Torque transmission mechanism

Abstract

A torque transmission mechanism includes a first rotating member and a second rotating member rotatable relative to each other, one of the first rotating member and the second rotating member being disposed radially inward of the other. The torque transmission mechanism further comprises a hydraulic device, and the torque transmission mechanism is configured to be capable of transmitting torque between the first rotating component and the second rotating component through the hydraulic device. The torque transmission mechanism has improved damping and buffering effects.

Description

Torque transmission mechanism Technical Field

[0001] The present invention relates to the field of transmission technology, and in particular to a torque transmission mechanism with vibration reduction and buffering effects. Background Art

[0002] In the prior art, mechanisms such as splines or gears are usually used to transmit torque between two rotating parts. Due to the gap between the coupled splines or teeth, the rotating parts may generate spline or tooth impact noise during operation. For example, in the non-torque transmission state of the transmission, this impact noise is very significant. It is necessary to meet high torque transmission and large damping requirements in a limited space to reduce this impact noise. For current rigid transmission mechanisms, this problem is difficult to solve. In existing transmissions, the noise of the splines or teeth is usually eliminated by increasing the torque to keep the mating splines or teeth in a compressed state at all times. However, this method will correspondingly increase the battery energy consumption and fuel consumption, and increase the operating temperature of the battery, thereby affecting the service life of the battery, motor, and related components of the thermal management system.

[0003] Summary of the Invention

[0004] Therefore, the technical problem to be solved by the present invention is to provide a torque transmission mechanism with vibration reduction and buffering effects.

[0005] The above technical problem is solved by a torque transmission mechanism according to the present invention. The torque transmission mechanism includes a first rotating component and a second rotating component that are capable of relative rotation, with one of the first rotating component and the second rotating component being arranged radially inward of the other. The torque transmission mechanism further includes a hydraulic device configured to transmit torque between the first and second rotating components via the hydraulic device. Torque transmission between the two rotating components is achieved via the hydraulic device, thereby dampening torque vibrations using the hydraulic fluid.

[0006] According to a preferred embodiment of the present invention, the hydraulic device may be one or more pistons. The second rotating component includes one or more piston chambers for containing hydraulic fluid. Each piston is movably mounted in a corresponding piston chamber so as to extend from the second rotating component to abut the first rotating component. The pistons can transmit torque by compressing the hydraulic fluid in the piston chambers. During the torque transmission, the hydraulic fluid can buffer torque vibrations transmitted to the pistons.

[0007] According to another preferred embodiment of the present invention, the first rotating component and the second rotating component can have a non-torque transmission position relative to each other, in which the one or more pistons do not contact the first rotating component or can only contact the first rotating component in a manner such that the circumferential component of the thrust resultant is zero, and when the first rotating component and the second rotating component rotate relative to each other within a predetermined range and deviate from the non-torque transmission position, the first rotating component can abut at least a portion of the one or more pistons in a direction having a circumferential force component, thereby causing the at least a portion of the pistons to move in a direction of retracting the second rotating component to compress the hydraulic fluid in the corresponding piston chamber and transmit torque between the first rotating component and the second rotating component through the at least a portion of the pistons. In a state where there is no significant torque transmission between the two rotating components, direct collisions between rigid torque transmission structures (such as splines or teeth) caused by vibration can be prevented, thereby reducing noise.

[0008] According to another preferred embodiment of the present invention, when each piston is pushed by the first rotating member and compresses the hydraulic fluid in the corresponding piston chamber, the hydraulic fluid can leak between the corresponding piston and the piston chamber in a direction opposite to the direction of movement of the corresponding piston. The leaked hydraulic fluid can cushion the movement of the piston by moving in the opposite direction of the piston, thereby further reducing vibration.

[0009] According to another preferred embodiment of the present invention, the one or more piston chambers may include a plurality of piston chambers spaced apart along the circumferential direction, and the second rotating component may include an annular liquid storage chamber, the liquid storage chamber being in communication with each piston chamber so as to be able to supply hydraulic fluid to each piston chamber. In this way, hydraulic fluid can be supplied to multiple piston chambers simultaneously using a single supply channel. Preferably, each piston chamber can be in communication with the liquid storage chamber via a corresponding connecting hole, so that the hydraulic fluid in each piston chamber can generate a transient high pressure relative to the hydraulic fluid in the liquid storage chamber when compressed by the corresponding piston. The connecting hole can produce a certain buffering effect between the piston chamber and the liquid storage chamber by shrinking the inner diameter of the flow channel. Therefore, when the piston vibration causes the liquid pressure in the piston chamber to suddenly increase, the transmission of the liquid pressure to the liquid storage chamber will be hindered by the connecting hole, thereby controlling the distribution range of the transient high pressure in the entire second rotating component, thereby reducing the impact on the structural strength of the second rotating component.

[0010] According to another preferred embodiment of the present invention, each piston chamber can be radially located between the reservoir chamber and the first rotating component. In other words, the reservoir chamber and the first rotating component are positioned in opposite radial directions relative to the piston chamber. This arrangement of the reservoir chamber away from the first rotating component facilitates the introduction of hydraulic fluid.

