CN114623170A

CN114623170A - Double-clutch linkage device and speed change mechanism

Info

Publication number: CN114623170A
Application number: CN202210339605.8A
Authority: CN
Inventors: 张欣; 吴志先; 张润生; 张权
Original assignee: Qingchi Automobile Beijing Co ltd
Current assignee: Qingchi Automobile Beijing Co ltd
Priority date: 2022-01-20
Filing date: 2022-04-01
Publication date: 2022-06-14
Anticipated expiration: 2042-04-01
Also published as: CN114623170B

Abstract

The invention belongs to the technical field of clutches, and particularly provides a double-clutch linkage device and a speed change mechanism. The double-clutch linkage device comprises a first part, a second part and a third part which can rotate relatively, a sliding part arranged on the first part, a first matching part arranged on the first part, a second matching part arranged on the second part, a third matching part arranged on the third part, a fourth matching part arranged on the sliding part, an elastic part arranged between the first part and the sliding part and a driving mechanism arranged on the third part; the elastic piece can be used for connecting the first matching piece and the second matching piece through the sliding piece, and the driving mechanism can be used for controlling the third matching piece and the fourth matching piece to be connected or separated and controlling the first matching piece and the second matching piece to be separated or connected through the sliding piece. The clutch device is ingenious in design, linkage control of the two clutch units can be achieved through one driving mechanism, and the clutch device has a wide application scene. When the gear shifting device is used for a transmission, power-interruption-free gear shifting can be realized.

Description

Double-clutch linkage device and speed change mechanism

The present application claims priority of the chinese invention patent application entitled "dual clutch linkage device with application date of 20/1/2022 and application number of 2022100672681".

Technical Field

The invention relates to the technical field of clutches, in particular to a double-clutch linkage device and a speed change mechanism.

Background

Clutches are similar in principle to brakes, except that both clutch-connected components are in a movable state, while one of the brake-connected components is in a fixed or stationary state. Thus, a brake may be defined as a clutch in a particular state.

In the field of clutches requiring linkage, multiple clutches need to work in concert. Because each clutch needs to be controlled independently, the requirement on the matching precision among the clutches is high. Taking the field of dual clutch transmissions as an example, as the dual clutch mechanisms disclosed in the invention patents (CN 109661526B, CN 110914563B) granted in china, two clutches are respectively controlled by two independent electronic hydraulic control systems, which require two sets of oil passages and two actuating mechanisms, so that the automatic control system thereof has a complex structure. It is necessary to ensure that one clutch is gradually disengaged while the other clutch is gradually engaged in order to ensure continuous power transmission. Therefore, the two devices need to be controlled synchronously and have high matching precision, so the design difficulty is high. If the two clutches are simultaneously separated, the power is interrupted, and serious equipment defects exist.

Therefore, the double-clutch device in the field of speed change mechanisms has the technical problems of complex structure, high control difficulty, high control precision requirement, easy interruption of power transmission and the like. In addition, in many fields such as machine tools, mechanical equipment, vehicles, and the like, there are technical problems such as a complicated control system structure of a transmission, a high requirement for control accuracy, and the like.

Disclosure of Invention

The invention provides a double-clutch linkage device, which aims to solve the technical problems of complex structure, high control difficulty, high control precision requirement, easiness in power transmission interruption and the like of the conventional double-clutch device. The dual clutch linkage includes a first component; a second part relatively rotatable with the first part about a central axis; a third part relatively rotatable with the first part about the central axis; a slider provided on the first member and configured to be rotatable in synchronization with the first member and to be reciprocally slidable with respect to the first member in a direction parallel to the central axis; a first mating member disposed on the first member and configured to rotate synchronously with the first member and to slide reciprocally relative to the first member in a direction parallel to the central axis; a second mating member disposed on the second component and configured to rotate synchronously with the second component and to slide reciprocally relative to the second component in a direction parallel to the central axis; a third mating member provided on the third member and configured to be synchronously rotatable with the third member and reciprocally slidable with respect to the third member in a direction parallel to the central axis; a fourth mating member provided on the slider and configured to be capable of rotating synchronously with the slider and capable of sliding reciprocally with respect to the slider in a direction parallel to the central axis; an elastic member provided between the first member and the slider and configured to be capable of engaging the first mating member and the second mating member via the slider; the driving mechanism is arranged on the third component and is configured to control the third matching piece and the fourth matching piece to be connected or separated and control the first matching piece and the second matching piece to be separated or connected through the sliding piece.

