Torque transmission mechanism

Abstract

The invention relates to a torque transmission mechanism. The torque transmission mechanism includes two rotating members capable of abutting against each other in a circumferential direction at two extreme positions of a predetermined rotation range and having a neutral position between the two extreme positions. The torque transmission mechanism further comprises at least one hydraulic cavity set, each hydraulic cavity set comprises a first hydraulic cavity and a second hydraulic cavity which are limited between the two rotating components in the circumferential direction, and the two rotating components compress each first hydraulic cavity in the circumferential direction when rotating relatively in the first rotating direction; each second hydraulic cavity is compressed in the circumferential direction when rotating relatively in the second rotating direction opposite to the first rotating direction; and at least one communication channel, each communication channel is formed in one of the two rotating parts, and in the neutral position, the first hydraulic cavity and the second hydraulic cavity in each hydraulic cavity group are in fluid communication through the corresponding communication channel. The torque transmission mechanism has improved damping and buffering effects.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of transmission. Specifically, the present application relates to a torque transmission mechanism with damping and buffering effect. BACKGROUND

[0002] In the prior art, spline or gear mechanisms are usually used to transmit torque between two rotating parts. Due to the gap between the coupled splines or gears, impact noise of the splines or gears may occur during the operation of the rotating parts. For example, in a hybrid power system in which an internal combustion engine is directly connected to an electric machine, such impact noise is very significant when the electric machine does not output torque. In many application scenarios, on the one hand, it is necessary to meet the requirements of high torque transmission and large damping in a limited space, and on the other hand, it is also desirable to reduce such impact noise. Due to the size limitation, conventional spring damping components cannot provide sufficient damping force and torque capacity in a limited space. For the current rigid transmission mechanism, it is difficult to solve this problem. In the existing transmission, the noise of the splines or gears can be eliminated by always keeping the paired splines or gears in a pressed state through increasing torque. However, this way will correspondingly increase the battery energy consumption and fuel consumption, and increase the working temperature of the battery, thereby affecting the service life of the battery, the electric machine and the related components of the thermal management system. At the same time, it is difficult to solve the above-mentioned problem through the electric machine torque calibration means and it is difficult to ensure good robustness. SUMMARY

[0003] Therefore, the technical problem to be solved by the present application is to provide a torque transmission mechanism with good damping and buffering effect.

[0004] The above technical problem is solved by a torque transmission mechanism according to the present application. The torque transmission mechanism includes two rotating components capable of relative rotation within a predetermined rotation range, the two rotating components being capable of abutting against each other in a circumferential direction at two limit positions of the predetermined rotation range to transmit torque in corresponding directions and having a neutral position located between the two limit positions. The torque transmission mechanism further includes: at least one hydraulic cavity set, each hydraulic cavity set including a first hydraulic cavity and a second hydraulic cavity respectively defined in a circumferential direction between the two rotating components to contain hydraulic fluid, the two rotating components compressing each first hydraulic cavity in a circumferential direction when relatively rotating in a first rotation direction and compressing each second hydraulic cavity in a circumferential direction when relatively rotating in a second rotation direction opposite to the first rotation direction; and at least one communication passage, each communication passage being formed in one of the two rotating components, at the neutral position, the first hydraulic cavity and the second hydraulic cavity in each hydraulic cavity set being in fluid communication by a corresponding communication passage, such that hydraulic fluid in each hydraulic cavity set can flow from a hydraulic cavity being compressed in a circumferential direction to a hydraulic cavity not being compressed in a circumferential direction through the corresponding communication passage. During the relative rotation of the two rotating components (e.g. one gear includes the damping device and the other gear is a rigid gear), the hydraulic fluid in the hydraulic cavities can dampen the torque vibration on the torque transmission path where the two rotating components are located, so that when the two rotating components are subjected to torque fluctuation or torque reversal, the knocking force of the positive and negative tooth surface reversal knocking is reduced, and the impact energy of the gear is reduced.

[0005] According to a preferred embodiment of the present application, each communication passage can include two passage openings for communicating to the corresponding first hydraulic cavity and the corresponding second hydraulic cavity respectively, the predetermined rotation range can be divided into two end sections and an intermediate section connected between the two end sections, the neutral position is located within the intermediate section, the two limit positions are respectively located in the two end sections, when the relative rotation position of the two rotating components is located in the intermediate section, the two passage openings of each communication passage are completely open, during the relative rotation of the two rotating components in either end section towards the corresponding limit position, at least a portion of the passage opening of each communication passage communicating to the hydraulic cavity being compressed in a circumferential direction is gradually closed by the other one of the two rotating components. This means that when the two rotating components are relatively rotated to the vicinity of either limit position, the allowable flow of the communication passage will start to gradually decrease, so that the liquid pressure in the hydraulic cavity being compressed in a circumferential direction increases, thereby further reducing the relative rotation speed of the two rotating components when abutting against each other.