[0011] According to another preferred embodiment of the present invention, the torque transmission mechanism may further include one or more elastic members, each of which is disposed in a corresponding piston cavity and elastically abuts against a corresponding piston in the extension direction. The elastic members may also provide a cushioning effect on the retraction movement of the piston, particularly to supplement the cushioning effect in the event of insufficient hydraulic fluid.

[0012] According to another preferred embodiment of the present invention, the first rotating component may include one or more guide profiles facing the second rotating component. Each piston is radially movably mounted in a corresponding piston cavity and abuts a corresponding guide profile. Each guide profile is recessed in a radial direction away from the second rotating component and has a maximum depth position at a circumferentially central location. In a non-torque-transmitting position, each piston abuts at the maximum depth position of the corresponding guide profile. The recessed depth of each guide profile gradually decreases circumferentially from the maximum depth position toward the ends of the corresponding guide profile, thereby pushing the corresponding piston back into the second rotating component when the first and second rotating components deviate from the non-torque-transmitting position. When the piston abuts at the maximum depth position of the guide profile, the thrust of the guide profile on the piston is radial and has no circumferential component, thereby preventing significant torque from being transmitted between the two rotating components. When the two rotating components rotate away from the non-torque-transmitting position, the end of the piston slides along the guide profile to a position with a smaller depth, thereby pushing the piston back into the second rotating component. At the same time, when the piston abuts at the non-maximum depth position of the guide profile, the thrust of the guide profile on the piston is no longer parallel to the radial direction and has a circumferential component, thereby enabling torque transmission between the two rotating components. Since the transmitted torque depends on the position of the piston in the piston chamber, the hydraulic fluid can dampen torque vibrations.

[0013] According to another preferred embodiment of the present invention, in a cross-section perpendicular to the axial direction, at least a portion of the one or more guide profiles may have a concave arcuate profile, and / or at least a portion of the one or more pistons may have a protruding arcuate profile at the end thereof that abuts the corresponding guide profile. This arcuate profile facilitates sliding of the piston along the guide profile and can reduce stress concentration. Alternatively, the guide profile may have a straight profile, such as a triangle, or other shaped profile.

[0014] According to another preferred embodiment of the present invention, the first rotating component may include one or more first limiting structures, and the second rotating component may include one or more second limiting structures. When the first rotating component and the second rotating component rotate relative to each other to the limit position of the predetermined rotation range, at least a portion of the one or more first limiting structures circumferentially abuts the corresponding second limiting structures, thereby preventing the first rotating component and the second rotating component from rotating beyond the predetermined rotation range. When the limit position of the predetermined rotation range is reached, the two rotating components can transmit torque by circumferentially abutting the first limiting structures and the second limiting structures against each other.

[0015] According to another preferred embodiment of the present invention, the one or more pistons may include at least one first piston and at least one second piston spaced circumferentially apart. Each first piston and each second piston are circumferentially movably mounted in a corresponding piston cavity. Each first piston is capable of abutting the first rotating member in a first circumferential rotational direction, and each second piston is capable of abutting the first rotating member in a second rotational direction opposite to the first rotational direction. Thus, the two rotating members can transmit torque in different rotational directions via two sets of pistons moving circumferentially in opposite directions. Preferably, each piston has a maximum extension position defined by its corresponding piston cavity. During rotation of the first rotating member relative to the second rotating member in either rotational direction, away from the non-torque-transmitting position, a portion of the one or more pistons are pushed by the first rotating member toward the second rotating member, and the pistons of the one or more pistons not pushed by the first rotating member are constrained in their respective maximum extension positions and separated from the first rotating member. Therefore, the first rotating member is not subjected to circumferential thrust from the pistons in the non-torque-transmitting position. When the first rotating member rotates in a certain direction, pushing one set of pistons, the other set of pistons is constrained by the piston cavity in their maximum extension positions and separated from the first rotating member.

[0016] According to another preferred embodiment of the present invention, the first rotating component may include one or more protrusions protruding toward the second rotating component, and the second rotating component may include one or more recesses recessed away from the first rotating component. Each protrusion is radially inserted into a corresponding recess, and each piston extends from the sidewall of the corresponding recess into the second rotating component and is capable of abutting the sidewall of the corresponding protrusion. This structure facilitates circumferential contact between the piston and the first rotating component.

[0017] According to another preferred embodiment of the present invention, the at least one first piston and the at least one second piston are alternately distributed in the circumferential direction. Any pair of circumferentially adjacent first and second pistons extending away from each other constitutes a piston pair, and each piston pair is mounted in the same circumferentially extending piston cavity. This facilitates a simplified flow channel structure. In this case, the elastic member can elastically abut between the two pistons of the piston pair. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The present invention is further described below with reference to the accompanying drawings. Elements with the same function are represented by the same reference numerals in the drawings.