The first fitting piece and the second fitting piece form a first clutch unit, and the third fitting piece and the fourth fitting piece form a second clutch unit. The elastic element has pretightening force, and in an initial state, the sliding element keeps the first matching element and the second matching element in compression joint under the driving of the elastic element, and in the initial state, the third matching element and the fourth matching element are separated. Accordingly, the first clutch unit is in an engaged state and the second clutch unit is in a disengaged state.

When the states of the two clutch units need to be switched, force is applied to the third fitting piece and the fourth fitting piece through the driving mechanism, so that the third fitting piece and the fourth fitting piece are gradually pressed and connected. In this process, the force of the drive mechanism is transmitted to the slider, so that the force of the slider on the first mating member and the second mating member is reduced. As the acting force of the driving mechanism is gradually increased, the pressing force of the third matching piece and the fourth matching piece is gradually increased, and the pressing force of the first matching piece and the second matching piece is gradually reduced. When the acting force of the driving mechanism is larger than the pretightening force of the elastic piece, the sliding piece is pushed and slides relative to the first component, and accordingly the first matching piece and the second matching piece are completely separated. The first clutch unit is then switched to the disengaged state and, correspondingly, the second clutch unit is switched to the engaged state.

In operation, the first clutch unit is only completely disengaged when the second clutch unit is fully engaged, and vice versa. Therefore, the double-clutch linkage device does not have the condition that the first clutch unit and the second clutch unit are simultaneously separated, namely, the condition that the power transmission is interrupted does not exist. The characteristic has outstanding advantages and wide application scenes, for example, the technical field of the double-clutch transmission, the two clutch units are not separated simultaneously during power transmission, and power interruption can be avoided in the gear shifting process, so that stable operation of the mechanism is ensured.

Compared with the traditional double-clutch linkage device which needs two sets of actuating mechanisms and two oil ways, the double-clutch linkage device can realize linkage control of two clutch units by only one set of driving mechanism, so that the double-clutch linkage device is simple in structure and simple in control logic. During the linkage control process, when the pressing force of the first clutch unit is gradually increased, the pressing force of the second clutch unit is synchronously and gradually reduced. Accordingly, when the pressing force of the first clutch unit is gradually reduced, the pressing force of the second clutch unit is synchronously gradually increased. In the whole linkage control process, the two clutch units are automatically and accurately matched. Therefore, the control logic of the invention is simplified, and the control precision requirement is reduced.

In a preferred embodiment of the above-described double clutch linkage, the first member is rotatable about the central axis. With the above arrangement, the first member serves as one power transmission member that transmits power to the second member and the third member by rotating about the central axis, and at this time, the double clutch linkage in this aspect can form clutch-clutch linkage.

In a preferred embodiment of the double clutch linkage, the second part is held stationary. With the above configuration, the second member is kept stationary on the basis that the first member can rotate, with a stopper formed between the first member and the second member, and the first member can be stopped by the second member when the first mating member is engaged with the second mating member. Therefore, the double-clutch linkage device in the technical scheme forms brake-clutch linkage.

In a preferred embodiment of the double clutch linkage, the third part is held stationary. With the above arrangement, the third member is held stationary while the first member is able to rotate, with the stopper formed between the first member and the third member, and the slider and the first member can be simultaneously stopped by the third member when the third engaging element is engaged with the fourth engaging element. Therefore, the double clutch linkage device in the technical scheme forms clutch-brake linkage.

In a preferred embodiment of the double clutch linkage, the first part is held stationary. With the above arrangement, the first member serves as a braking member, the second member is independently rotatable with respect to the first member, and the third member is independently rotatable with respect to the first member, so that the double clutch linkage in the technical solution forms a double braking linkage, which enables alternative operation of the second member and the third member.

In an optimal technical scheme of the double-clutch linkage device, the first part comprises a first matching portion, the first matching portion is arranged on the first matching portion, the second part comprises a second matching portion, the second matching portion is arranged on the second matching portion, and the second matching portion is sleeved outside the first matching portion. With the above configuration, the second member is partially fitted around the outside of the first member.

In an optimal technical scheme of the above dual clutch linkage device, the first component includes a first matching portion, the first matching portion is disposed on the first matching portion, the second component includes a second matching portion, the second matching portion is disposed on the second matching portion, and the first matching portion is sleeved outside the second matching portion. With the above configuration, the first member is partially fitted around the second member.