[0006] According to another preferred embodiment of the present application, during the relative rotation of the two rotating components towards the respective limit position within either end section, the passage opening of each communication passage to the hydraulic chamber subjected to circumferential compression can not be completely closed before reaching the respective limit position. This means that the first hydraulic chamber and the second hydraulic chamber remain in communication at all times during the approach of the two rotating components to each other until mutual abutment, whereby the two rotating components can smoothly abut each other.

[0007] According to another preferred embodiment of the present application, during the relative rotation of the two rotating components towards the respective limit position within either end section, the passage opening of each communication passage to the hydraulic chamber subjected to circumferential compression can be completely closed before reaching the respective limit position, so that the two rotating components can transmit torque through the hydraulic fluid enclosed in the respective hydraulic chamber. Since the passage opening of the communication passage has been completely closed before the two rotating components abut each other, the hydraulic fluid in the hydraulic chamber subjected to circumferential compression cannot flow out or can only leak at a very low rate, so that the two rotating components can remain in this state of not abutting each other while stably transmitting torque through the hydraulic fluid, thereby avoiding direct rigid contact of the two rotating components. In this case, preferably, when either passage opening of each communication passage is completely closed, the hydraulic fluid enclosed in the respective hydraulic chamber can gradually leak through the completely closed respective passage opening at a predetermined rate, so that the two rotating components can eventually reach the respective limit position while abutting each other in the circumferential direction. After the passage is completely closed, the transfer of hydraulic fluid through leakage is very slow during which the two rotating components can stably transmit torque through the hydraulic fluid; after a long period of leakage, the two rotating components can slowly approach and eventually abut each other, and the two rotating components in turn begin to directly transmit torque, which makes the contact process of the two rotating components very gentle, thereby significantly reducing the impact force at the time of contact.

[0008] According to another preferred embodiment of the present application, the neutral position can be located at the circumferential center of the predetermined rotation range, and the two end sections can be circumferentially symmetrical about the neutral position. This ensures that the transmission characteristics of the torque transmission mechanism are the same in both rotation directions.

[0009] According to another preferred embodiment of the present application, the torque transmission mechanism can include a plurality of hydraulic chamber groups distributed in the circumferential direction, and the first hydraulic chamber and the second hydraulic chamber of each hydraulic chamber group are adjacent in the circumferential direction. This facilitates the mutual communication of the first hydraulic chamber and the second hydraulic chamber in the same hydraulic chamber group.

[0010] According to another preferred embodiment of the present application, the first rotating member of the two rotating members comprises a first body portion in the shape of a ring and a plurality of first protruding portions extending from the first body portion towards the radially inner side to abut against the second body portion, the second rotating member of the two rotating members comprises a second body portion located radially inside the first body portion and a plurality of second protruding portions extending from the second body portion towards the radially outer side to abut against the first body portion, each first protruding portion is opposite to a corresponding second protruding portion in the circumferential direction, so that each first hydraulic chamber and each second hydraulic chamber is defined circumferentially between a corresponding first protruding portion and a corresponding second protruding portion respectively, and the two channel openings of the same communication channel are formed on the radially inner surface of the first body portion or on the radially outer surface of the second body portion respectively. The channel openings of the communication channel formed on one rotating member can be gradually closed by the corresponding protruding portions of the other rotating member during rotation.

[0011] According to another preferred embodiment of the present application, the torque transmission mechanism can further comprise a reset elastic member abutting between the two rotating members in the circumferential direction, and when the torque transmission mechanism does not transmit torque, the elastic force exerted by the reset elastic member can keep the two rotating members in the neutral position. In addition, when the hydraulic fluid in the hydraulic chamber is insufficient, the reset elastic member can also play a supplementary buffering role.