[0019] FIG. 1 a shows a perspective view of a torque transmission mechanism according to a first embodiment of the present invention;

[0020] FIG1 b shows a longitudinal sectional view of a torque transmission mechanism according to a first embodiment of the present invention;

[0021] FIG1c shows a partial enlarged view of the torque transmission mechanism according to the first embodiment of the present invention;

[0022] FIG2 a shows a perspective view of a torque transmission mechanism according to a second embodiment of the present invention;

[0023] FIG2 b shows a perspective cross-sectional view of a torque transmission mechanism according to a second embodiment of the present invention;

[0024] FIG3 a shows a transverse cross-sectional view of a torque transmission mechanism according to a third embodiment of the present invention;

[0025] FIG3 b shows a longitudinal sectional view of a torque transmission mechanism according to a third embodiment of the present invention;

[0026] FIG4 a shows a perspective view of a torque transmission mechanism according to a fourth embodiment of the present invention;

[0027] FIG4 b shows a transverse cross-sectional view of a torque transmission mechanism according to a fourth embodiment of the present invention;

[0028] FIG5 is a graph showing an operation curve of a torque transmitting mechanism according to an exemplary embodiment of the present invention; and

[0029] FIG. 6 is a simulation graph illustrating a torque transmitting mechanism according to an exemplary embodiment of the present invention. DETAILED DESCRIPTION

[0030] The following detailed description and accompanying drawings are used to illustrate the principles of the present invention. The present invention is not limited to the preferred embodiments described. The scope of protection of the present invention is defined by the claims.

[0031] According to an embodiment of the present invention, a torque transmission mechanism is provided that can replace a traditional spline transmission mechanism or gear transmission mechanism with a hydraulic device to transmit torque between two rotating parts. The present invention provides multiple exemplary embodiments of such a torque transmission mechanism.

[0032] Figures 1a to 1c illustrate a first embodiment of a torque transmission mechanism according to the present invention. As shown in Figure 1a, the torque transmission mechanism includes an outer rotating component 10 and an inner rotating component 20. The outer rotating component 10 is a generally annular component, and the inner rotating component 20 is a generally disc-shaped or annular component. The inner rotating component 20 is coaxially arranged radially inward of the outer rotating component 10. The outer rotating component 10 and the inner rotating component 20 are capable of relative rotation about a common central axis. The radial support and relative rotation between the outer rotating component 10 and the inner rotating component 20 can be achieved, for example, by bearings or rolling elements 40 directly mounted therebetween (i.e., the outer and inner rings of the bearing are integrally formed with the rotating component).

[0033] As shown in Figures 1b and 1c, the torque transmission mechanism also includes one or more pistons 30, and the inner rotating component 20 is formed with one or more piston cavities 21. Each piston 30 is installed in a corresponding piston cavity 21 and can be guided by the side wall of the piston cavity 21 and move along the extension direction of the piston cavity 21. When there are multiple pistons 30 (and corresponding multiple piston cavities 21), these pistons 30 (and therefore piston cavities 21) can be distributed at intervals along the circumference (preferably evenly distributed). In addition, these pistons 30 preferably have substantially the same shape and size, and these piston cavities 21 also preferably have substantially the same shape and size. In the first embodiment, each piston cavity 21 extends generally radially and penetrates to the outer circumferential surface of the inner rotating component 20, so that the piston 30 installed in the piston cavity 21 can move generally radially and partially extend out of the piston cavity 21 to abut the inner circumferential surface of the outer rotating component 10.

[0034] Corresponding to the one or more pistons 30 in the inner rotating component 20, the outer rotating component 10 includes one or more guide surfaces 11 facing the inner rotating component 20 (in this embodiment, radially inward). These guide surfaces 11 can be integrally formed with the outer rotating component 10 or attached to the outer rotating component 10. Each piston 30 corresponds to a corresponding guide surface 11 along the circumference. The end of each piston 30 extending beyond the piston cavity 21 can abut against a corresponding guide surface 11. Each guide surface 11 is concave in the radial direction away from the inner rotating component 20 (in this embodiment, radially outward). Each guide surface 11 has a maximum depth at the circumferential center, and the concave depth (radial depth) of the guide surface 11 gradually decreases from the corresponding maximum depth toward the ends. In a cross-section perpendicular to the axial direction, the guide surface 11 can have, for example, an arcuate profile, a sharp-angled triangular profile, or a triangular profile with rounded vertices. Preferably, in a cross-section perpendicular to the axial direction, the profile of the guide surface 11 is symmetrical about the maximum depth.

[0035] Each piston chamber 21 is filled with hydraulic fluid. The hydraulic pressure generated by the hydraulic fluid causes the piston 30 to extend from the inner rotating member 20 and abut the outer rotating member 10. When any piston 30 abuts the corresponding guide profile 11 at its maximum depth, the piston 30 is at its maximum extension position, and the thrust between the piston 30 and the guide profile 11 (excluding friction on the contact surface) is substantially radial, with no circumferential (or tangential) component.