In an optimal technical solution of the above dual clutch linkage device, the third component includes a third matching portion, the third matching piece is disposed on the third matching portion, the sliding member includes a fourth matching portion, the fourth matching piece is disposed on the fourth matching portion, and the third matching portion is sleeved on the outside of the fourth matching portion. With the above configuration, the third member is partially fitted on the outside of the slider.

In a preferred technical solution of the above dual clutch linkage device, the third component includes a third matching portion, the third matching portion is disposed on the third matching portion, the sliding member includes a fourth matching portion, the fourth matching portion is disposed on the fourth matching portion, and the fourth matching portion is disposed outside the third matching portion in a sleeved manner. With the above configuration, the slider portion is fitted around the outside of the third member.

In a preferred embodiment of the above dual clutch linkage device, the sliding member includes a sleeve portion, and the sleeve portion is connected to the first member by a spline. The surface of the nesting portion opposite to the first part is provided with the matched internal spline and the matched external spline, through the configuration, the sliding piece can synchronously rotate along with the first part, and meanwhile, the sliding piece can horizontally move relative to the first part, and the connection mode is simple in structure and stable and firm in transmission.

In a preferred embodiment of the above dual clutch linkage device, the first member includes a first position-limiting portion, and the elastic member has a pre-tightening thrust and has one end connected to the first position-limiting portion and the other end connected to the engaging portion. With the above arrangement, in the initial state, the slider is pushed by the elastic member to press-engage the first engaging member and the second engaging member. Because the elastic piece has pretension thrust and is in a compressed state, the size of the elastic piece is smaller after assembly, and the size of the double-clutch linkage device is correspondingly reduced.

In a preferred embodiment of the above dual clutch linkage device, a preload adjustment portion is provided at an end of the elastic member. Through the configuration, the pre-tightening elasticity of the elastic piece can be adjusted by the pre-tightening adjusting part so as to meet the design requirements of different devices.

In a preferred technical solution of the above dual clutch linkage device, the first component includes a second position-limiting portion, the elastic member has a pretension force and one end thereof is connected to the second position-limiting portion, and the other end thereof is connected to the engaging portion. With the above arrangement, in the initial state, the sliding member is pulled by the elastic member to press and engage the first mating member and the second mating member.

In an optimal technical scheme of the dual clutch linkage device, the first fitting piece, the second fitting piece, the third fitting piece and the fourth fitting piece all include a plurality of friction ring pieces, the friction ring pieces of the first fitting piece and the second fitting piece are arranged at intervals, and the friction ring pieces of the third fitting piece and the fourth fitting piece are arranged at intervals. Through the configuration, friction type clutch units are respectively formed between the first fitting piece and the second fitting piece and between the third fitting piece and the fourth fitting piece, and the clutch units have larger action areas and can effectively improve the firmness degree during the joint.

In an optimal technical scheme of the double-clutch linkage device, the friction ring piece of the first fitting piece is connected with the first part through a spline, the friction ring piece of the second fitting piece is connected with the second part through a spline, the friction ring piece of the third fitting piece is connected with the third part through a spline, and the friction ring piece of the fourth fitting piece is connected with the sliding piece through a spline. With the above arrangement, each mating member is connected to the corresponding member by a spline structure.

In a preferred technical solution of the above dual clutch linkage device, the sliding member includes a first pressing portion, the first component includes a third limiting portion, and the third limiting portion is opposite to the first pressing portion and located on two sides of the first fitting piece and the second fitting piece respectively. With the above configuration, the slider and the first member press-engage the first mating member and the second mating member via the first pressing portion and the third stopper portion, respectively. In this preferred technical scheme, the power of elastic component one end is exerted on first part, and the power of the other end acts on the third spacing portion after passing slider, first fitting piece, second fitting piece transmission. Consequently, the elasticity at elastic component both ends all is used in on the first part, can not cause the interference to the motion state of first part, also can not influence the connection between first part, second part, the third part, consequently this preferred technical scheme can effectively promote the stability of whole device.

In a preferred technical solution of the above-mentioned dual clutch linkage device, a pre-tightening adjusting portion is provided on the third limiting portion, and the pre-tightening adjusting portion is attached to the first fitting piece and can move relative to the third limiting portion in a direction parallel to the central axis. The position of the first clutch unit is changed by the pre-tightening adjusting part when the first clutch unit is engaged, and then the position of the sliding part in the initial state is changed, so that the initial length of the elastic part is changed, and the pre-tightening elastic force on the elastic part is adjusted. Thus, the pressing force of the first clutch unit in the initial state is adjusted.