[0012] According to another preferred embodiment of the present application, the hydraulic fluid contained in the at least one hydraulic chamber group can be a magneto-rheological fluid, and the torque transmission mechanism can further comprise at least one magnetic field generator, each magnetic field generator is arranged at a position corresponding to a corresponding communication channel so as to control the fluid properties of the hydraulic fluid flowing through the corresponding communication channel by a magnetic field. By changing the fluid properties (such as viscosity and density, etc.) of the hydraulic fluid flowing through the communication channel, the speed of relative rotation of the two rotating members can be adjusted, thereby obtaining a suitable buffering effect. BRIEF DESCRIPTION OF DRAWINGS

[0013] The present application will be further described below with reference to the drawings. The same reference signs are used in the drawings to represent the same functional elements. Among them:

[0014] Figure 1 A transverse sectional view of a torque transmission mechanism according to an exemplary embodiment of the present application is shown;

[0015] Figure 2 A transverse sectional view of a torque transmission mechanism according to another exemplary embodiment of the present application is shown;

[0016] Figures 3a to 3c The closing process of the channel opening of the communication channel of the torque transmission mechanism according to an exemplary embodiment of the present application is shown;

[0017] Figure 4 a schematic view showing a passage opening of a communication passage of a torque transmission mechanism according to an exemplary embodiment of the present application; and

[0018] Figure 5 a simulation graph showing a torque transmission mechanism according to an exemplary embodiment of the present application. DETAILED DESCRIPTION

[0019] The following will describe a specific embodiment of a torque transmission mechanism according to the present application with reference to the accompanying drawings. The following detailed description and drawings are used to exemplarily explain the principles of the present application, the present application is not limited to the described preferred embodiments, the scope of protection of the present application is defined by the claims.

[0020] According to an embodiment of the present application, a torque transmission mechanism is provided, which can dampen the torque vibration on a torque transmission path where two rotating components are located by hydraulic fluid, thereby reducing impact and noise.

[0021] Figure 1 and Figure 2 respectively show a cross-sectional view of a torque transmission mechanism according to two different exemplary embodiments of the present application. As shown in Figure 1 and Figure 2 The torque transmission mechanism includes two rotating components, i.e. a first rotating component 10 and a second rotating component 20. The first rotating component 10 and the second rotating component 20 are coaxially arranged and can relatively rotate within a predetermined rotation range about a common central axis. The predetermined rotation range refers to the allowable range of the relative rotation position of the two rotating components, i.e. the allowable relative rotation range of one rotating component with respect to the other rotating component. The predetermined rotation range has two limit positions, i.e. two circumferential end points of the predetermined rotation range. When the two rotating components are located at either limit position, the two rotating components abut each other along the circumference, thereby being able to transmit torque in the corresponding direction. The corresponding direction here refers to the torque direction that forces the two rotating components to remain abutting at the current limit position. In the predetermined rotation range, there is a neutral position located between the two limit positions (not coinciding with the limit positions). At the neutral position, the two rotating components cannot directly abut each other along the circumference, so the two rotating components can start to relatively rotate from the neutral position towards either rotation direction, i.e. towards either limit position.

[0022] The torque transmission mechanism further includes at least one hydraulic chamber set and at least one communication passage 30. Each hydraulic chamber set includes a first hydraulic chamber Cl and a second hydraulic chamber C2 defined circumferentially between two rotating members to accommodate hydraulic fluid, respectively. The two rotating members circumferentially compress each first hydraulic chamber Cl when relatively rotated in one rotational direction (may be referred to as first rotational direction) and circumferentially compress each second hydraulic chamber C2 when relatively rotated in another opposite rotational direction (may be referred to as second rotational direction).

[0023] Each communication passage 30 is formed in one of the two rotating members. For example, in the embodiment shown in FIG. 1, each communication passage 30 is formed in the radially outer first rotating member 10, while in the embodiment shown in FIG. 2, each communication passage 30 is formed in the radially inner second rotating member 20. Figure 1 In the embodiment shown in FIG. 1, each communication passage 30 is formed in the radially outer first rotating member 10, while in the embodiment shown in FIG. 2, each communication passage 30 is formed in the radially inner second rotating member 20. Figure 2 In the embodiment shown in FIG. 1, each communication passage 30 is formed in the radially outer first rotating member 10, while in the embodiment shown in FIG. 2, each communication passage 30 is formed in the radially inner second rotating member 20.