[0036] The outer rotating component 10 and the inner rotating component 20 have a non-torque-transmitting position relative to each other. As the name suggests, the non-torque-transmitting position is a relative position in which no torque can be transmitted, or no significant torque (i.e., torque greater than a predetermined amount) can be transmitted, between the outer rotating component 10 and the inner rotating component 20. It can also be referred to as a neutral position. Furthermore, the non-torque-transmitting position can also be considered the zero-degree point of the relative rotation angle between the two rotating components. When the outer rotating component 10 and the inner rotating component 20 are in the non-torque-transmitting position relative to each other, each piston 30 abuts at the maximum depth of its corresponding guide profile 11, thereby preventing significant torque from being transmitted between the two rotating components. When the outer rotating component 10 and the inner rotating component 20 rotate relative to each other within a predetermined rotation range and deviate from the non-torque-transmitting position, the end of each piston 30 slides along the guide profile 11 to a smaller depth. As a result, the outer rotating component 10, through each guide profile 11, pushes the corresponding piston 30 toward retraction into the inner rotating component 20 (i.e., toward the interior of the corresponding piston chamber 21). At the same time, since the extension direction of the guide profile 11 on both sides of the maximum depth position is inclined with respect to the tangential direction, the thrust of the guide profile 11 on the piston 30 at positions outside the maximum depth position is no longer parallel to the radial direction but generates a circumferential component, thereby enabling torque to be transmitted between the two rotating parts.

[0037] Preferably, in a cross-section perpendicular to the axial direction, the guide profile 11 may have a concave arcuate profile. Similarly, the end of the piston 30 that abuts the corresponding guide profile 11 may also have a convex arcuate profile. This arcuate profile facilitates sliding of the piston along the guide profile and reduces stress concentration. For example, the end of the piston 30 that abuts the corresponding guide profile 11 may be an integrally formed spherical end, or it may be a rotatably mounted pulley, allowing the end of the piston 30 to roll along the guide profile 11.

[0038] FIG5 illustrates an operational graph of a torque transmission mechanism according to an exemplary embodiment of the present invention. The abscissas of the two graphs in FIG5 represent rotational position, with the vertical line in the middle corresponding to the non-torque-transmitting position. The ordinates of the upper graph represent the depth of the guide profile at the abutment point of piston 30, and the ordinate of the lower graph represents the pressure angle at the abutment point of piston 30 (a pressure angle of 0 degrees indicates that the pressure acts entirely radially). As shown, this torque transmission mechanism has two operating stages within its rotational range. Near the non-torque-transmitting position, the torque transmission mechanism is in a decoupling stage. During this decoupling stage, the two rotating components deviate from the non-torque-transmitting position by a small angle, resulting in a small pressure angle. The torque transmitted between the two components via piston 30 is very small and negligible. This primarily corresponds to vibrations of rotating components in a non-operating state, such as those occurring in a transmission during parking, charging, or light throttle acceleration. The energy of this vibration can be absorbed by the hydraulic fluid in piston chamber 21, thereby reducing noise. During the torque-transmitting stage, the two rotating components deviate from the non-torque-transmitting position by a large angle, resulting in a large pressure angle, allowing for the transmission of a significant torque between the two components via piston 30. During the torque transmission stage, the torque vibration can still be buffered by the hydraulic fluid.

[0039] Preferably, an elastic member 50 (e.g., a coil spring or other elastic member) may be additionally installed in one or more piston cavities 21. The elastic member 50 elastically abuts radially between the corresponding piston 30 and the end of the piston cavity 21 facing away from the outward rotating component 10. In particular, when hydraulic fluid is insufficient, the elastic force generated by the elastic member 50 can supplement the liquid pressure of the hydraulic fluid.

[0040] Preferably, each piston 30 may be in non-sealed contact with the sidewall of the corresponding piston chamber 21. Therefore, when the piston 30 is pushed by the outer rotating component 10 and compresses the hydraulic fluid in the corresponding piston chamber 21, the hydraulic fluid may leak between the corresponding piston 30 and the piston chamber 21 in a direction opposite to the direction of movement of the corresponding piston 30. The leaked hydraulic fluid can cushion the movement of the piston 30 by moving in the opposite direction of the piston 30, thereby further reducing vibration.

[0041] As shown in FIG1c , in the first embodiment, when the inner rotating component 20 includes multiple circumferentially spaced piston chambers 21, the inner rotating component 20 may also preferably include an annular liquid reservoir chamber 22. The liquid reservoir chamber 22 communicates with each piston chamber 21, thereby supplying hydraulic fluid to each piston chamber 21. This allows a single supply channel to simultaneously supply hydraulic fluid to multiple piston chambers 21. In this case, each piston chamber 21 communicates with the liquid reservoir chamber 22 via a corresponding communication hole 23. The communication hole 23 can create a buffering effect between the corresponding piston chamber 21 and the liquid reservoir chamber 22 by constricting the inner diameter of the flow channel. This allows the hydraulic fluid in the piston chamber 21 to generate a transient high pressure relative to the hydraulic fluid in the liquid reservoir chamber 22 when compressed by the corresponding piston 30. Therefore, when the vibration of the piston 30 causes a sudden increase in the liquid pressure in the piston chamber 21, the transmission of the liquid pressure to the liquid reservoir chamber 22 is hindered by the communication hole 23. This effectively controls the distribution of the transient high pressure throughout the inner rotating component 20, thereby reducing the impact on the structural strength of the inner rotating component 20. Preferably, the reservoir chamber 22 can be located radially inward of all piston chambers 21, such that the piston chamber 21 is radially located between the reservoir chamber 22 and the outer rotating component 10. The reservoir chamber 22 is thus positioned away from the outer rotating component 10, facilitating the introduction of hydraulic fluid. The hydraulic fluid can be introduced into the reservoir chamber 22 via the one-way valve 60 located radially inward of the reservoir chamber 22, and then further flow through the reservoir chamber 22 to each piston chamber 21.