In a preferred embodiment of the above dual clutch linkage device, the third member includes a fourth position-limiting portion, and the fourth position-limiting portion is opposite to the first pressing portion. Along with the continuous movement of the driving end, the driving end drives the sliding part to move for a preset distance through the third matching piece, the fourth matching piece and the second pressing part, so that the first pressing part and the fourth limiting part of the sliding part are abutted. The driving end continuously applies force to the third fitting piece and the fourth fitting piece, so that pressing force of the second clutch unit can be improved. Through the configuration, in the process of continuously applying force to the driving end, the acting force of the driving end can be shared by the fourth limiting part, so that the acting force transmitted to the first component is reduced, and further the unstable operation of the first component caused by overlarge stress is avoided.

In a preferred embodiment of the above-described double clutch linkage device, the slider includes a second pressing portion; the driving mechanism comprises a driving end, the driving end can move along the direction parallel to the central shaft, and the driving end is opposite to the second pressing part and is respectively positioned on two sides of the third matching piece and the fourth matching piece. With the above configuration, the driving mechanism and the sliding member respectively press and engage the third mating member and the fourth mating member via the driving end and the second pressing portion. Along with the continuous removal of drive end, the drive end will drive slider synchronous motion through third fitting piece, fourth fitting piece and second portion of compressing tightly for first fitting piece and second fitting piece are kept away from gradually to first portion of compressing tightly, then first fitting piece and second fitting piece separate gradually. Therefore, in this preferred embodiment, the engagement or disengagement state of the two clutch units can be adjusted simultaneously by controlling the reciprocating movement of the driving end, thereby realizing the interlocking control of the first clutch unit and the second clutch unit.

In a preferred technical solution of the above dual clutch linkage device, the third member includes a fifth limiting portion, and the fifth limiting portion is opposite to the driving end and located at two sides of the second pressing portion respectively. Along with the continuous movement of the driving end, after the driving end drives the sliding part to move for a preset distance through the third matching piece, the fourth matching piece and the second pressing part, the second pressing part is abutted against the fifth limiting part. The driving end continuously applies force to the third fitting piece and the fourth fitting piece, so that pressing force of the second clutch unit can be improved. Through the configuration, in the process of continuously applying force to the driving end, the acting force of the driving end can be shared by the fifth limiting part, so that the acting force transmitted to the first component is reduced, and further the unstable operation of the first component caused by overlarge stress is avoided.

In a preferred embodiment of the double clutch linkage device, the driving mechanism is disposed at a position that is displaced from the position at which the driving mechanism is disposed on the third member to the position at which the driving mechanism is disposed on the first member. Through the configuration, the mounting position of the driving mechanism is replaced to the first part from the third part, the acting force of the driving end and the acting force of the elastic piece act on the first part through the sliding piece, and the resultant force of the driving end and the acting force of the elastic piece only exists in the first part, so that the interference on the motion state of the first part is avoided, and the interference on the assembly among the first part, the second part and the third part is avoided.

The invention also provides a speed change mechanism, which comprises a shell; a planet carrier; a ring gear; and according to any one of the above preferred technical solutions, the ring gear is connected with a first part of the double-clutch linkage, the planet carrier is connected with a second part of the double-clutch linkage, and the shell is connected with a third part of the double-clutch linkage. With the above configuration, the transmission mechanism forms a planetary transmission having a speed ratio of 1 for rigid transmission when the first clutch unit is engaged and the second clutch unit is disengaged; when the first clutch unit is disengaged and the second clutch unit is engaged, the speed ratio of the speed change mechanism is i, and speed change transmission is performed. When the double-clutch linkage device is used for the speed change mechanism, the structure of the speed change mechanism can be effectively simplified, and meanwhile, the power is not interrupted when the speed change mechanism switches the speed ratio, so that the double-clutch linkage device has obvious technical advantages.

