Cam, actuator, suspension assembly and vehicle

Abstract

A cam, an actuator, a suspension assembly and a vehicle. The cam is provided with at least one guide groove, the guide groove spirally extends in the axial direction of the cam, the radius of the cam is defined as r, and the helix angle of the guide groove is defined as θ; the cam is adapted to fit with an output member, such that the cam moves relative to the output member in the axial direction of the cam, so as to output a thrust F; and the relationship between the radius r of the cam and the helix angle θ of the guide groove satisfies formula I, where M is an input torque for driving the cam to rotate, and n is a coefficient, and satisfies 0.9≤n≤1.1.

Description

Cams, actuators, suspension components and vehicle

[0001] This application claims priority to Chinese Patent Application No. 202411935289.6, filed on December 24, 2024, and Chinese Patent Application No. 202411934251.7, filed on December 24, 2024, the entire contents of which are incorporated herein by reference. Technical Field

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

[0003] A vehicle includes a body, wheels, and a suspension assembly connecting the body and wheels. The suspension assembly is used to buffer the impact forces transmitted to the body from uneven road surfaces to ensure the smoothness of the vehicle's ride. Summary of the Invention

[0004] In a first aspect, a cam is provided. The cam has at least one guide groove that extends helically along the axial direction of the cam, the radius of the cam is r, and the helix angle of the guide groove is θ; the cam is adapted to cooperate with an output component so that the cam and the output component move relative to each other along the axial direction of the cam to output a thrust F.

[0005] The relationship between the cam radius r and the helix angle θ of the guide groove is as follows:

[0006] Where M is the input torque that drives the cam to rotate, and n is a coefficient, 0.9≤n≤1.1.

[0007] Secondly, an actuator is provided. The actuator includes the aforementioned cam and output member. At least a portion of the output member is located within a guide groove.

[0008] Thirdly, a cam is provided. The cam can cooperate with an output element to convert the rotational motion of one of the cam and the output element into the linear motion of the other. The cam has a receiving cavity configured to store a lubricating medium for lubricating the cam and the output element.

[0009] Fourthly, an actuator is provided. The actuator includes the aforementioned cam and output member. The output member is adapted to engage with the cam to convert the rotational motion of one of the cam and the output member into the linear motion of the other.

[0010] Fifthly, a suspension assembly is provided. The suspension assembly includes the aforementioned actuator.

[0011] Sixthly, a vehicle is provided. The vehicle includes any one of the aforementioned cam, actuator, or suspension assembly. Attached Figure Description

[0012] Figure 1 is a structural schematic diagram of the vehicle provided in an embodiment of this disclosure;

[0013] Figure 2 is a schematic diagram of the connection relationship between the wheels and the suspension assembly in the vehicle shown in Figure 1;

[0014] Figure 3 is a schematic diagram of the external structure of the actuator shown in Figure 2;

[0015] Figure 4 is a cross-sectional schematic diagram of the actuator shown in Figure 3;

[0016] Figure 5 is a schematic diagram of the external structure of the casing in Figure 4;

[0017] Figure 6 is a schematic diagram of the cross-sectional structure of the casing in Figure 5;

[0018] Figure 7 is a schematic diagram of the external structure of the cam in Figure 4;

[0019] Figure 8 is a schematic diagram of the cross-sectional structure of the cam in Figure 7;

[0020] Figure 9 is a schematic diagram of the fit between the cam and the output component in Figure 4;

[0021] Figure 10 is a schematic cross-sectional view of the cam and output component in Figure 9;

[0022] Figure 11 is a schematic diagram of the guide routes of the first guide groove and the second guide groove;

[0023] Figure 12 is a schematic diagram of the external structure of the output component in Figure 4;

[0024] Figure 13 is a cross-sectional view of the output component in Figure 12;

[0025] Figure 14 is a schematic diagram of the output component in Figure 12 viewed from top to bottom;

[0026] Figure 15 is a schematic diagram of the force analysis during the relative motion between the cam and the output component;

[0027] Figure 16 is a schematic diagram showing the relationship between the development line of the cam profile and the helix angle;

[0028] Figure 17 is a schematic diagram of the structure of a cam provided in some embodiments of this disclosure, which retains only the guide groove and the circumferential groove wall forming the guide groove;

[0029] Figure 18 is a top view of the cam shown in Figure 17;

[0030] Figure 19 is a cross-sectional view of the cam shown in Figure 18 along the CC line;

[0031] Figure 20 shows the outline parameters of the guide groove when they satisfy the linear parameters of a first-order polynomial, a second-order polynomial, a cosine acceleration motion trajectory, and a sine acceleration motion trajectory, respectively.

[0032] Reference numerals: 100, vehicle; 10, body; 20, wheel; 30, suspension assembly; 1, actuator; 11, drive component; 111, housing; 1111, body; 1112, cover; 1113, wishbone; 112, stator; 113, mover; 114, limiting boss; 12, cam; 121, guide groove; 1211, first guide groove; 1212, second guide groove; 122, receiving cavity; 123, first opening; 124, main body; 125, sealing part; 13, output component; 131, transmission component; 1311, rod; 1312, connecting column; 132, follower; 1321, first follower; 1322, second follower; 1323, sliding column; 133, limiting protrusion; 15. Buffer component; 16. First bearing; 17. Second bearing; 2. Tower top assembly; 3. Spring. Detailed Implementation

[0033] The technical solutions of the embodiments of this disclosure will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this disclosure, and not all embodiments. Based on the embodiments of this disclosure, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this disclosure.

[0034] In the description of this disclosure, it should be understood that the terms "upper," "lower," "left," "right," "front," "rear," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or relative positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this disclosure and for simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this disclosure. Unless otherwise specified, the above-mentioned orientational descriptions can be flexibly set in practical applications, provided that the relative positional relationships shown in the accompanying drawings are satisfied.

[0035] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this disclosure, unless otherwise stated, "a plurality of" means two or more.

[0036] In the description of this disclosure, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "communication" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection. They can refer to a direct connection or an indirect connection through an intermediate medium, or a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this disclosure according to the specific circumstances.

[0037] In embodiments of this disclosure, the terms "comprising," "including," or any other variations thereof are intended to cover a non-exclusive inclusion, such that a process, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, article, or apparatus that includes that element.

[0038] In this disclosure, the terms "exemplarily" or "for example" are used to indicate that something is an example, illustration, or illustration. Any embodiment or design described as "exemplarily" or "for example" in this disclosure should not be construed as being more preferred or advantageous than other embodiments or designs. Rather, the use of the terms "exemplarily" or "for example" is intended to present the relevant concepts in a specific manner.

[0039] "At least one of A, B and C" has the same meaning as "at least one of A, B or C", both including the following combinations of A, B and C: only A, only B, only C, combinations of A and B, combinations of A and C, combinations of B and C, and combinations of A, B and C.

[0040] 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.

[0041] In related technologies, suspension components include cams and drive shafts. The cams and drive shafts work together to adjust the distance between the vehicle body and the wheels to ensure vehicle stability. However, in order to ensure the structural strength of the cams when the suspension components push the vehicle body, the cams are usually large, resulting in the suspension components occupying a large amount of space, which is not conducive to the layout of the suspension components.

[0042] Therefore, some embodiments of this disclosure provide a vehicle 100. The vehicle 100 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 100 can also be a sedan, truck, bus, lorry, trailer, etc., and this disclosure does not limit the type of vehicle.

[0043] As shown in Figures 1 and 2, Figure 1 is a structural schematic diagram of a vehicle 100 provided in some embodiments of this disclosure, and Figure 2 is a schematic diagram of the connection relationship between the wheel 20 and the suspension assembly 30 in the vehicle 100 shown in Figure 1. The vehicle 100 may include wheels 20 and a body 10. The wheels 20 are connected to the underside of the body 10, and during the driving of the vehicle 100, the wheels 20 rotate to drive the body 10 to move.

[0044] In some embodiments, as shown in Figures 1 and 2, the vehicle 100 may further include a suspension assembly 30. The suspension assembly 30 is connected between the vehicle body 10 and the wheels 20 to buffer the impact force transmitted to the vehicle body 10 from uneven road surfaces, thereby ensuring the smoothness of the vehicle 100's ride and improving the performance of the vehicle 100.

[0045] The suspension assembly 30 includes a tower top assembly 2, an actuator 1, and a spring 3.

[0046] For example, the tower top assembly 2 is connected to the actuator 1 and to the vehicle body 10. The spring 3 is sleeved on the actuator 1. During the operation of the vehicle 100, affected by the bumps of the road surface, the actuator 1 can adjust the distance between the vehicle body 10 and the wheel 20 to ensure the stability of the vehicle body 10; the spring 3 is used to buffer the force transmission between the wheel 20 and the vehicle body 10.

[0047] In some embodiments, spring 3 can be a helical spring, air spring, etc. The helical spring can be a cylindrical helical spring, which is sleeved around the actuator 1. In other embodiments, spring 3 can also be a tower spring, disc spring, etc.

[0048] In some embodiments, as shown in Figures 3 and 4, the actuator 1 includes a drive member 11, a cam 12, and an output member 13. The drive member 11 includes a housing 111. At least a portion of the cam 12 and the output member 13 are disposed within the housing 111. Thus, the housing 111 can provide protection for the cam 12 and the output member 13, preventing damage to them.