[0024] The hydraulic chambers can be formed between the two rotating members in various ways. For example, as shown in FIG. 1, each first hydraulic chamber Cl and each second hydraulic chamber C2 can be defined circumferentially between the first rotating member 10 and the second rotating member 20 by a first annular groove 11 and a second annular groove 21, respectively. Figure 1 and Figure 2As shown, the first rotating member 10 can include a first body portion 11 and a plurality of first protruding portions 12. The first body portion 11 is a substantially annular portion around the central axis. The second rotating member 20 can correspondingly include a second body portion 21 located radially inside the first body portion 11 and a plurality of second protruding portions 22. The second body portion 21 is a substantially disc or annular portion around the central axis. These first protruding portions 12 respectively extend from the first body portion 11 towards the radially inner side to abut against the second body portion 21, while these second protruding portions 22 respectively extend from the second body portion 21 towards the radially outer side to abut against the first body portion 11. A respective seal 40 can be provided between the contact surface of each protruding portion and the opposite body portion to achieve fluid sealing. Each first protruding portion 12 is opposite to a respective second protruding portion 22 in the circumferential direction, and each hydraulic chamber is defined circumferentially between a respective first protruding portion 12 and the opposite second protruding portion 22. Here, the circumferential distribution direction (clockwise or counterclockwise) of the first protruding portions 12 and the second protruding portions 22 for defining the first hydraulic chambers Cl is opposite to that of the first protruding portions 12 and the second protruding portions 22 for defining the second hydraulic chambers C2. Preferably, the two limit positions of the predetermined rotation range can be defined by the first protruding portions 12 and the second protruding portions 22 facing each other: in one limit position, all the first protruding portions 12 and the second protruding portions 22 defining the first hydraulic chambers Cl abut against each other in the circumferential direction, while in the other limit position, all the first protruding portions 12 and the second protruding portions 22 defining the second hydraulic chambers C2 abut against each other in the circumferential direction. Alternatively, the two limit positions of the predetermined rotation range can also be defined by stop structures formed at other positions of the two rotating members.

[0025] In order to close these hydraulic chambers from both axial sides, the torque transmission device can further include two cover plates (not shown). The two cover plates are respectively located at both axial sides of the two rotating members to close all the hydraulic chambers, and each cover plate is fixed to one of the two rotating members, so it can be regarded as a part of the rotating member to which it is fixed. Preferably, each protruding portion on one rotating member can respectively cooperate with two protruding portions located on the other rotating member at both circumferential sides to define two different hydraulic chambers at both circumferential sides thereof, one of which is the first hydraulic chamber Cl and the other is the second hydraulic chamber C2. It should be understood that the above structure described in combination with Figure 1 and Figure 2 The above structure described above is only illustrative, and the two rotating members of the present application can also have other structures as long as they can provide hydraulic chambers that meet the above torque transmission relationship.

[0026] When the torque transmission mechanism includes a plurality of hydraulic chamber groups distributed along the circumferential direction, the first hydraulic chamber Cl and the second hydraulic chamber C2 of each hydraulic chamber group are preferably adjacent in the circumferential direction. In addition, the hydraulic chamber groups can preferably be uniformly distributed in the circumferential direction.

[0027] Each communication passage 30 includes two passage openings, one of which is in communication with the corresponding first hydraulic chamber C1 and the other of which is in communication with the corresponding second hydraulic chamber C2. The passage opening in communication with the first hydraulic chamber C1 can be referred to as the first passage opening, and the passage opening in communication with the second hydraulic chamber C2 can be referred to as the second passage opening. Each communication passage 30 extends inside the first rotary member 10 or inside the second rotary member 20 and between the corresponding two passage openings, thereby forming a through hole through the corresponding rotary member. In the preferred embodiment, the predetermined rotation range can be divided into three sections: two end sections and a middle section connected between the two end sections. The neutral position is located in the middle section. The two extreme positions are located in the two end sections, thereby constituting the mutually remote end points of the two end sections, respectively. When the relative rotation position of the two rotary members is located in the middle section, the two passage openings of each communication passage 30 are in a fully open state (i.e., not at all obstructed), whereby the hydraulic fluid can flow between the first hydraulic chamber C1 and the second hydraulic chamber C2 at the maximum flow rate (the flow direction being determined by the direction of relative rotation). Figure 1 During the process of relative rotation of the two rotary members in either end section toward the corresponding extreme position (i.e., the extreme position located in that end section), one of the first hydraulic chamber C1 and the second hydraulic chamber C2 of each hydraulic chamber group will be circumferentially compressed, at which time at least a portion of the passage opening of each communication passage 30 in communication with the compressed hydraulic chamber is gradually closed by the other rotary member (i.e., the other rotary member opposite to the rotary member in which the communication passage 30 is formed, which is thus capable of rotating relative to the passage opening of the communication passage 30). For example, in the specific embodiment shown in Figs. 1 and 2, the first rotary member 10 can close at least a portion of the corresponding passage opening on the second rotary member 20 by means of its own protrusion, and vice versa. Figure 2 and Figure 3a This means that, in any end section of the predetermined rotation range, the passage opening in communication with the hydraulic chamber whose volume is reduced (relative to the volume at the neutral position) is at least partially obstructed, and the obstructed area gradually increases as the volume of the hydraulic chamber is reduced (i.e., as the two rotary members are relatively rotated toward the extreme position that makes the volume of the hydraulic chamber reach the minimum state), until it is completely obstructed or until the corresponding extreme position is reached and relative rotation cannot continue. Therefore, when the two rotary members are relatively rotated to the vicinity of either extreme position, the allowable flow of the communication passage 30 will begin to gradually decrease, so that the liquid pressure in the circumferentially compressed hydraulic chamber increases, thereby further damping the relative rotation speed of the two rotary members when they abut against each other.