[0042] Alternatively, the inner rotating component 20 may not have a fluid reservoir 22, as shown in the third embodiment of Figures 3a and 3b. As shown, the multiple piston chambers 21 of the inner rotating component 20 are independent of each other. Each piston chamber 21 may communicate with the inner circumference of the inner rotating component 20 via a separate orifice. Each orifice may be equipped with a corresponding one-way valve 60 to control the flow of hydraulic fluid into the piston chamber 21.

[0043] In the first embodiment shown in Figures 1a to 1c, both circumferential ends of the guide profile 11 extend directly to the inner circumferential surface of the inner rotating component 20. The contact range between the guide profile 11 and the corresponding piston 30 defines the predetermined rotational range between the two rotating components. The magnitude of the torque transmitted between the two rotating components depends on the relative positions of the two rotating components within the predetermined rotational range. When the transmitted torque is excessive, causing the two rotating components to exceed the predetermined rotational range, the piston 30 will disengage from the corresponding guide profile 11 and abut against the inner circumferential surface of the inner rotating component 20 between adjacent guide profiles 11. At this point, the pressure angle at the contact surface is zero, and the pressure has no circumferential component, resulting in only circumferential friction between the two rotating components. This ineffectively transmits torque between the two rotating components, thereby limiting the maximum transmittable torque.

[0044] Unlike the first embodiment, the second embodiment shown in Figures 2a and 2b incorporates limiting structures to prevent the two rotating components from rotating beyond a predetermined range. As shown, the outer rotating component 10 includes one or more first limiting structures 12, while the inner rotating component 20 includes one or more second limiting structures 24. When the outer rotating component 10 and the inner rotating component 20 rotate relative to each other to the limit of the predetermined range, at least a portion of the first limiting structures 12 circumferentially abut against the corresponding second limiting structures 24, thereby preventing the two rotating components from rotating further beyond the predetermined range. Furthermore, when the limit of the predetermined range is reached, the two rotating components can also transmit greater torque by circumferentially abutting against the first limiting structures 12 and the second limiting structures 24. The axial position of these limiting structures can overlap, partially overlap, or not overlap with the piston 30 and / or the guide profile 11. The third embodiment (Figures 3a and 3b) also illustrates the same limiting structures as the second embodiment. In the second and third embodiments, the first limiting structure 12 and the second limiting structure 24 can be step surfaces formed on the corresponding rotating parts and facing each other basically along the circumferential direction (as shown in the figure); or, the first limiting structure 12 can be a step surface formed on the outer rotating part 10, and the second limiting structure can be acted as a piston 30 installed on the inner rotating part 20 (not shown).

[0045] Figures 4a and 4b illustrate a torque transmission mechanism according to a fourth embodiment of the present invention. Unlike the first embodiment, in which each piston can cooperate with a corresponding guide profile 11 to transmit bidirectional torque, in the fourth embodiment, each piston 30 can only abut the outer rotating component 10 in a unidirectional, circumferential direction. Therefore, the torque transmission mechanism of the fourth embodiment includes a plurality of pistons 30 spaced circumferentially, each piston 30 comprising at least one first piston 30a and at least one second piston 30b. Each first piston 30a and each second piston 30b is mounted in a corresponding piston cavity 21. Each piston cavity 21 extends generally circumferentially and, through its sidewalls, guides the circumferential movement of the piston 30 (first piston 30a and / or second piston 30b) therein. The ends of each piston cavity 21 are circumferentially continuous, allowing the ends of the pistons 30 mounted therein to partially extend out of the piston cavity 21 and abut the outer rotating component 10. The surface of the outer rotating component 10 abutted by the pistons 30 can be a radial surface of a structure formed on or fixed to the outer rotating component 10, such as a radially extending step or baffle. Each first piston 30a can abut the outer rotating component 10 in a first rotational direction along the circumferential direction, while each second piston 30b can abut the outer rotating component 10 in a second rotational direction opposite to the first rotational direction. When the two rotating components rotate in a certain rotational direction, one of the first piston 30a and the second piston 30b is pushed to retract into the corresponding piston chamber 21. Thus, the two rotating components can transmit torque and dampen vibration in different rotational directions through two sets of pistons moving in opposite directions.

