includes a first end face (16A) and the other includes a second end face (16B). The first gap (16) is provided between the first end face (16A) and the second end face (16B). The first gap (16) connects the mounting cavity (11A) and the external space.

29. The motor according to claim 27 further includes a sensing component (4), the sensing component (4) including a sensing element (41) and a signal element (42), the sensing element (41) being adapted to acquire the signal of the signal element (42) to generate the displacement signal; The housing (11) is provided with a cable outlet hole (11D) that passes through the housing (11); The signal element (42) is connected to the second component (2), and the sensing element (41) is connected to the side of the housing (11) opposite to the end cover (13) and covers the wire outlet (11D). The connecting wire of the sensor (41) is led out to the outside of the housing (11) through the outlet hole (11D).

30. The motor according to claim 29, wherein a second gap (17) is formed between the sensing element (41) and the housing (11), the second gap (17) communicating the mounting cavity (11A) and the external space, and is adapted to communicate the air spring (30) and the external space; The motor also includes a second sealing structure (5) for blocking fluid communication between the mounting cavity (11A) and the external space, and between the air spring and the external space through the second gap (17).

31. The motor according to claim 30, wherein the second sealing structure (5) is disposed between the sensing element (41) and the housing (11), and surrounds the wire outlet (11D); In the first direction, one of the sensing elements (41) and the housing (11) includes a third end face (17A) and the other includes a fourth end face (17B), and the second gap (17) is provided between the third end face (17A) and the fourth end face (17B).

32. A suspension system comprising the motor according to any one of claims 1-31.

33. A vehicle comprising an electric motor as described in any one of claims 1-31, or comprising a suspension system as described in claim 32.

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