[0028] In a preferred embodiment, in order to ensure that the torque transmission mechanism has the same transmission characteristics in both rotation directions, the neutral position can preferably be located at the circumferential center of the predetermined rotation range, and the two end sections can also preferably be circumferentially symmetrical about the neutral position. That is, the circumferential positions of the two passage openings of the same communication passage 30 can also preferably be circumferentially symmetrical about the neutral position.

[0029] In order to facilitate the gradual blocking of the passage openings, the two passage openings of the communication passage 30 can be respectively formed on the circumferentially extending wall surface of the corresponding hydraulic chamber. For example, in the case of the embodiments shown in Figure 1 and Figure 2 , the two passage openings of the same communication passage 30 can be respectively formed on the radially inner surface of the first body portion 11 Figure 1 , or can also be respectively formed on the radially outer surface of the second body portion 21 Figure 2 . Alternatively, the two passage openings of the same communication passage 30 can be respectively formed on one cover plate (not shown). The scheme of forming the passage openings on the first body portion or the second body portion is generally more preferred, because the body portion generally has more sufficient size to form the passage.

[0030] The circumferential positions of the passage openings are different, and the process of the opening state of the passage openings changing with the rotation position of the two rotating components in the end section is also different. In one case, during the relative rotation of the two rotating components in either end section towards the corresponding limit position, the passage opening of each communication passage 30 that communicates to the hydraulic chamber that is circumferentially compressed is not completely closed before reaching the corresponding limit position. This can mean that the passage opening is just completely closed when reaching the limit position, or can also mean that the passage opening is still not completely closed when reaching the limit position. For example, in the specific embodiments shown in Figure 1 and Figure 2 , the passage opening can be completely formed on the circumferentially extending surface of the corresponding hydraulic chamber, such as the radially inner surface of the first body portion 11 or the radially outer surface of the second body portion 21 or the axial side surface of the cover plate, and the passage opening is circumferentially adjacent to the corresponding protrusion, so that when the two protrusions defining the corresponding hydraulic chamber abut each other, the passage opening is just completely blocked. If it is desired that the passage opening is still not completely closed when reaching the limit position, the passage opening can be extended all the way to a surface area that is still not in contact with the other rotating component at the limit position.

[0031] Figure 1The closing process of the passage opening being shielded during the relative rotation of the two rotary components towards a certain limit position is shown. In each figure, the relative rotation position of the two rotary components is shown on the left side, and the corresponding closing state of the passage opening is shown on the right side, wherein the circle represents the position of the passage opening, the square represents the position of the part (in this embodiment, the top end face of the corresponding protrusion) of the other rotary component for shielding the passage opening, and the hatching represents the unshielded part of the passage opening. In Figure 2 , the two rotary components are located in the middle section, the circle and the square are separated from each other, the passage opening is completely open, and the maximum allowable flow rate of the communication channel 30; in Figures 3a to 3c , the two rotary components are located in one end section but have not reached the corresponding limit position, the circle and the square partially overlap, a part of the passage opening is closed, and the allowable flow rate of the communication channel 30 is reduced; in Figure 3a , the two rotary components reach the limit position, the circle is completely shielded by the square, the passage opening is just completely closed, and the allowable flow rate of the communication channel 30 is substantially zero.