[0046] When the two rotating parts are in the non-torque transmission position, the circumferential component of the thrust resultant generated by all pistons 30 (including the first piston 30a and the second piston 30b) on the outer rotating part 10 is zero. This can include three situations: first, in the non-torque transmission position, the pistons 30 do not contact the outer rotating part 10; second, in the non-torque transmission position, the pistons 30 contact the outer rotating part 10 without thrust; third, in the non-torque transmission position, at least some of the pistons 30 may contact the outer rotating part 10, wherein the thrust generated by a single piston 30 on the outer rotating part 10 is not zero, but the circumferential component of the thrust resultant generated by all pistons 30 on the outer rotating part 10 is zero (in this embodiment, the thrust generated by the pistons 30 on the outer rotating part 10 acts in the circumferential direction, so a circumferential component of zero means that the thrust resultant is also zero). In any case, the outer rotating part 10 is not subjected to the circumferential thrust of the pistons 30 in the non-torque transmission position. When the outer rotating component 10 rotates in a certain direction relative to the inner rotating component 20 and pushes a group of pistons (the first piston 30a or the second piston 30b) in the corresponding direction, the group of pistons contacts the outer rotating component 10 and moves in the direction of retracting the inner rotating component 20. Therefore, the circumferential thrust on the outer rotating component 10 in the corresponding direction increases while the circumferential thrust in the opposite direction decreases or remains unchanged, so that the resultant force of the circumferential thrusts acting between all the pistons 30 on the outer rotating component 10 increases in the corresponding direction as the rotation position increases.

[0047] Preferably, each piston 30 can have a maximum extended position defined by its corresponding piston cavity 21. During rotation of the outer rotating component 10 relative to the inner rotating component 20 in either direction and away from the non-torque-transmitting position, the other group of pistons 30 (the second pistons 30b or the first pistons 30a) not pushed by the outer rotating component 10 will be constrained by their corresponding piston cavities 21 in the maximum extended position and separated from the outer rotating component 10. Specifically, each piston 30 can include a plug body 31 and a plug head 32 divided along the extension direction of the piston cavity 21, wherein the outer diameter of the plug body 31 is larger than the outer diameter of the plug head 32. The inner diameter of the end opening of the piston cavity 21 is smaller than the inner diameters of the piston cavity 21 and the plug body 31, but larger than the outer diameter of the plug head 32, so that the plug body 31 cannot extend out of the piston cavity 21, but the plug head 32 can. At the maximum extended position, the plug body 31 abuts against the end of the corresponding piston cavity 21, thereby achieving position limiting. If the piston 30 does not contact the outer rotating part 10 in the non-torque transmission position or can only contact the outer rotating part 10 without thrust, the piston 30 is limited to the maximum extension position by the corresponding piston cavity 21 in the non-torque transmission position, and any angle of deviation of the outer rotating part 10 from the non-torque transmission position in the direction away from a certain group of pistons 30 will cause the piston 30 to separate from the group of pistons 30; if the piston 30 contacts the outer rotating part 10 with a non-zero thrust in the non-torque transmission position, the piston 30 does not reach the maximum extension position in the non-torque transmission position. In the process of the outer rotating part 10 deviating from the non-torque transmission position in the direction away from a certain group of pistons 30, the group of pistons 30 can initially continue to extend from the corresponding piston cavity 21 as the outer rotating part 10 rotates, until the outer rotating part 10 rotates to a predetermined angle, the group of pistons 30 reaches the maximum extension position limited by the corresponding piston cavity 21 and begins to separate from the outer rotating part 10 that continues to rotate.

[0048] Preferably, the outer rotating component 10 may include one or more protrusions 13 projecting toward the inner rotating component 20 (radially inward), and the inner rotating component 21 may include one or more recesses 25 recessed away from the outer rotating component 10 (radially inward). Each protrusion 13 radially inserts into a corresponding recess 25, and each piston 30 extends from the sidewall of the corresponding recess 25 within the inner rotating component 20 and is capable of abutting the sidewall of the corresponding protrusion 13. Furthermore, the first pistons 30a and second pistons 30b are preferably arranged alternately in the circumferential direction. Any pair of first and second pistons 30a, 30b that are circumferentially adjacent and extend away from each other constitutes a piston pair. Each piston pair is mounted in the same circumferentially extending piston cavity 21 and extends from opposite ends of the piston cavity 21. In this case, the piston pairs in the same piston cavity 21 may share a common elastic member 50, which elastically abuts between the two pistons of the piston pair. Alternatively, in the fourth embodiment, each piston 30 may be mounted in a separate piston cavity 21. In this case, the corresponding elastic member 50 may elastically abut between the piston 30 and the end of the piston chamber 21 .

[0049] As shown in Figures 4a and 4b, in the fourth embodiment, when the two rotating components rotate to the extreme positions of the predetermined rotation range, the surfaces of the two rotating components will directly abut each other. For example, at the extreme position of a certain rotation direction, the protrusion 13 corresponding to that rotation direction will directly abut the corresponding recessed portion 25, thereby directly transmitting torque between the two rotating components and preventing the two rotating components from rotating further beyond the predetermined rotation range.