[0049] The cam 12 and the output member 13 are connected to each other so that the cam 12 and the output member 13 can move relative to each other along the axial direction of the cam 12. For example, the cam 12 and the output member 13 are connected to convert the rotational motion of one of the cam 12 and the output member 13 into the linear motion of the other.

[0050] The drive element 11 is connected to one of the cam 12 and the output element 13 to drive one of the cam 12 and the output element 13 to rotate.

[0051] In some examples, the drive element 11 includes a stator 112 and a mover 113, the stator 112 being disposed within and fixedly connected to the housing 111.

[0052] The mover 113 is located inside the housing 111 and is rotatable relative to the stator 112. The mover 113 is connected to one of the cam 12 and the output component 13.

[0053] With the above configuration, during the rotation of the mover 113 relative to the stator 112, the mover 113 can drive one of the cam 12 and the output component 13 to rotate, thereby driving the other of the cam 12 and the output component 13 to perform linear motion.

[0054] In this way, during the driving of the vehicle 100, the drive member 11 can drive one of the cam 12 and the output member 13 to rotate, thereby adjusting the length of the actuator 1, so that the vehicle body 10 is kept at a suitable height, so that the vehicle body 10 is kept stable and the vibration reduction effect of the vehicle 100 is achieved.

[0055] For example, the mover 113 can be connected to the output member 13. In this case, the output member 13 rotates to drive the cam 12 to move linearly.

[0056] For example, the mover 113 can be connected to the cam 12. In this case, the cam 12 rotates to drive the output element 13 to move linearly.

[0057] In some embodiments, as shown in FIG4, the cam 12 is disposed inside the housing 111, and the mover 113 surrounds the cam 12, and the stator 112 surrounds the mover 113.

[0058] With the above configuration, the mover 113 can drive the cam 12 to rotate, thereby driving the output component 13 to move linearly. Furthermore, by arranging the mover 113 around the cam 12, a large contact area can be achieved between the cam 12 and the mover 113, ensuring the stability of the connection between the mover 113 and the cam 12.

[0059] For example, the drive component 11 can be an electric motor or a hydraulic motor, etc.

[0060] In some embodiments, as shown in Figures 5 and 6, a limiting boss 114 is provided inside the housing 111. The limiting boss 114 is located on one side of the mover 113 in a first direction (the X direction as shown in Figure 4) to limit the stator 112. The first direction is consistent with the movement direction of the other of the cam 12 and the output member 13 (i.e. the one that performs linear motion).

[0061] For example, the number of limiting bosses 114 can be one. A limiting boss 114 can be set to extend around the first direction for one circumference, or it can be set not to extend around the first direction for one circumference.

[0062] For example, there can be multiple limiting bosses 114, which can be set at intervals or not at intervals.

[0063] With the above settings, when the stator 112 is installed onto the housing 111, the limiting protrusion 133 can restrict the stator 112 from moving along the first direction, thereby positioning the stator 112. This makes it easier to install the stator 112 onto the housing 111 at a suitable position, facilitating the installation of the stator 112.

[0064] In some embodiments, as shown in Figures 4, 5, and 6, the housing 111 includes a body 1111 and a cover 1112, and the body 1111 is provided with a second channel penetrating the body 1111 along a first direction.

[0065] The cover 1112 is connected to the body 1111. The cover 1112 is located on the side of the first opening 123 (as shown in Figures 7 and 8) opposite to the second opening and covers one end opening of the second channel.

[0066] It is understood that both the stator 112 and the mover 113 are located in the second channel, and at least a portion of the cam 12 and the output member 13 are located in the second channel.

[0067] With the above configuration, the cover 1112 can block one end opening of the second channel, thereby facilitating the placement of the stator 112 and the mover 113 within the second channel.

[0068] In some embodiments, as shown in FIG4, the housing 111 further includes a fork arm 1113, which is connected to the side of the body 1111 facing away from the cover 1112 and is adapted to connect to the wheel 20.

[0069] In this way, the main body 1111 can be connected to the wheel 20 through the fork arm 1113, so that the main body 1111, stator 112, mover 113 and other components do not need to be set to be large, thereby simplifying the structure of the actuator 1 and facilitating the spatial arrangement of the actuator 1.

[0070] In some embodiments, as shown in FIG4, the actuator 1 further includes a first bearing 16, which is connected between the cover 1112 and the cam 12.

[0071] With the above configuration, the housing 111 can support the cam 12 through the first bearing 16 to ensure the stability of the cam 12 installed in the housing 111, and can reduce the friction between the cam 12 and the cover 1112 during rotation through the first bearing 16 to extend the service life of the actuator 1.

[0072] In some examples, the first bearing 16 includes a first inner ring and a first outer ring, the first inner ring being connected to the rod 1311 (as shown in Figure 13), and the first outer ring being connected to the cam 12.

[0073] For example, the first outer ring is located at the first opening 123 and extends into the receiving cavity 122 (as shown in Figure 8). The rod body 1311 includes a mounting tube, the output member 13 passes through the mounting tube, and the mounting tube extends into the first inner ring.

[0074] Based on this, in some embodiments, as shown in FIG4, the actuator 1 further includes a second bearing 17, which is connected between the fork arm 1113 and the cam 12.

[0075] With the above configuration, the housing 111 can also support the cam 12 through the second bearing 17, thereby improving the stability of the cam 12 installed in the housing 111 and reducing the friction between the cam 12 and the fork arm 1113 during rotation through the second bearing, thus further extending the service life of the actuator 1.

[0076] It should be noted that the cover 1112 is provided with a mounting hole that extends along the first direction, and the output component 13 passes through the mounting hole so that the output component 13 can be connected to the vehicle body 10 to realize the adjustment of the height of the vehicle body 10 by the actuator 1. For example, a mounting hole is formed inside the mounting tube.

[0077] In some examples, actuator 1 also includes a third bearing disposed within the mounting tube and connected to cover 1112. The third bearing is sleeved on output component 13 for supporting and lubricating output component 13. This reduces friction between output component 13 and cover 1112 via the third bearing.

[0078] Based on the above, during the process of one of the cam 12 and the output component 13 rotating to drive the other of the cam 12 and the output component 13 to move linearly, friction will occur between the cam 12 and the output component 13. As the cam 12 and the output component 13 are used for a long time, the wear of the cam 12 and the output component 13 will become more and more serious.

[0079] Therefore, in order to reduce friction between the cam 12 and the output member 13 during relative movement, in some embodiments, as shown in Figures 7 and 8, the cam 12 is provided with a receiving cavity 122. The receiving cavity 122 is used to store a lubricating medium to achieve lubrication between the cam 12 and the output member 13.

[0080] With the above configuration, during the rotational movement of one of the cam 12 and the output component 13 to drive the linear movement of the other of the cam 12 and the output component 13, the lubricating medium in the receiving cavity 122 can lubricate the cam 12 and the output component 13, thereby reducing the wear of the cam 12 and the output component 13 and extending the service life of the cam.

[0081] For example, when one of the cam 12 and the output member 13 rotates, it can deliver the lubricating medium to the gap between the cam 12 and the output member 13.

[0082] In this way, as one of the cam 12 and the output member 13 rotates, the cam 12 and the output member 13 can drive the lubricating medium to move in the gap between the cam 12 and the output member 13, thereby flowing to the entire gap between the cam 12 and the output member 13, so as to improve the lubrication effect of the lubricating medium on the cam 12 and the output member 13.

[0083] In some embodiments, as shown in Figures 7 and 8, the cam 12 is provided with a guide groove 121. The guide groove 121 is recessed radially along the cam 12 and spirals upward along the axial direction of the cam 12. The guide groove 121 communicates with the receiving cavity 122.

[0084] In some examples, as shown in Figure 8, the guide groove 121 is recessed radially from the inner wall surface of the receiving cavity 122 along the cam 12.

[0085] At least a portion of the output element 13 is located within the guide groove 121 and is connected in conjunction with the cam 12 to convert the rotational motion of one of the cam 12 and the output element 13 into the linear motion of the other.

[0086] With the above configuration, since the receiving cavity 122 is connected to the guide groove 121, the lubricating medium in the receiving cavity 122 can be delivered to the guide groove 121, thereby lubricating the cam 12 and the output component 13, thereby reducing the wear of the cam 12 and the output component 13 and extending the service life of the actuator 1.

[0087] Furthermore, by providing the receiving cavity 122, the friction between the cam 12 and the output member 13 can be reduced, thus enabling the cam 12 and the output member 13 to move more smoothly relative to each other and improving the performance of the actuator 1.

[0088] For example, the lubricating medium can be a solid, such as grease, or a liquid, such as lubricating oil.

[0089] In some embodiments, the actuator 1 further includes a first oil seal connected between the body 1111 and the cam 12 for sealing the gap between the body 1111 and the cam 12. The first oil seal is located on the side of the stator 112 and the mover 113 facing the first opening 123 (as shown in Figures 7 and 8).

[0090] With the above configuration, the lubricating medium in the receiving cavity 122, after leaking out from the first opening 123, cannot move to the stator 112 and the mover 113, thereby achieving the storage of the lubricating medium in the receiving cavity 122, avoiding the lubricating medium from affecting the stator 112 and the mover 113, and ensuring the normal use of the stator 112 and the mover 113.

[0091] In some embodiments, the actuator 1 further includes a second oil seal disposed inside the mounting tube to seal the gap between the mounting tube and the output component 13. In this way, after the lubricating medium leaks out from the first opening 123, it cannot leak out from the cover 1112 to the outside of the housing 111, thus further ensuring the storage effect of the lubricating medium.