[0032] In another case, during the relative rotation of the two rotary components towards the corresponding limit position in either end section, the passage opening of each communication channel 30 to the hydraulically compressed hydraulic cavity is already completely closed before reaching the corresponding limit position, so that the two rotary components can transmit torque by the hydraulic fluid enclosed in the corresponding (hydraulically compressed) hydraulic cavity. This means that when the passage opening is just completely closed, the two rotary components have not yet abutted together in the circumferential direction. However, since the communication channel 30 has already been completely closed at this time, the hydraulic fluid cannot flow out of the hydraulically compressed hydraulic cavity or can only leak at a very low rate, so the two rotary components can remain in this state of not abutting each other and stably transmit torque by the hydraulic fluid. If the sealing effect of the surface for closing the passage opening is high enough, the two rotary components can remain in this state of not abutting each other and stably transmit torque; if the sealing effect of the surface for closing the passage opening is not absolutely ideal, then when any passage opening of each communication channel 30 is completely closed, the hydraulic fluid enclosed in the corresponding hydraulic cavity can still gradually leak to the corresponding other hydraulic cavity through the corresponding passage opening at a predetermined rate, which enables the two rotary components to finally reach the corresponding limit position and abut each other in the circumferential direction after a predetermined time, thereby starting to directly transmit torque. Since the speed of such leakage is very small (relative to the at least partially open communication channel 30), the process of the two rotary components finally achieving abutment with each other is also very slow. This makes the contact process of the two rotary components very gentle, thereby significantly reducing the impact force at the time of contact.

[0033] Figure 3b The cross-sectional shape of the passage opening in the middle is only schematic. As Figure 3cAs shown, the passage opening can have different cross-sectional shapes, such as circular, square, trapezoidal or other shapes. By designing different shapes of cross-section, the rate of change of the enclosed area of the passage opening with the rotational position can be different, which mainly depends on how the cross-sectional dimension of the passage opening in the direction perpendicular to the circumferential direction varies with the circumferential position.

[0034] In a preferred embodiment, the torque transmission mechanism can further comprise one or more reset elastic members (not shown). Each reset elastic member abuts between the two rotating components in the circumferential direction, and when the torque transmission mechanism does not transmit torque, the elastic force exerted by the reset elastic member can keep the two rotating components in the neutral position. When there is only one reset elastic member in the torque transmission mechanism, this reset elastic member can provide reset force in both rotational directions through two deformation states of stretching and contraction, respectively. When there are multiple reset elastic members in the torque transmission mechanism, each reset elastic member can provide reset force in both rotational directions, or can only provide reset force in one direction, that is, part of the reset elastic members provide elastic force resisting relative rotation of the two rotating components in the first rotational direction, and the other part provides elastic force resisting relative rotation of the two rotating components in the second rotational direction. For example, the elastic reset members can be coil springs or torsion springs. The coil spring can be a straight coil spring or an arc-shaped coil spring, which can be installed in the corresponding hydraulic chamber, for example, and can directly abut between the circumferentially opposite two side walls of the hydraulic chamber (the two side walls are respectively provided by the two rotating components) in the rotational direction. The torsion spring can be installed on the cover plate of the two rotating components or other components such as flanges connected to the rotating components. A single torsion spring can have two prongs inserted into fixed slots on the two rotating components, respectively, so as to provide reset force in both rotational directions through two deformation states of stretching and contraction. The reset elastic member not only keeps the two rotating components in the neutral position, but also plays a supplementary buffering role, which is particularly advantageous when the hydraulic fluid in the hydraulic chamber is insufficient.

[0035] In any of the above embodiments, the hydraulic fluid contained in the hydraulic chambers can preferably be a magneto-rheological fluid. Meanwhile, the torque transmission mechanism can further comprise at least one magnetic field generator 50, each of which is arranged at a position corresponding to the respective communication passage 30, so as to be able to control the fluid property of the hydraulic fluid flowing through the respective communication passage 30 by means of a magnetic field. The magnetic field generator 50 can for example be an electromagnetic coil, which is able to generate an electromagnetic field when energized and to vary the magnitude of the magnetic field based on the electric current. By varying the magnitude of the magnetic field, the magnetic field generator 50 can control the fluid property (e.g. the viscosity and density of the hydraulic fluid, etc.) of the hydraulic fluid in the communication passage 30, so as to adjust the rate at which the hydraulic fluid is transferred between the two hydraulic chambers. This means that the magnetic field generator 50 can adjust the damping and dynamic stiffness effects of the hydraulic chambers and control the approach process of the two rotating components, thereby achieving a better cushioning and damping effect on the transmission path.