[0050] In the fourth embodiment, the inner rotating member 20 may also be formed with a liquid storage chamber 22 and / or communication hole 23 similar to those in the first embodiment. Their structure and function are similar to those in the first embodiment and will not be further described here. Similarly, in the fourth embodiment, each piston 30 may also preferably be in non-sealed contact with the sidewall of the corresponding piston chamber 21.

[0051] It should be noted that in each embodiment of the present invention, the piston 30 can alternatively be installed in the piston cavity formed in the outer rotating component 10 so as to abut the inner rotating component 20. This allows the positional relationship of various mating structures on the two rotating components to be interchanged between the two rotating components. For ease of distinction, the rotating component used to abut the piston 30 can be collectively referred to as the first rotating component, while the rotating component used to mount the piston 30 can be collectively referred to as the second rotating component. In addition, except for the differences explicitly stated, the technical features described in any embodiment can also be applied to the other embodiments.

[0052] In the torque transmission mechanism according to various embodiments of the present invention, the first and second rotating members transmit torque via a hydraulic device. Thus, torque vibrations can be damped by the hydraulic fluid, thereby reducing noise. Specifically, when the first and second rotating members are in a non-torque transmission position, the pistons do not contact the first rotating member or only contact the first rotating member with a circumferential component of the resultant thrust being zero. This contact state in which the circumferential component of the resultant thrust is zero includes three contact states: the first is when no thrust exists between all pistons and the first rotating member (although static friction may exist); the second is when thrust exists between at least some of the pistons and the first rotating member, but each piston's thrust has no circumferential component (the circumferential component is zero) (first embodiment); and the third is when thrust exists between at least some of the pistons and the first rotating member, but the circumferential component of the resultant thrust between all pistons and the first rotating member is zero. In other words, the circumferential thrusts exerted on the first rotating member by different pistons cancel each other out (fourth embodiment). When the first rotating member and the second rotating member rotate relative to each other within a predetermined range and deviate from the non-torque transmission position, the first rotating member can abut at least a portion of the piston in the direction having a circumferential force component, thereby pushing the at least a portion of the piston to retract the second rotating member to compress the hydraulic fluid in the corresponding piston chamber, and transmit torque between the first rotating member and the second rotating member through the at least a portion of the piston. This torque transmission method has the torque transmission effect previously described with reference to Figure 5. Due to the buffering effect of the hydraulic fluid, the vibration and noise of the rotating parts can be significantly reduced. This is particularly suitable for (but not limited to) replacing conventional spline or gear transmission mechanisms in the vehicle's transmission to reduce noise, especially when parking, charging, or accelerating with a small throttle.

[0053] The effectiveness of the torque transfer mechanism according to the present invention can be verified through simulation experiments. For example, the inventors used multi-body dynamic simulation methods to verify the damping effect of this torque transfer mechanism. As shown in the curve graph of the vehicle transmission simulation experiment in Figure 6, the impact force in charging mode is significantly reduced. This proves that the torque transfer mechanism according to the present invention can effectively buffer torque shock and vibration, while also reducing the maximum driving torque in the tow-start mode.

[0054] While the foregoing descriptions illustrate possible embodiments, it should be understood that numerous variations exist through combinations of all known and other technical features and implementations readily conceivable to a skilled artisan. Furthermore, it should be understood that the exemplary embodiments serve merely as examples and in no way limit the scope, application, or configuration of the present invention. The foregoing descriptions are intended primarily to provide a skilled artisan with technical guidance for implementing at least one exemplary embodiment. Various modifications, particularly regarding the functionality and structure of the components described, may be made without departing from the scope of the claims.

[0055] Reference Signs 10 Outer rotating member 11 Guide profile 12 First limiting structure 13 Protrusion 20 Inner rotating member 21 Piston cavity 22 Liquid storage cavity 23 Communication hole 24 Second limiting structure 25 Recessed portion 30 Piston 30a First piston 30b Second piston 31 Plug body 32 Plug head 40 Rolling element 50 Elastic member 60 One-way valve

Claims

1. A torque transmission mechanism, comprising a first rotating member and a second rotating member capable of relative rotation, wherein one of the first rotating member and the second rotating member is arranged radially inside the other, It is characterized in that The torque transmission mechanism further includes a hydraulic device, and the torque transmission mechanism is configured to be able to transmit torque between the first rotating member and the second rotating member through the hydraulic device.

2. The torque transmission mechanism according to claim 1, characterized in that: The hydraulic device is one or more pistons (30), the second rotating component includes one or more piston chambers (21) for containing hydraulic fluid, each piston (30) is movably installed in a corresponding piston chamber (21) so as to be able to extend the second rotating component to abut the first rotating component.

3. The torque transmission mechanism according to claim 2, characterized in that: The first rotating component and the second rotating component have a non-torque transmission position relative to each other. In the non-torque transmission position, the one or more pistons (30) do not contact the first rotating component or can only contact the first rotating component in a manner where the circumferential component of the thrust resultant force is zero. When the first rotating component and the second rotating component rotate relative to each other within a predetermined range and deviate from the non-torque transmission position, the first rotating component can abut at least a portion of the one or more pistons (30) in a direction having a circumferential force component, thereby causing the at least a portion of the pistons (30) to move in a direction of retracting the second rotating component to compress the hydraulic fluid in the corresponding piston chamber (21) and to transmit torque between the first rotating component and the second rotating component through the at least a portion of the pistons (30).