[0092] For example, the receiving cavity 122 can be located on one side of the guide groove 121 in a direction perpendicular to the first direction, and the receiving cavity 122 and the guide groove 121 are connected by a channel.

[0093] In some embodiments, as shown in Figures 8 to 10, the guide groove 121 is recessed from the inner wall surface of the receiving cavity 122 toward the outer wall surface of the cam 12, and the cam 12 is also provided with a first opening 123 communicating with the receiving cavity 122, and the output member 13 passes through the first opening 123.

[0094] With the above configuration, a portion of the output component 13 can extend out of the receiving cavity 122 through the first opening 123 to connect with the vehicle body 10, and another portion of the output component 13 can be disposed in the receiving cavity 122 and cooperate with the guide groove 121 on the inner wall of the receiving cavity 122 to convert the rotational motion of one of the cam 12 and the output component 13 into the linear motion of the other.

[0095] Since the guide groove 121 is recessed from the inner wall of the receiving cavity 122 toward the outer wall of the cam 12, the output component 13 can directly contact the lubricating medium in the receiving cavity 122, thereby delivering the lubricating medium to the gap between the cam 12 and the output component 13 during the movement, which can further improve the lubrication effect of the lubricating medium on the cam 12 and the output component 13.

[0096] Furthermore, there is no need to separately provide a receiving cavity 122 within the cam 12, which reduces the space required for the guide groove 121 and the receiving cavity 122 in the direction perpendicular to the first direction, thereby reducing the volume of the cam 12 and facilitating the spatial arrangement of the cam 12.

[0097] In some embodiments, the cam 12 is movable relative to the output member 13 between a first position and a second position.

[0098] When the cam 12 is in the first position, the length of the actuator 1 is the first length; when the cam 12 is in the second position, the length of the actuator 1 is the second length, and the first length is less than the second length.

[0099] When the cam 12 is in the first position, the output element is at least partially immersed in the lubricating medium.

[0100] In some examples, when the cam 12 is in the first position, the lubricating medium fills the receiving cavity 122.

[0101] It is understandable that during the movement of vehicle 100, if cam 12 is in the first position, actuator 1 is in the compression limit position, at which point the distance between body 10 and wheel 20 is the smallest. If cam 12 is in the second position, actuator 1 is in the extension limit position, at which point the distance between body 10 and wheel 20 is the largest.

[0102] With the above settings, when the cam 12 is in the first position, the volume of the output component 13 extending into the receiving cavity 122 reaches its maximum value, and the lubricating medium fills the receiving cavity 122. This ensures that there is enough lubricating medium in the receiving cavity 122 to lubricate the cam 12 and the output component 13, so as to ensure the lubrication effect of the lubricating medium on the cam 12 and the output component 13.

[0103] It should be noted that when the cam 12 is in the first position, the lubricating medium fills the receiving cavity 122. At this time, the volume of the lubricating medium is the maximum value that the receiving cavity 122 can hold. If the volume of the lubricating medium continues to increase, the lubricating medium will overflow the receiving cavity 122 when the cam 12 is in the first position.

[0104] In some embodiments, as shown in FIG8, the cam 12 includes a main body 124 and a blocking part 125. The main body 124 is provided with a first channel having a first opening 123 and a second opening. The first opening 123 and the second opening are respectively located at both ends of the first channel in a first direction.

[0105] The sealing portion 125 covers the second opening of the first channel and is connected to the main body portion 124 so that at least a portion of the first channel is formed as a receiving cavity 122.

[0106] With the above configuration, the sealing part 125 can block the second opening, thus facilitating the placement of lubricating medium within the receiving cavity for lubrication of the cam 12 and the output component. Furthermore, it prevents the lubricating medium from leaking out of the second opening, ensuring the receiving cavity 122's function of storing the lubricating medium.

[0107] For example, the main body 124 can be a columnar structure, such as a cylinder or a prism. The main body 124 can also be a frustum-shaped structure, such as a frustum of a cone or a frustum of a prism.

[0108] Some embodiments of this disclosure are illustrated by way of a cylindrical structure for the main body 124. The cylindrical structure facilitates the arrangement of the mover 113 around the cam 12, thereby facilitating the machining of the actuator 1. However, this should not be construed as a limitation on the present disclosure.

[0109] For ease of description, some embodiments of this disclosure will be described below using the example of cam 12 rotating and output component 13 moving linearly.

[0110] In some embodiments, as shown in Figures 8 and 11, the guide groove 121 extends helically along the axial direction of the cam 12. That is, the guide groove 121 spirals upward in a first direction, which is consistent with the direction of movement of the other of the cam 12 and the output member 13, and is also consistent with the axial direction of the cam 12.

[0111] With the above settings, during the rotation of the cam 12, since the output component 13 is connected to the guide groove 121, the inner wall of the guide groove 121 can apply a thrust to the output component 13, thereby pushing the output component 13 to move linearly along the first direction, realizing the motion conversion function of the actuator 1.

[0112] In some embodiments, as shown in Figures 12 to 14, the output member 13 includes a transmission member 131 and a follower member 132. The follower member 132 is connected to the transmission member 131, and at least a portion of the follower member 132 is accommodated in the guide groove 121.

[0113] With the above configuration, during the rotation of the cam 12, the inner wall of the guide groove 121 can apply a thrust to the follower 132, so that the follower 132 and the transmission member 131 move along the first direction.

[0114] By cooperating with the follower 132 and the guide groove 121, the machining accuracy of the cam 12 and the output component 13 can be reduced compared with structures such as ball screws, thereby facilitating the machining of the cam 12 and the output component 13, making the machining of the actuator 1 easier, and reducing the machining cost of the actuator 1.

[0115] In some embodiments, the number of guide slots 121 can be one or more.

[0116] When there are multiple guide slots 121, the multiple guide slots 121 satisfy N-fold symmetry. That is, one of the multiple guide slots 121 can coincide with another of the multiple guide slots 121 after rotating about the axis of the cam 12 by a preset angle α. The preset angle α satisfies: n1 is a positive integer less than the number of guide slots 121, and n2 is the number of guide slots 121.

[0117] By setting multiple guide slots 121, during the relative movement of the cam 12 and the output component 13, the multiple guide slots 121 can guide and limit the output component 13, thereby improving the stability of the relative movement of the cam 12 and the output component 13.

[0118] When there are multiple guide slots 121, there are also multiple follower components 132, with multiple follower components 132 respectively disposed in multiple guide slots 121.

[0119] In some embodiments, as shown in FIG10, the guide groove 121 includes a first guide groove 1211 and a second guide groove 1212, which are located on opposite sides of the axis of the cam 12. That is, the first guide groove 1211 and the second guide groove 1212 satisfy two-fold symmetry and are arranged opposite to each other.

[0120] The follower 132 includes a first follower 1321 and a second follower 1322. The first follower 1321 is disposed in the first guide groove 1211, and the second follower 1322 is disposed in the second guide groove 1212. The first follower 1321 and the second follower 1322 are respectively located on opposite sides of the axis of the cam 12.

[0121] With the above configuration, the first guide groove 1211 can apply a thrust to the first follower 1321, and the second guide groove 1212 can apply a thrust to the second follower 1322. Since the first guide groove 1211 and the second guide groove 1212 are arranged opposite to each other, and the first follower 1321 and the second follower 1322 are arranged opposite to each other, the output member 13 can be subjected to a more balanced force in the radial direction of the cam, so as to avoid the output member 13 tilting relative to the axis of the cam 12 and ensure the normal movement of the output member 13.

[0122] For example, the transmission component 131 can be a transmission block, transmission plate, etc.

[0123] For example, as shown in Figure 13, the transmission component 131 includes a rod 1311 and a connecting post 1312. The connecting post 1312 is connected to one side of the rod 1311 in the radial direction. The follower component 132 is connected to the connecting post 1312.

[0124] In this way, the thrust of the follower 132 on the inner wall of the guide groove 121 can be transmitted to the rod 1311 through the connecting column, thereby driving the rod 1311 to move in the first direction, so that the vehicle body 10 can be supported by the rod 1311.

[0125] In some embodiments, the connecting post 1312 and the rod 1311 are integrally formed. This increases the structural strength of the connecting post 1312 and the rod 1311, thereby improving the overall structural strength of the actuator 1.

[0126] In some embodiments, the follower includes a slider that is slidable along the guide groove 121.

[0127] In other embodiments, the follower includes a sliding post whose axial direction is aligned with the radial direction of the rod 1311.

[0128] In this way, the circumferential surface of the sliding column can contact the guide groove 121 and slide along the guide groove 121, thereby reducing the contact area between the follower and the guide groove 121, thus reducing the friction between the follower and the guide groove 121, further reducing the wear of the cam 12 and the output component 13, and extending the service life of the actuator 1.

[0129] Based on this, in some embodiments, as shown in FIG10, the transmission member 131 further includes a damping member 14, which is connected to the rod body 1311 and located in the receiving cavity 122.

[0130] With the above configuration, since the damping element 14 is located in the receiving cavity 122, there is resistance between the damping element 14 and the lubricating medium during the movement of the transmission element 131. Thus, when the transmission element 131 moves to the appropriate position, it can quickly stop moving due to the resistance of the damping element 14. This makes it easier to control the movement distance of the transmission element 131 relative to the cam 12 and improves the performance of the actuator 1.