[0036] The effect of the torque transmission mechanism according to the present application can be verified by simulation experiments. For example, the inventors have verified the damping effect of such a torque transmission mechanism by means of a multi-body dynamic simulation method. As shown in the graph of the simulation experiment of a vehicle transmission in Figures 3a to 3c The impact force between the rotating components is significantly reduced, as shown in the graph of the simulation experiment of a vehicle transmission in

[0037] The torque transmission mechanism according to the present application can damp the torque vibration by means of the hydraulic fluid in the hydraulic chambers, which not only enables the decoupling of the two rotating components in the non-torque transmission state, but also reduces the impact force when the two rotating components abut against each other, thereby reducing the noise and lowering the risk of damaging the rotating components. Furthermore, since the hydraulic fluid reciprocates in the two hydraulic chambers, it is not necessary to additionally provide a fluid supply source, and the hydraulic fluid does not need to be frequently replenished. Moreover, the dynamic process when the two rotating components abut against each other can be controlled by means of the position of the passage opening of the communication passage and the fluid property of the hydraulic fluid, so as to facilitate obtaining better dynamic characteristics.

[0038] Although possible embodiments have been described in the above description by way of example, it is understood that there are still many variations of the embodiments which fall within the scope of the present application. Moreover, it is understood that the example embodiments are only examples and are not limiting in any way to the scope of the present application, applications and configurations. The foregoing description is more of a practical guidance for a skilled person to transform at least one example embodiment, wherein various changes can be made without departing from the scope of the claims, especially with respect to the function and structure of the components.

[0039] Figure 4 Figure 5 List of reference signs

[0040] 10 first rotating member

[0041] 11 first body portion

[0042] 12 first protruding portion

[0043] 20 second rotating member

[0044] 21 second body portion

[0045] 22 second protruding portion

[0046] 30 connecting passage

[0047] 40 seal member

[0048] 50 magnetic field generator

[0049] C1 first hydraulic chamber

[0050] C2 second hydraulic chamber

Claims

1. A torque transmission mechanism comprising two rotating members capable of relative rotation within a predetermined rotation range, the two rotating members being capable of abutting each other in a circumferential direction at two limit positions of the predetermined rotation range to transmit torque in a corresponding direction and having a neutral position located between the two limit positions, characterized in that, the torque transmission mechanism further comprises: at least one hydraulic cavity group, each hydraulic cavity group comprising a first hydraulic cavity (C1) and a second hydraulic cavity (C2) respectively defined in a circumferential direction between the two rotating members to contain hydraulic fluid, the two rotating members compressing each first hydraulic cavity (C1) in a circumferential direction when relatively rotating in a first rotation direction and compressing each second hydraulic cavity (C2) in a circumferential direction when relatively rotating in a second rotation direction opposite to the first rotation direction; and at least one communication passage (30), each communication passage (30) being formed in one of the two rotating members, at the neutral position, the first hydraulic cavity (C1) and the second hydraulic cavity (C2) in each hydraulic cavity group being in fluid communication by a corresponding communication passage (30) so that the hydraulic fluid in each hydraulic cavity group can flow from the hydraulic cavity being compressed in a circumferential direction to the hydraulic cavity not being compressed in a circumferential direction through the corresponding communication passage (30).

2. The torque transfer mechanism of claim 1, wherein, Each communication passage (30) comprises two passage openings for communicating to the corresponding first hydraulic cavity (C1) and the corresponding second hydraulic cavity (C2) respectively, the predetermined rotation range is divided into two end sections and an intermediate section connected between the two end sections, the neutral position is located within the intermediate section, the two limit positions are located in the two end sections respectively, when the relative rotation position of the two rotating members is located in the intermediate section, both passage openings of each communication passage (30) are completely open, during the relative rotation of the two rotating members in either end section towards the corresponding limit position, at least a part of the passage opening of each communication passage (30) communicating to the hydraulic cavity being compressed in a circumferential direction is gradually closed by the other one of the two rotating members.

3. The torque transmitting mechanism of claim 2, wherein, During the relative rotation of the two rotating members in either end section towards the corresponding limit position, before reaching the corresponding limit position, the passage opening of each communication passage (30) communicating to the hydraulic cavity being compressed in a circumferential direction is not completely closed.

4. The torque transmission mechanism of claim 2, wherein During the relative rotation of the two rotating members in either end section towards the corresponding limit position, before reaching the corresponding limit position, the passage opening of each communication passage (30) communicating to the hydraulic cavity being compressed in a circumferential direction is completely closed so that the two rotating members can transmit torque by the hydraulic fluid enclosed in the corresponding hydraulic cavity.