4. The torque transmission mechanism according to claim 3, characterized in that: When each piston (30) is pushed by the first rotating member to compress the hydraulic fluid in the corresponding piston chamber (21), the hydraulic fluid can leak between the corresponding piston (30) and the piston chamber (21) in a direction opposite to the moving direction of the corresponding piston (30).

5. The torque transmission mechanism according to claim 3, characterized in that: The one or more piston chambers (21) include a plurality of piston chambers (21) distributed at intervals along the circumferential direction, and the second rotating component includes an annular liquid storage chamber (22), and the liquid storage chamber (22) is connected to each piston chamber (21), so as to be able to supply hydraulic fluid to each piston chamber (21).

6. The torque transmission mechanism according to claim 5, characterized in that: Each piston chamber (21) is connected to the liquid storage chamber (22) through a corresponding communication hole (23), so that the hydraulic fluid in each piston chamber (21) can generate an instantaneous high pressure relative to the hydraulic fluid in the liquid storage chamber (22) when compressed by the corresponding piston (30).

7. The torque transmission mechanism according to claim 5, characterized in that: Each piston chamber (21) is located between the liquid storage chamber (22) and the first rotating component in the radial direction.

8. The torque transmission mechanism according to claim 3, characterized in that: The torque transmission mechanism further comprises one or more elastic members (50), each elastic member (50) being arranged in a corresponding piston cavity (21) and elastically abutting against a corresponding piston (30) in an extending direction.

9. The torque transmission mechanism according to any one of claims 3 to 8, characterized in that: The first rotating component includes one or more guide surfaces (11) facing the second rotating component. Each piston (30) is radially movably installed in the corresponding piston cavity (21) and abuts the corresponding guide surface (11). Each guide surface (11) is recessed in the radial direction away from the second rotating component and has a maximum depth position in the circumferential middle. In the non-torque transmission position, each piston (30) abuts at the maximum depth position of the corresponding guide surface (11). The recessed depth of each guide surface (11) gradually decreases from the corresponding maximum depth position toward both ends in the circumferential direction, thereby pushing the corresponding piston (30) to retract into the second rotating component when the first rotating component and the second rotating component deviate from the non-torque transmission position.

10. The torque transmission mechanism according to claim 9, characterized in that: In a cross section perpendicular to the axial direction, at least a portion of the one or more guide profiles (11) has a concave arc profile, and / or at least a portion of the one or more pistons (30) has an end portion for abutting the corresponding guide profile (11) having a protruding arc profile.

11. The torque transmission mechanism according to claim 9, characterized in that: The first rotating component includes one or more first limiting structures (12), and the second rotating component includes one or more second limiting structures (24). When the first rotating component and the second rotating component rotate relative to each other to the extreme position of the predetermined rotation range, at least a portion of the one or more first limiting structures (12) abuts against the corresponding second limiting structures (24) along the circumferential direction, thereby preventing the first rotating component and the second rotating component from rotating beyond the predetermined rotation range.

12. The torque transmission mechanism according to any one of claims 3 to 8, characterized in that: The one or more pistons (30) include at least one first piston (30a) and at least one second piston (30b) spaced apart along the circumferential direction. Each first piston (30a) and each second piston (30b) are respectively mounted in a corresponding piston chamber (21) so as to be circumferentially movable. Each first piston (30a) can abut against the first rotating component in a first rotational direction along the circumferential direction, and each second piston (30b) can abut against the first rotating component in a second rotational direction opposite to the first rotational direction.

13. The torque transmission mechanism according to claim 12, characterized in that: Each piston (30) has a maximum extension position defined by a corresponding piston chamber (21). During the process in which the first rotating component rotates relative to the second rotating component in any rotation direction and deviates from the non-torque transmission position, a portion of the one or more pistons (30) is pushed by the first rotating component in a direction of retracting toward the second rotating component, and the one or more pistons (30) that are not pushed by the first rotating component can be constrained in the corresponding maximum extension position and separated from the first rotating component.

14. The torque transmission mechanism according to claim 13, characterized in that: The first rotating component includes one or more protrusions (13) protruding toward the second rotating component, and the second rotating component includes one or more recessed portions (25) recessed away from the first rotating component. Each protrusion (13) is radially inserted into a corresponding recessed portion (25), and each piston (30) extends out of the second rotating component from a side wall of a corresponding recessed portion (25) and is capable of abutting against a side wall of a corresponding protrusion (13).

15. The torque transmission mechanism according to claim 14, characterized in that: The at least one first piston (30a) and the at least one second piston (30b) are alternately distributed in the circumferential direction, and any pair of the first piston (30a) and the second piston (30b) that are adjacent in the circumferential direction and away from each other in the extension direction among the one or more pistons (30) constitute a piston pair, and each piston pair is installed in the same piston chamber (21) extending in the circumferential direction.

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