[0131] In some embodiments, the damping member 14 slides against the inner wall surface of the receiving cavity 122.

[0132] In this way, the inner wall of the receiving cavity 122 can restrict the movement of the damping member 14 in a direction perpendicular to the first direction, thereby further improving the stability of the transmission member 131 during its movement.

[0133] In other embodiments, the damping element 14 is clearance-fitted with the inner wall surface of the receiving cavity 122.

[0134] In this way, there is a gap between the damping element 14 and the inner wall of the receiving cavity 122. This allows the transmission element 131 to stop moving quickly only by the resistance between the damping element 14 and the lubricating medium, thereby avoiding friction between the damping element 14 and the inner wall of the receiving cavity 122, reducing the wear of the damping element 14, and extending the service life of the damping element 14.

[0135] For example, the damping component 14 can be a damping block, damping strip, etc.

[0136] For example, the damping element 14 is a damping plate, and the thickness direction of the damping plate is consistent with the axial direction of the rod 1311.

[0137] Thus, during the movement of the transmission component 131, since the thickness direction of the damping plate is consistent with the axial direction of the rod 1311, the resistance of the lubricating medium on the damping plate is relatively large, which can ensure the damping effect of the damping component 14 on the transmission component 131.

[0138] In some embodiments, the damping member 14 is provided with a plurality of through holes, which pass through the damping member 14 along the axial direction of the rod 1311.

[0139] With the above settings, as the damping member 14 moves with the transmission member 131, the lubricating medium can move in multiple through holes. Thus, the resistance of the damping member 14 can be set according to the number and size of the through holes, so that the resistance of the damping plate during movement meets the needs of the transmission member 131, thereby facilitating the processing of the damping member 14.

[0140] For example, the material of the damping element 14 can be a rigid material, such as metal.

[0141] For example, the material of the damping element 14 can be a flexible material, such as rubber, plastic, silicone, etc.

[0142] In this way, when the damping element 14 moves with the transmission element 131, and the damping element 14 collides with the cam 12, the cam 12 and the damping element 14 can be prevented from being damaged because the material of the damping element 14 is a flexible material, thereby extending the service life of the cam 12 and the damping element 14.

[0143] Furthermore, compared to rigid materials, flexible materials are easier to mold, which facilitates the processing of damping component 14.

[0144] In some examples, the damper 14 is clearance-fitted with the cam 12 to further prevent damage from collision between the damper and the cam 12.

[0145] In some embodiments, as shown in Figures 4 and 13, the transmission member 131 further includes a limiting protrusion 133, which is connected to the rod 1311 and protrudes radially along the rod 1311.

[0146] The actuator 1 also includes a buffer 15, which is located on the side of the guide groove 121 facing the first opening 123. The buffer 15 is used to cooperate with the limiting protrusion 133 to buffer the transmission member 131.

[0147] For example, the cushioning pad can be a rubber pad, a plastic pad, etc.

[0148] With the above settings, before the cam 12 moves to the second position relative to the output component 13, the buffer pad can contact the limiting protrusion 133 to buffer the cam 12 and the output component 13, avoid excessive impact between the cam 12 and the output component 13, and ensure the normal use of the cam 12 and the output component 13.

[0149] In some examples, actuator 1 also includes bolts, and buffer 15 is fixed to cam 12 by bolts.

[0150] Extensive research has shown that by controlling the helix angle θ of the guide groove 121, the volume of the cam 12 can be kept within a small range, thereby reducing the space occupied by the cam 12.

[0151] In some embodiments, as shown in FIG8, the cam 12 is provided with a guide groove 121, which extends spirally along the axial direction of the cam 12. That is, the guide groove is a spiral groove.

[0152] The radius of cam 12 is r, and the helix angle of guide groove 121 is θ. The radius r of cam 12 is negatively correlated with tanθ. That is, the larger the helix angle θ of guide groove 121 (the larger tanθ), the smaller the radius r of cam 12, and the smaller the volume of cam 12.

[0153] In this way, the helix angle θ can be appropriately increased to reduce the radius of cam 12, thereby reducing the volume of cam 12 and the space occupied by cam 12.

[0154] It should be noted that the larger the helix angle θ of the guide groove 121, the larger the distance between two adjacent helical grooves in the guide groove 121 (i.e., the lead h of the cam 12). In this way, the radius of the cam 12 does not need to be set too large to meet the structural strength of the groove wall of the guide groove 121. Thus, the radius of the cam 12 can be reduced by appropriately increasing the helix angle θ, thereby reducing the volume of the cam 12.

[0155] Furthermore, when the cam 12 is used in the suspension assembly 30 of a vehicle, it is often limited by the distance between the body 10 and the wheel 20. Reducing the volume of the cam 12 can reduce the space occupied by the suspension assembly 30, so as to facilitate the arrangement of the suspension assembly 30 between the body 10 and the wheel 20.

[0156] In some embodiments, the cam 12 cooperates with the output member 13 to move relative to the output member 13 along the axial direction of the cam 12, thereby outputting a thrust F. That is, the drive member 11 drives one of the cam 12 and the output member 13 to rotate, thereby causing the other of the cam 12 and the output member 13 to move along the axial direction of the cam 12, thereby outputting a thrust F to the vehicle body.

[0157] The relationship between the radius r of cam 12 and the helix angle θ of guide groove 121 is as follows:

[0158] M is the input torque that drives the cam 12 to rotate. When the drive component 11 is directly connected to the cam 12, the input torque that drives the cam 12 to rotate is the torque output by the drive component 11.

[0159] n is a coefficient, where 0.9 ≤ n ≤ 1.1. Since there may be some measurement errors in the actual measurement of the input torque M, output thrust F, helix angle θ of the guide groove 121, and cam radius r, the coefficient n is introduced to correct these errors, making the relationship between the input torque M, output thrust F, helix angle θ of the guide groove 121, and cam radius r in the above formulas more accurate. For example, n can be 0.9, 0.92, 0.95, 1, 1.02, 1.05, 1.08, or 1.1, etc.

[0160] In an actuator equipped with a cam 12 and an output component 13, regardless of the type of guide groove used in the cam 12, the radius r of the cam 12, the helix angle θ of the guide groove on the cam 12, the thrust F output by the actuator, and the input torque M that drives the cam 12 to rotate, these four parameters satisfy the following relationship:

[0161] n is a coefficient, where 0.9 ≤ n ≤ 1.1.

[0162] It should be noted that during the relative movement of cam 12 and output component 13, there is a relative rotation between cam 12 and output component 13. Therefore, whether the drive component 11 drives cam 12 to rotate or drives output component 13 to rotate, cam 12 rotates relative to output component 13. When the drive component 11 directly drives cam 12, the input torque M that drives cam 12 to rotate is the torque of drive component 11.

[0163] As can be seen from the above formula, when the thrust F output by the cam 12 and the output component 13 meets the design requirements, and when the driving component that drives the cam 12 to rotate is determined (i.e., the input torque M that drives the cam 12 to rotate is determined), the radius of the cam 12 can be reduced by increasing the helix angle θ of the guide groove 121, thereby reducing the volume of the cam 12, reducing the space occupied by the cam 12, and facilitating the miniaturization of the suspension assembly.

[0164] Furthermore, while ensuring the thrust F output by the cam 12 and the output component 13, the radius of the cam 12 and the helix angle θ of the guide groove 121 can be appropriately reduced, while satisfying the structural strength requirements of the cam. This reduces the input torque M driving the cam 12 to rotate, i.e., reduces the torque of the drive component 11, thereby improving the working efficiency of the drive component 11 and preventing damage to the drive component 11 due to excessive torque. The reduced torque of the drive component 11 also allows for a reduction in the rotor volume of the drive component 11, thus reducing the size of the drive component 11 and the space it occupies, further facilitating the miniaturization of the suspension assembly.

[0165] Furthermore, given a fixed input torque M for driving the cam 12 to rotate, the radius of the cam 12 and the helix angle θ of the guide groove 121 can be appropriately reduced while satisfying the structural strength of the cam, so as to increase the thrust F output by the cam 12 and the output component 13. This allows the suspension assembly to be suitable for more working conditions, such as roads with large undulations, off-road roads, etc.

[0166] In summary, by reasonably adjusting the relationship between the input torque M driving the cam 12, the helix angle θ of the guide groove 121, and the radius r of the cam 12, the thrust F output by the cam 12 and the output component 13 can be ensured. Furthermore, the input torque M driving the cam 12, the helix angle θ of the guide groove 121, and the radius r of the cam 12 can all be kept within a suitable range. This avoids the cam 12 becoming too large and occupying too much space, and also avoids the input torque driving the cam 12 becoming too large and affecting the drive component 11.

[0167] As shown in Figure 15, Figure 15 is a schematic diagram of the force analysis during the relative motion of cam 12 and output component 13. In order to make cam 12 and output component 13 more stable during the relative motion, it is necessary to cancel out the component f1 of the driving force F1 that drives cam 12 to rotate and the component f2 of the thrust F output by cam 12 and output component 13, that is, f1 = f2.

[0168] and Therefore, from f1 = f2, we can conclude that: Therefore, we can conclude that: Right now In some embodiments, the helix angle θ of the guide groove 121 is less than or equal to 35°. For example, the helix angle θ can be 5°, 8°, 10°, 15°, 20°, 25°, 28°, 30°, 32°, 35°, etc.