5. The torque transmitting mechanism of claim 4, wherein, When either passage opening of each communication passage (30) is completely closed, the hydraulic fluid enclosed in the corresponding hydraulic cavity can gradually leak through the corresponding passage opening being completely closed at a predetermined rate so that the two rotating members can eventually reach the corresponding limit position to abut each other in a circumferential direction.

6. The torque transmitting mechanism of claim 2, wherein, The neutral position is located at the circumferential center of the predetermined rotation range, and the two end sections are circumferentially symmetrical about the neutral position.

7. The torque transmitting mechanism of claim 1, wherein The torque transmission mechanism comprises a plurality of hydraulic cavity groups distributed in circumferential intervals, and a first hydraulic cavity (C1) and a second hydraulic cavity (C2) of each hydraulic cavity group are circumferentially adjacent.

8. The torque transmitting mechanism of claim 2, wherein, The first rotating component (10) of the two rotating components comprises an annular first body portion (11) and a plurality of first protruding portions (12), the second rotating component (20) of the two rotating components comprises a second body portion (21) located radially inside the first body portion (11) and a plurality of second protruding portions (22), the plurality of first protruding portions (12) extend from the first body portion (11) to the radially inner side to abut the second body portion (21), the plurality of second protruding portions (22) extend from the second body portion (21) to the radially outer side to abut the first body portion (11), each first protruding portion (12) is circumferentially opposite to a corresponding second protruding portion (22), so that each first hydraulic cavity (C1) and each second hydraulic cavity (C2) are respectively defined circumferentially between the corresponding first protruding portion (12) and the corresponding second protruding portion (22), and two channel openings of the same communication channel (30) are respectively formed on the radially inner surface of the first body portion (11) or on the radially outer surface of the second body portion (21).

9. The torque transfer mechanism of claim 1, wherein, The torque transmission mechanism further comprises a reset elastic member, which is circumferentially abutted between the two rotating components, and when the torque transmission mechanism does not transmit torque, the elastic force of the reset elastic member can keep the two rotating components at the neutral position.

10. The torque transmission mechanism according to any one of claims 1 to 9, characterized in that, The hydraulic fluid contained in the at least one hydraulic cavity group is a magneto-rheological fluid, and the torque transmission mechanism further comprises at least one magnetic field generator (50), each magnetic field generator (50) is arranged at a position corresponding to a corresponding communication channel (30) to control the fluid property of the hydraulic fluid flowing through the corresponding communication channel (30) by a magnetic field. The neutral position is located at the circumferential center of the predetermined rotation range, and the two end sections are circumferentially symmetrical about the neutral position. The torque transmission mechanism comprises a plurality of hydraulic cavity groups distributed in circumferential intervals, and a first hydraulic cavity (C1) and a second hydraulic cavity (C2) of each hydraulic cavity group are circumferentially adjacent. The first rotating component (10) of the two rotating components comprises an annular first body portion (11) and a plurality of first protruding portions (12), the second rotating component (20) of the two rotating components comprises a second body portion (21) located radially inside the first body portion (11) and a plurality of second protruding portions (22), the plurality of first protruding portions (12) extend from the first body portion (11) to the radially inner side to abut the second body portion (21), the plurality of second protruding portions (22) extend from the second body portion (21) to the radially outer side to abut the first body portion (11), each first protruding portion (12) is circumferentially opposite to a corresponding second protruding portion (22), so that each first hydraulic cavity (C1) and each second hydraulic cavity (C2) are respectively defined circumferentially between the corresponding first protruding portion (12) and the corresponding second protruding portion (22), and two channel openings of the same communication channel (30) are respectively formed on the radially inner surface of the first body portion (11) or on the radially outer surface of the second body portion (21). The torque transmission mechanism further comprises a reset elastic member, which is circumferentially abutted between the two rotating components, and when the torque transmission mechanism does not transmit torque, the elastic force of the reset elastic member can keep the two rotating components at the neutral position. The hydraulic fluid contained in the at least one hydraulic cavity group is a magneto-rheological fluid, and the torque transmission mechanism further comprises at least one magnetic field generator (50), each magnetic field generator (50) is arranged at a position corresponding to a corresponding communication channel (30) to control the fluid property of the hydraulic fluid flowing through the corresponding communication channel (30) by a magnetic field.

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