[0169] The maximum axial travel of cam 12 relative to output component 13 is usually limited by the distance between the vehicle body and the wheel. If the helix angle θ is greater than 35°, the distance between two adjacent helical grooves of guide groove 121 will be relatively large. That is, the relative displacement in the axial direction of cam 12 and output component 13 is relatively large when they rotate one revolution. Since the maximum axial travel of cam 12 relative to output component 13 is limited, if we want to control the relative displacement of cam 12 and output component 13 to be small, the relative rotation angle of cam 12 and output component 13 needs to be small. This is not conducive to controlling the relative displacement of cam 12 and output component 13 in the axial direction, thus affecting the performance of the suspension assembly.

[0170] Furthermore, if the helix angle θ is greater than 35°, and the radius of cam 12 remains unchanged, and the thrust F output by cam 12 and output component 13 is sufficient, the input torque M that drives cam 12 to rotate may be large, resulting in a large size of drive component 11, which is not conducive to the miniaturization of suspension components and the arrangement of suspension components between the vehicle body and the wheels.

[0171] Furthermore, if the helix angle θ is greater than 35°, while keeping the radius of cam 12 constant and the input torque M driving cam 12 to rotate constant, the larger helix angle will result in a smaller thrust F output by cam 12 and output component 13, which will lead to insufficient thrust of the suspension assembly on the vehicle body and affect the performance of the suspension assembly.

[0172] Therefore, setting the helix angle θ of the guide groove 121 to a range of less than or equal to 35° facilitates the control of the relative displacement of the cam 12 and the output component 13, and makes it easier to ensure the thrust of the suspension assembly on the vehicle body, thereby improving the performance of the suspension assembly. In addition, it also makes it easier to set the drive component 11 to be smaller, so as to facilitate the arrangement of the suspension assembly between the vehicle body and the wheel.

[0173] In some embodiments, the helix angle θ of the guide groove 121 is less than or equal to 25°. For example, the helix angle θ can be 5°, 8°, 12°, 18°, 20°, 22°, 25°, etc.

[0174] When the helix angle is greater than 25°, for vehicles with high control precision of suspension components, the distance between two adjacent helical grooves of the guide groove 121 is still relatively large. That is, when the cam 12 and the output component 13 rotate one revolution relative to each other, the relative displacement in the axial direction is still relatively large. This is not conducive to precise control of the cam 12 and the output component 13 when the relative displacement in the axial direction of the cam 12 is small, and affects the performance of the suspension components.

[0175] Therefore, setting the helix angle to less than or equal to 25° allows the suspension components to be applied to more vehicle models and facilitates precise control of the relative displacement of the cam 12 and the output component 13, further improving the performance of the suspension components.

[0176] Furthermore, by setting the helix angle to less than or equal to 25°, which is a reduction compared to the range of less than or equal to 35°, and keeping the radius of cam 12 constant, and ensuring that the thrust F output by cam 12 and output member 13 is sufficient, the input torque M driving cam 12 to rotate can be reduced, thereby reducing the volume of drive member 11, which facilitates the miniaturization of suspension components and the arrangement of suspension components between the vehicle body and wheels.

[0177] Furthermore, the helix angle is reduced compared to the range of less than or equal to 35°. While keeping the radius of cam 12 constant and the input torque M driving cam 12 to rotate constant, the thrust F output by cam 12 and output component 13 will increase. This can improve the thrust of the suspension assembly on the vehicle body and improve the performance of the suspension assembly.

[0178] In summary, the helix angle θ of the guide groove 121 is less than or equal to 25°. However, the helix angle θ cannot be too small. For example, the helix angle θ of the guide groove 121 can be greater than or equal to 13° and less than or equal to 25°. For example, the helix angle θ of the guide groove 121 can be 13°, 15°, 18°, 20°, 22°, 25°, etc.

[0179] If the helix angle θ of the guide groove 121 is less than 13°, the spacing between two adjacent spiral grooves in the guide groove 121 will be too small, which will result in a smaller wall thickness between the groove walls of the two adjacent spiral grooves. This will lead to lower structural strength of the groove walls. Since the weight of the vehicle body is usually large, the groove walls of the spiral grooves may deform when the suspension components push the vehicle body, thus affecting the performance of the suspension.

[0180] Furthermore, if the helix angle θ of the guide groove 121 is less than 13°, the helix angle is too small. If the radius of the cam 12 remains unchanged, the structural strength of the cam 12 may be low, leading to deformation of the cam during operation. Moreover, if the input torque M driving the cam 12 and the thrust F output by the cam 12 and the output component 13 remain constant, the radius of the cam 12 may be large, resulting in a larger volume of the cam 12. This leads to a larger space occupied by the suspension assembly, which is detrimental to the arrangement of the suspension assembly between the vehicle body and the wheels.

[0181] Therefore, by setting the helix angle θ of the guide groove 121 to a range greater than or equal to 13°, the structural strength of the cam 12 can meet the requirements of the suspension assembly, and the volume of the cam 12 can be avoided to make the suspension assembly smaller and facilitate the arrangement of the suspension assembly between the vehicle body and the wheel.

[0182] It should be noted that, as shown in Figure 16, which is a schematic diagram of the relationship between the developed line of the cam 12's contour and the helix angle, the developed line of the guide groove 121's contour is L. The line segment with the same height as the guide groove 121's contour in the axial direction of the cam 12 (i.e., the maximum stroke of the cam 12 relative to the output component in the axial direction of the cam 12) is the stroke line H. One end of H is connected to one end of L, and L is perpendicular to H. Then, the other end of H is connected to the other end of L to form a hypotenuse C. The angle between the hypotenuse C and the developed line L is the helix angle of the guide groove 121, which is also the pressure angle of the guide groove 121.

[0183] As shown in Figures 17, 18, and 19, Figure 17 is a structural schematic diagram of a cam provided in some embodiments of this disclosure, retaining only the guide groove and the circumferential groove wall forming the guide groove. Figure 18 is a top view of the cam shown in Figure 17, and Figure 19 is a cross-sectional view of the cam shown in Figure 18 along line CC. The parameters such as input torque M, output thrust F, helix angle θ of the guide groove 121, and radius r of the cam are defined and measured using the example of a cam 12 with one guide groove in Figures 17 to 19. When the cam 12 has multiple guide grooves 121, since the multiple guide grooves satisfy N-sufficiency symmetry, the definition and measurement of the above parameters for the multiple guide grooves are the same as those for the single guide groove, and will not be repeated here.

[0184] The radius r of the cam refers to the distance from the cam axis Q to the midpoint of the guide groove. Along the radial direction of the cam, the guide groove 121 has opposing third openings 121A and bottom wall surfaces 121B. The midpoint of the guide groove is the position where the distance L1 between the guide groove 121 and the third opening 121A is equal to the distance L2 between the guide groove 121 and the bottom wall surface 121B. The radius r of the cam is the same as the r shown in Figure 19.

[0185] The lead h of cam 12 refers to the height h that cam 12 moves axially relative to output member 13 when cam 12 rotates one revolution (360°) relative to output member 13, as shown in Figure 19. The cam lead is measured as follows: Mark a point on cam 12, designated as the first point, for example, the first point being either the upper limit position (position M1 shown in Figures 18 and 19) or the lower limit position (position M2 shown in Figures 18 and 19). Then, rotate cam 12 one revolution relative to output member 13. That is, when the projection of the first point on the cross-section of cam 12 rotates one revolution from the starting position and returns to the starting position, measure the height that the first point moves axially on cam 12. The cross-section of cam 12 is perpendicular to its axis.

[0186] The input torque M that drives the cam 12 can be obtained by reading the nameplate of the drive component 11 in the actuator (e.g., the drive component can be a drive motor). Generally, the torque on the nameplate of the drive component 11 is greater than the aforementioned input torque M value because the drive component usually has a safety factor, requiring the drive component to exceed the minimum output requirement of the system. Typically, the safety factor is taken as 1.2, that is, the input torque M is equal to the torque reading on the nameplate of the drive component 11 divided by 1.2.

[0187] The output thrust F of the cam 12 and output component 13 refers to the external thrust of the actuator, such as the thrust exerted on the vehicle body when the actuator is used in a vehicle. The measurement method is as follows: Fix both ends of the actuator, i.e., fix the drive component 11, but allow the mover of the drive component to rotate, and fix the output component 13. Power is applied to the drive component 11, and according to the requirements on the nameplate of the drive component 11, the rated current and peak current are applied respectively. The external output force of the actuator under stall conditions is measured; this external output force is the output thrust F. The output thrust F obtained by applying the rated current to the drive component 11 is the rated thrust. The formula is then used... The input torque M is the rated torque. The output thrust F obtained by applying the peak current to the drive component 11 is the peak thrust, and the formula is used in this case. The input torque M in the figure uses the peak torque.

[0188] In some embodiments, the outline of the guide groove 121 is a linear curve or a non-linear curve.

[0189] When the outline of the guide groove 121 is a linear curve, the parameters of the outline of the guide groove 121 can satisfy a first-order polynomial.

[0190] When the outline of the guide groove 121 is a non-linear curve, the parameters of the outline of the guide groove 121 can satisfy quadratic polynomial, multiple polynomial, cosine acceleration motion trajectory or sine acceleration motion trajectory, etc.

[0191] In some examples, the outline of the guide groove 121 is a first-order polynomial.

[0192] As shown in Figure 20, the outline parameters of the guide groove 121 satisfy the parameters of a first-order polynomial, a second-order polynomial, a cosine acceleration motion trajectory, and a sine acceleration motion trajectory, respectively. Figure 20 shows that when the outline parameters of the guide groove 121 satisfy a first-order polynomial, the outline is a straight line. In this case, the helix angle of the guide groove 121 remains constant. Thus, when controlling the rotation of the cam 12 and when controlling the cam 12 in conjunction with other components (such as the output component 13), the number of control variables can be reduced, thereby facilitating the control of the cam 12.

[0193] As shown in Figure 20, when the parameters of the outline of the guide groove 121 satisfy a first-order polynomial, the motion law between the cam 12 and the output component 13 is constant-speed motion. This is suitable for scenarios with low speed and light load. The helix angle is constant, and motion control is relatively easy.

[0194] When the parameters of the contour line of the guide groove 121 satisfy a quadratic polynomial, the motion between the cam 12 and the output component 13 is either constant acceleration or constant deceleration, i.e., parabolic motion as shown in Figure 20. In this case, in applicable scenarios, the speed can be the same as when the contour line of the guide groove 121 is a first-order polynomial, or slightly higher. Furthermore, the load is lighter, the helix angle varies, and motion control is more difficult.

[0195] When the parameters of the contour line of the guide groove 121 satisfy cosine acceleration, the motion between the cam 12 and the output component 13 is simple harmonic motion. In this case, in applicable scenarios, the speed can be the same as when the contour line of the guide groove 121 is a first-order polynomial, or slightly higher. Furthermore, the load can be the same as when the contour line of the guide groove 121 is a first-order polynomial, or slightly higher. However, the helix angle varies, making motion control more difficult.

[0196] When the contour parameters of the guide groove 121 satisfy sinusoidal acceleration, the motion between the cam 12 and the output component 13 is cycloidal. In this case, in applicable scenarios, the velocity is higher than the velocity when the contour of the guide groove 121 is subjected to first-order polynomial, second-order polynomial, and cosine acceleration. The helix angle varies, and the variation is significant, making motion control relatively difficult.

[0197] Additionally, please refer to Tables 1 and 2 below. Table 1 shows a comparison of the parameters of the maximum stroke of the guide groove 121 (the height of the guide groove 121's contour line in the axial direction of the cam 12), the diameter of the cam 12, the number of helices in the guide groove 121, the torque of the drive member 11 (i.e., the input torque M that drives the cam 12 to rotate), and the helix angle θ (i.e., the pressure angle) of the guide groove 121 when the contour line of the guide groove 121 satisfies a first-order polynomial. Table 2 shows a comparison of the parameters of the maximum stroke of the guide groove 121, the diameter of the cam 12, the number of helices in the guide groove 121, the torque of the drive member 11, and the helix angle of the guide groove 121 when the contour line of the guide groove 121 satisfies a sine and cosine acceleration motion trajectory.

[0198] A comparison of Tables 1 and 2 shows that, with the same maximum stroke of the guide groove 121 and the same diameter of the cam 12, the input torque required to drive the cam 12 is smaller when the parameters of the guide groove 121's contour line satisfy a first-order polynomial. In other words, when the parameters of the guide groove 121's contour line satisfy a first-order polynomial, the input torque M required to drive the cam 12 can be reduced, thus preventing damage to the drive component 11 due to excessive torque.

[0199] Table 1

[0200] Table 2

[0201] It should be noted that the maximum stroke of the guide groove 121 refers to the maximum axial stroke of the cam 12 relative to the output component during the relative motion between the cam 12 and the output component.

[0202] Please refer to Table 1. As can be seen from Table 1, when the helix angle θ of the guide groove 121 is greater than or equal to 13° and less than or equal to 25°, the torque of the drive component 11 is between 76 Nm and 90 Nm. That is, the torque of the drive component 11 is within a relatively small range. Therefore, when controlling the helix angle θ of the guide groove 121 to be greater than or equal to 13° and less than or equal to 25°, the torque of the drive component 11 that drives the cam 12 can be controlled within a small range to avoid damage to the drive component 11.

[0203] In some embodiments, the input torque M driving the cam 12 to rotate is positively correlated with the helix angle θ. For example, referring to Table 1, when the outer diameter of the cam 12 is 70 mm, the helix angle of the guide groove 121 increases from 19.99° to 22.26°, and then to 23°, and the torque of the drive member 11 driving the cam 12 to rotate also increases from 76.39 Nm to 85.94 Nm, and then to 89.13 Nm. Furthermore, when the outer diameter of the cam 12 is 90 mm and 110 mm, the trend of the input torque M driving the cam 12 to rotate is consistent with the change trend of the helix angle of the guide groove 121.

[0204] In this way, the input torque M of the drive cam 12 can be adjusted by adjusting the size of the helix angle θ, so as to minimize the torque of the drive component 11 while meeting the matching requirements of the guide groove 121 and the output component, so as to avoid damage to the drive component 11 and reduce the size of the drive component 11.

[0205] In some embodiments, the outline of the guide groove 121 is a linear curve, and the relationship between the lead h of the cam 12, the output thrust F of the cam 12 and the output member 13, and the input torque M that drives the cam 12 and the output member 13 to rotate relative to each other is as follows:

[0206] n is a coefficient, where 0.9 ≤ n ≤ 1.1.

[0207] It should be noted that the height of the stroke line H in Figure 16 is the cam's lead h multiplied by the number of turns m of the spiral groove 121, and the unfolded line L in Figure 16 is the length of the outline of the guide groove 121, that is, the unfolded line L is the circumference B of the circle formed by the projection of the outline of the guide groove 121 onto the cross section of the cam 12 multiplied by the number of turns m of the spiral groove 121.

[0208] and and therefore, Furthermore, we can obtain:

[0209] As can be seen from the above formula, if the structural strength of cam 12 meets the requirements and the thrust F output by cam 12 and output component 13 meets the design requirements, the input torque M can be reduced by reducing the lead h of the cam, that is, the torque of drive component 11 can be reduced, so as to reduce the space occupied by drive component 11 and avoid the drive component 11 from being damaged due to excessive torque.

[0210] Furthermore, if the structural strength of cam 12 meets the requirements and the input torque M driving cam 12 to rotate is constant, the thrust F output by cam 12 and output component 13 can be increased by reducing the lead h of cam 12, so that the suspension assembly can be adapted to more working conditions.

[0211] In some embodiments, the contour line of the guide groove 121 is a non-linear curve. In this case, the relationship between the target lead h1 of the cam 12, the output thrust F of the cam 12 and the output member 13, and the input torque M that drives the relative rotation of the cam 12 and the output member 13 is as follows:

[0212] Where h1 is the height by which cam 12 moves axially relative to output component 13 when the rotation angle φ between cam 12 and output component 13 is φ, and p is the coefficient of rotation angle φ relative to one revolution (360°), i.e.

[0213] It should be noted that, because the contour line of the guide groove 121 is a non-linear curve, the lead of the cam may not be equal for each revolution of the cam relative to the output component 13. Therefore, the rotation angle φ of the cam 12 relative to the output component 13 is introduced to calculate the target lead h1 of the cam 12. For example, Substitute the formula You can get

[0214] In some embodiments, the guide groove has a first extreme position, a second extreme position, and an intermediate position between the first extreme position and the second extreme position; the helix angle of the guide groove at the intermediate position is θ1, the helix angle of the guide groove at the first extreme position is θ2, and the helix angle of the guide groove at the second extreme position is θ3; wherein, θ1≥θ2; or, θ1≥θ3; or, θ1≥θ2 and θ1≥θ3.

[0215] It should be noted that the first limit position is the position of one end of the guide groove 121 in the axial direction of the cam 12. For example, when the cam 12 is in the first position (i.e. the compression limit position of the actuator 1), the follower 132 is in the first limit position of the guide groove 121.

[0216] The second limit position is the position of the other end of the guide groove 121 in the axial direction of the cam 12. For example, when the cam 12 is in the second position (i.e., the extension limit position of the actuator 1), the follower 132 is in the second limit position of the guide groove 121.

[0217] When the outline of the guide groove 121 is a linear curve, θ1 = θ2, and θ1 = θ3.

[0218] When the outline of the guide groove 121 is a linear curve, θ1 > θ2; or θ1 > θ3; or θ1 ≥ θ2 and θ1 ≥ θ3. That is, the distance between two adjacent spiral grooves at the middle position of the guide groove 121 is greater than the distance between two adjacent spiral grooves at the first extreme position of the guide groove 121; or, the distance between two adjacent spiral grooves at the middle position of the guide groove 121 is greater than the distance between two adjacent spiral grooves at the second extreme position of the guide groove 121; or, the distance between two adjacent spiral grooves at the middle position of the guide groove 121 is greater than the distance between two adjacent spiral grooves at the first extreme position of the guide groove 121, and the distance between two adjacent spiral grooves at the second extreme position of the guide groove 121.

[0219] Since the follower 132 typically decelerates when it moves to the first or second limit position within the guide groove 121 to facilitate reversing or stopping, high precision is required in controlling the axial displacement of the follower 132 relative to the guide groove 121 on the cam 12. Therefore, by setting θ1 to be greater than or equal to at least one of θ2 or θ3, more precise control can be achieved when the follower 132 moves to the first or second limit position within the guide groove 121, allowing for smoother reversing or stopping and improving the performance of the suspension assembly.

[0220] In some embodiments, the diameter of the cam 12 is greater than or equal to 70 mm and less than or equal to 110 mm. For example, the diameter of the cam 12 can be 70 mm, 75 mm, 80 mm, 85 mm, 90 mm, 95 mm, 100 mm, 105 mm, 110 mm, etc.

[0221] If the diameter of cam 12 is too large, for example, if the diameter of cam 12 is greater than 110mm, it will result in cam 12 occupying a large space, which in turn will result in the suspension components occupying a large space, which is not conducive to the arrangement of the suspension components between the vehicle body and the wheels.

[0222] Furthermore, if the diameter of cam 12 is too large, in order to ensure that the thrust F output by cam 12 and output component 13 is sufficient while keeping the helix angle θ constant, the input torque M required to drive cam 12 to rotate may be large. This would require a large torque for drive component 11, which would lead to increased energy consumption and increased volume of drive component 11.

[0223] If the diameter of cam 12 is too small, for example, less than 70mm, the structural strength of cam 12 will be low. As a result, when the suspension assembly pushes the vehicle body, cam 12 may not be able to support the weight of the vehicle body and may deform, thus affecting the performance of the rotating assembly.

[0224] Furthermore, if the diameter of cam 12 is too small, in order to ensure that the thrust F output by cam 12 and output component 13 is sufficient while keeping the input torque M that drives cam 12 to rotate constant, the helix angle θ of guide groove 121 may need to be large. This may result in poor control accuracy of the relative displacement of cam 12 and output component 13 in the axial direction of cam 12, which is not conducive to improving the performance of suspension.

[0225] Therefore, controlling the diameter of cam 12 within the range of 70mm to 110mm can prevent the outer diameter of cam 12 from being too small, which would affect the structural strength of cam 12, and also prevent the control accuracy of the relative displacement between cam 12 and output component 13 in the axial direction of cam 12 from being too small. Furthermore, it can also prevent the outer diameter of cam 12 from being too large, which would result in a larger volume of cam 12 and a larger torque and volume of drive component 11, thus ensuring the structural strength of cam 12, facilitating the miniaturization of suspension components, and improving the performance of suspension components.

[0226] In some embodiments, the input torque M for driving the cam 12 to rotate satisfies: 70 Nm ≤ M ≤ 90 Nm. For example, the input torque M for driving the cam 12 to rotate can be 70 Nm, 75 Nm, 80 Nm, 85 Nm, 90 Nm, etc.

[0227] If the input torque M that drives the cam 12 to rotate is too large, for example, if the input torque M is greater than 90 Nm, it will lead to an increase in the energy consumption of the drive component 11, and may cause the drive component 11 to be damaged due to excessive torque. It may also cause the size of the drive component to increase, affecting the arrangement of the suspension components between the vehicle body and the wheels.

[0228] Furthermore, if the input torque M driving the cam 12 to rotate is too large, and the thrust F output by the cam 12 and the output component 13 remains constant, it may result in a larger radius r of the cam 12, leading to a larger volume of the cam 12, which is not conducive to the miniaturization of the suspension assembly. It may also result in a larger helix angle θ of the guide groove 121, which is not conducive to the precise control of the relative displacement between the cam 12 and the output component 13.

[0229] If the input torque M that drives the cam 12 to rotate is too small, for example, if the input torque M is less than 70 Nm, then with the radius r of the cam 12 and the helix angle θ of the guide groove 121 remaining unchanged, the thrust F output by the cam 12 and the output component 13 will be small, which will not be able to meet the thrust requirements of the suspension assembly to the vehicle body and will affect the performance of the suspension assembly.

[0230] Furthermore, if the input torque M driving the cam 12 to rotate is too small, and the thrust F output by the cam 12 and the output component 13 remains constant, the radius r of the cam 12 may be smaller, affecting the structural strength of the cam 12. It may also result in a smaller helix angle θ of the guide groove 121, affecting the structural strength of the groove wall of the helical groove, thereby affecting the structural strength of the cam 12.

[0231] Therefore, setting the input torque M for driving the cam 12 to rotate within the range of 70mm to 90mm can prevent the input torque of driving the cam 12 from being too small to meet the thrust requirements of the suspension assembly on the vehicle body, and also prevent the torque of the drive component 11 from being too small to affect the structural strength of the cam 12. Furthermore, it can also prevent the input torque of driving the cam 12 from being too large, which would increase the size of the suspension assembly, and also prevent the input torque of driving the cam 12 from being too large, which would affect the performance of the suspension assembly.

[0232] In some embodiments, along the axial direction of the cam 12, the height of the outline of the guide groove 121 in the axial direction of the cam 12 is greater than or equal to 90 mm and less than or equal to 120 mm. That is, the maximum stroke of the guide groove 121 is greater than or equal to 90 mm and less than or equal to 120 mm. For example, the height of the outline of the guide groove 121 in the axial direction of the cam 12 can be 90 mm, 95 mm, 100 mm, 105 mm, 110 mm, 115 mm, 120 mm, etc.

[0233] If the height of the guide groove 121's outline in the axial direction of the cam 12 is greater than 120mm, the suspension assembly may be unable to be positioned due to limitations in the distance between the vehicle body and the wheels. If the height of the guide groove 121's outline in the axial direction of the cam 12 is less than 90mm, the maximum travel of the cam 12 relative to the output member 13 in the axial direction of the cam 12 will be insufficient, causing the suspension assembly to be unable to adapt to some operating conditions with large adjustment ranges, thus affecting the performance of the suspension assembly.

[0234] By making the height of the guide groove 121 in the axial direction of the cam 12 greater than or equal to 90 mm and less than or equal to 120 mm, the maximum stroke of the cam 12 relative to the output member 13 can be satisfied while avoiding the excessive length of the cam 12 in its axial direction, thereby reducing the space occupied by the cam 12 in its axial direction and further facilitating the miniaturization of the actuator.

[0235] The above are merely specific embodiments of this disclosure, but the scope of protection of this disclosure is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in this disclosure should be included within the scope of protection of this disclosure. Therefore, the scope of protection of this disclosure should be determined by the scope of the claims.

Claims

1. A cam (12), wherein, The cam (12) is provided with at least one guide groove (121), the guide groove (121) extends spirally along the axial direction of the cam (12), the radius of the cam (12) is r, and the helix angle of the guide groove (121) is θ; The cam (12) is adapted to cooperate with the output member (13) so that the cam (12) and the output member (13) move relative to each other along the axial direction of the cam (12) to output a thrust F; The relationship between the radius r of the cam (12) and the helix angle θ of the guide groove (121) is as follows: Where M is the input torque that drives the cam (12) to rotate, and n is a coefficient, 0.9≤n≤1.

1.

2. The cam (12) according to claim 1, wherein, The helix angle of the guide groove (121) is less than or equal to 35°.

3. The cam (12) according to claim 2, wherein, The helix angle of the guide groove (121) is less than or equal to 25°.

4. The cam (12) according to claim 3, wherein, The helix angle of the guide groove (121) is greater than or equal to 13° and less than or equal to 25°.

5. The cam (12) according to any one of claims 1 to 4, wherein, Along the axial direction of the cam (12), the height of the outline of the guide groove (121) in the axial direction of the cam (12) is greater than or equal to 90 mm and less than or equal to 120 mm.

6. The cam (12) according to any one of claims 1 to 5, wherein, The cam (12) has a cylindrical structure and a receiving cavity (122). The guide groove (121) is formed by the inner wall surface of the receiving cavity (122) being recessed along the radial direction of the cam (12).

7. The cam (12) according to any one of claims 1 to 6, wherein, The diameter of the cam (12) is greater than or equal to 70 mm and less than or equal to 110 mm.

8. The cam (12) according to claim 7, wherein, When the diameter of the cam (12) is greater than or equal to 70 mm and less than or equal to 110 mm, the input torque M that drives the cam (12) to rotate satisfies: 70 Nm ≤ M ≤ 90 Nm.

9. The cam (12) according to any one of claims 1 to 8, wherein, The outline of the guide groove (121) is a linear curve or a non-linear curve.

10. The cam (12) according to any one of claims 1 to 9, wherein, The outline of the guide groove (121) is a linear curve, and the relationship between the lead h of the cam (12), the output thrust F, and the input torque M is as follows: Where n is a coefficient, 0.9≤n≤1.

1.

11. The cam (12) according to any one of claims 1 to 9, wherein, Along the axial direction of the cam (12), the guide groove (121) has a first limit position, a second limit position, and an intermediate position between the first limit position and the second limit position; The helix angle of the guide groove (121) at the intermediate position is θ1, the helix angle of the guide groove (121) at the first extreme position is θ2, and the helix angle of the guide groove (121) at the second extreme position is θ3; Wherein, the helix angle θ1 is greater than or equal to at least one of the helix angle θ2 or helix angle θ3.

12. The cam (12) according to any one of claims 1 to 11, wherein, The at least one guide groove (121) includes a plurality of guide grooves (121), which satisfy N-fold symmetry.

13. The cam (12) according to claim 12, wherein, The plurality of guide grooves (121) include a first guide groove (1211) and a second guide groove (1212), the first guide groove (1211) and the second guide groove (1212) being located on opposite sides of the axis of the cam (12).

14. An actuator (1), comprising: Cam (12) according to any one of claims 1 to 13; as well as The output element (13) is located at least in the guide groove (121).

15. The actuator (1) according to claim 14, wherein, The output component (13) includes: Transmission component (131); and At least one follower (132) is connected to the transmission member (131), and at least a portion of the follower (132) is accommodated in the guide groove (121).

16. The actuator (1) according to claim 15, wherein, The transmission component (131) includes: Rod (1311); and A connecting post (1312) is provided on one side of the rod (1311) in the radial direction; the follower (132) is connected to the connecting post (1312).

17. The actuator (1) according to claim 16, wherein, The connecting column (1312) and the rod (1311) are integrally formed.

18. The actuator (1) according to claim 16, wherein, The follower (132) includes a sliding post, the axial direction of which is consistent with the radial direction of the rod (1311).

19. The actuator (1) according to any one of claims 15 to 18, wherein, The at least one guide groove (121) includes a first guide groove (1211) and a second guide groove (1212), wherein the first guide groove (1211) and the second guide groove (1212) are located on opposite sides of the axis of the cam (12); The at least one follower (132) includes a first follower (1321) and a second follower (1322). The first follower (1321) is disposed in the first guide groove (1211), and the second follower (1322) is disposed in the second guide groove (1212). The first follower (1321) and the second follower (1322) are respectively located on opposite sides of the axis of the cam (12).

20. The actuator (1) according to any one of claims 14 to 19 further includes a drive member (11) connected to one of the cam (12) and the output member (13) to drive the other of the cam (12) and the output member (13) to move.

21. The actuator (1) according to claim 20, wherein, The driving component (11) includes: Casing (111); A stator (112), wherein the stator (112) is disposed within the housing (111) and is fixedly connected to the housing (111); and A mover (113) is disposed within the housing (111) and is rotatable relative to the stator (112). The mover (113) is connected to one of the cam (12) and the output component (13).

22. The actuator (1) according to claim 21, wherein, The cam (12) is disposed inside the housing (111), and the mover (113) surrounds the cam (12), and the stator (112) surrounds the mover (113).

23. The actuator (1) according to claim 21 or 22, wherein, The housing (111) includes: Body (1111), said body (1111) having a second channel extending through said body (1111) along a first direction; and A cover (1112) is connected to the body (1111) and covers one end opening of the second channel.

24. The actuator (1) according to claim 23 further includes a first bearing (16) connected between the cam (12) and the cover (1112).

25. The actuator (1) according to claim 24 further includes a fork arm (1113) connected to the side of the body (1111) opposite to the cover (1112), the fork arm (1113) being adapted to connect to a wheel (20).

26. The actuator (1) according to claim 25 further includes a second bearing (17) connected between the fork arm (1113) and the cam (12).

27. A cam (12), wherein, The cam (12) can cooperate with the output member (13) to convert the rotational motion of one of the cam (12) and the output member (13) into the linear motion of the other; The cam (12) is provided with a receiving cavity (122), and the receiving cavity (122) is configured to store a lubricating medium to lubricate the cam (12) and the output member (13).

28. The cam (12) according to claim 27, wherein, When one of the cam (12) and the output member (13) rotates, it can deliver the lubricating medium in the receiving cavity (122) to the gap between the cam (12) and the output member (13).

29. The cam (12) according to claim 27 or 28, wherein, The cam (12) is provided with a guide groove (121), which extends spirally along the axial direction of the cam (12) and communicates with the receiving cavity (122).

30. The cam (12) according to claim 29, comprising: The main body (124) is provided with a first channel, the first channel having a first opening (123) and a second opening, and the output member (13) is adapted to be movably disposed in the first channel and pass through the first opening (123); as well as A blocking part (125) covers the second opening and is connected to the main body part (124) so ​​that at least a portion of the first channel is formed as the receiving cavity (122).

31. The cam (12) according to claim 30, wherein, The guide groove (121) is formed by the inner wall surface of the first channel being recessed toward the outer wall surface of the cam (12).

32. The cam (12) according to claim 30 or 31, wherein, The main body (124) has a cylindrical structure.

33. An actuator, comprising: The cam (12) according to any one of claims 27 to 32; as well as The output element (13) is adapted to engage with the cam (12) to convert the rotational motion of one of the cam (12) and the output element (13) into the linear motion of the other.

34. The actuator according to claim 33, wherein, The cam (12) is movable between a first position and a second position relative to the output member (13); When the cam (12) is in the first position, the length of the actuator is a first length; when the cam (12) is in the second position, the length of the actuator is a second length, and the first length is less than the second length. When the cam (12) is in the first position, at least a portion of the output element (13) is immersed in the lubricating medium.

35. The actuator according to claim 33 or 34, wherein, The cam (12) is provided with at least one guide groove (121), and the output member (13) includes: Transmission component (131); and At least one follower (132) is connected to the transmission member (131), and at least a portion of the follower (132) is accommodated in the guide groove (121).

36. The actuator according to claim 35, wherein, The at least one guide groove (121) includes a plurality of guide grooves (121), and the plurality of guide grooves (121) satisfy N-fold symmetry; The at least one follower (132) includes a plurality of follower (132), which are respectively located in the plurality of guide grooves (121).

37. The actuator according to claim 36, wherein, The plurality of guide grooves (121) include a first guide groove (1211) and a second guide groove (1212), wherein the first guide groove (1211) and the second guide groove (1212) are respectively located on opposite sides of the axis of the cam (12); The plurality of follower members (132) includes a first follower member (1321) and a second follower member (1322), wherein the first follower member (1321) is disposed in the first guide groove (1211) and the second follower member (1322) is disposed in the second guide groove (1212).

38. The actuator according to any one of claims 35 to 37, wherein, The transmission component (131) includes: Rod (1311); and A connecting post (1312) is provided on one side of the rod (1311) in the radial direction; the follower (132) is connected to the connecting post (1312).

39. The actuator according to claim 38, wherein, The connecting column (1312) and the rod (1311) are integrally formed.

40. The actuator according to claim 38, wherein, The follower (132) includes a sliding post, the axial direction of which is consistent with the radial direction of the rod (1311).

41. The actuator according to any one of claims 38 to 40, wherein, The transmission component (131) also includes: A damping element (14) is connected to the rod body (1311) and slides with the inner wall surface of the cam (12).

42. The actuator according to claim 41, wherein, The damping element (14) is a damping plate, and the thickness direction of the damping plate is consistent with the axial direction of the rod (1311).

43. The actuator according to claim 41 or 42, wherein, The damping element (14) is provided with a plurality of through holes, which pass through the damping element (14) along the axial direction of the rod (1311).

44. The actuator according to any one of claims 41 to 43, wherein, The damping element (14) is made of either a rigid material or a flexible material.

45. The actuator according to any one of claims 38 to 44, wherein, The transmission component (131) further includes a limiting protrusion (133), which is connected to the rod body (1311) and protrudes radially along the rod body (1311); The actuator also includes a buffer (15) disposed on the side of the guide groove (121) facing the first opening (123), and the buffer (15) is configured to cooperate with the limiting protrusion (133) to buffer the transmission member (131).

46. ​​The actuator according to any one of claims 33 to 45, further comprising a drive member (11) connected to one of the cam (12) and the output member (13) to drive one of the cam (12) and the output member (13) to rotate.

47. The actuator according to claim 46, wherein, The driving component (11) includes: Casing (111); A stator (112), wherein the stator (112) is disposed within the housing (111) and is fixedly connected to the housing (111); and A mover (113) is disposed within the housing (111) and is rotatable relative to the stator (112). The mover (113) is connected to one of the cam (12) and the output component (13).

48. The actuator according to claim 47, wherein, The cam (12) is disposed inside the housing (111), and the mover (113) surrounds the cam (12), and the stator (112) surrounds the mover (113).

49. The actuator according to claim 48, wherein, The housing (111) is provided with a limiting boss (114), which is located on one side of the mover (113) in the first direction to limit the stator (112).

50. The actuator according to claim 49, wherein, The housing (111) includes: Body (1111), the body (1111) having a second channel extending through the body (1111) along the first direction; and A cover (1112) is connected to the body (1111). The cover (1112) is located on the side of the first opening (123) opposite to the second opening and covers one end opening of the second channel.

51. The actuator according to claim 50, further comprising: A first bearing (16) is connected between the cam (12) and the cover (1112).

52. The actuator according to claim 50 further includes a fork arm (1113) connected to the side of the body (1111) opposite to the cover (1112), the fork arm (1113) being adapted to connect to a wheel (20).

53. The actuator according to claim 52 further includes a second bearing (17) connected between the fork arm (1113) and the cam (12).

54. The actuator according to claim 52 further includes a first oil seal connected between the body (1111) and the cam (12) and configured to seal the gap between the body (1111) and the cam (12), the first oil seal being located on the side of the stator (112) and the mover (113) facing the first opening (123).

55. A suspension assembly (30) comprising an actuator (1) according to any one of claims 14 to 26, or 33 to 54.

56. The suspension assembly (30) according to claim 55, further comprising: A tower top assembly (2) adapted to connect to the vehicle body (10) and connected to the actuator (1).

57. A vehicle (100), comprising: The cam (12) according to any one of claims 1 to 13, or 27 to 32; Alternatively, the actuator (1) according to any one of claims 14 to 26, or 33 to 54; or the suspension assembly (30) according to claim 55 or 56.

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