Drawings

Preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which:

FIG. 1 is a schematic structural diagram of one embodiment of a dual clutch linkage according to the present invention;

FIG. 2 is a schematic cross-sectional view of the slider taken along line A-A in the embodiment of FIG. 1;

FIG. 3 is a schematic cross-sectional view of the first member taken along line A-A in the embodiment of FIG. 1;

FIG. 4 is a schematic structural diagram of a first embodiment of a dual clutch linkage assembly in accordance with the present invention in state one;

FIG. 5 is a schematic structural view of an embodiment of a dual clutch linkage assembly according to the present invention in states two, three and four;

FIG. 6 is a schematic structural diagram of a first embodiment of a dual clutch linkage assembly in state five in accordance with the present invention;

FIG. 7 is a force analysis diagram of the components of the second clutch unit during engagement in an embodiment of the first dual clutch linkage assembly of the present invention;

FIG. 8 is a force analysis of the components of the first clutch unit during engagement in an embodiment of a first embodiment of the dual clutch linkage assembly according to the present invention;

fig. 9 is a schematic structural view of an embodiment of a dual clutch linkage according to a second embodiment of the present invention.

List of reference numerals:

t, a double-clutch linkage device; 1. a first member; 10. a first mating portion; 11. a first mating member; 101. a first limiting part; 102. a second limiting part; 103. a third limiting part; 1a, an external spline; 2. a second component; 20. a second mating portion; 21. a second mating member; 3. a third component; 30. a third mating portion; 31. a third mating member; 301. a fourth limiting part; 302. a fifth limiting part; 4. a slider; 40. a fourth mating portion; 41. a fourth mating member; 42. a nesting portion; 401. a first pressing part; 402. a second pressing part; 4a, an internal spline; 5. an elastic member; 6. a drive mechanism; 61. a piston; 62. a pressure chamber; 63. an oil inlet; l, a central axis; k1, a first clutch unit; k2, a second clutch unit.

Detailed Description

Preferred embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood by those skilled in the art that these embodiments are only for explaining the technical principle of the present invention, and are not intended to limit the scope of the present invention.

It should be noted that in the description of the present invention, the terms of direction or positional relationship indicated by the terms "left", "right", "inside", "outside", etc. are based on the directions or positional relationships shown in the drawings, which are only for convenience of description, and do not indicate or imply that the device or element must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," "third," "fourth," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. It is also to be understood that, unless expressly stated or limited otherwise, the terms "connected" and "coupled" are intended to be open-ended, meaning that the terms "connected" and "coupled" are used in a generic sense, and are intended to cover, for example, fixedly connected, detachably connected, or integrally connected; the two components can be directly connected and matched, or indirectly connected and matched through an intermediate medium, or communicated inside the two components, or matched with a gap between the two components. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In order to solve the technical problems of complex structure, high control difficulty, high control precision requirement, easy interruption of power transmission and the like of the conventional double-clutch linkage device, the embodiment of the invention provides a double-clutch linkage device T. The double clutch linkage T comprises a first component 1; a second component 2, wherein the second component 2 and the first component 1 can rotate relatively around a central axis L; a third member 3, the third member 3 and the first member 1 being rotatable relative to each other about the central axis L; a slider 4 provided on the first member 1 and configured to be capable of rotating synchronously with the first member 1 and to be capable of sliding reciprocally with respect to the first member 1 in a direction parallel to the central axis L; a first engaging member 11 provided on the first member 1, the first engaging member 11 being configured to be synchronously rotatable with the first member 1 and to be reciprocally slidable with respect to the first member 1 in a direction parallel to the central axis L; a second engaging member 21 provided on the second member 2 and configured to be rotatable in synchronization with the second member 2 and to be slidable reciprocally with respect to the second member 2 in a direction parallel to the central axis L; a third engaging element 31 provided on the third member 3, the third engaging element 31 being configured to be rotatable synchronously with the third member 3 and to be slidable reciprocally with respect to the third member 3 in a direction parallel to the central axis L; a fourth engaging element 41 provided on the slider 4 and configured to be capable of rotating synchronously with the slider 4 and to be capable of sliding reciprocally with respect to the slider 4 in a direction parallel to the central axis L; an elastic member 5 provided between the first member 1 and the slider 4 and configured to be able to engage the first mating member 11 and the second mating member 21 via the slider 4; and the driving mechanism 6 is arranged on the third component 3, and is configured to control the third matching piece 31 and the fourth matching piece 41 to be jointed or separated and control the first matching piece 11 and the second matching piece 21 to be separated or jointed through the sliding piece 4.

Specifically, the phrase "the second member 2 and the first member 1 are relatively rotatable about the central axis L" may mean that the first member 1 rotates and the second member 2 is stationary, that the first member 1 is stationary and the second member 2 rotates, that both the first member 1 and the second member 2 rotate, and that the rotation directions and the rotation speeds of both members are different. Accordingly, the phrase "the third member 3 and the first member 1 are relatively rotatable about the central axis L" may specifically refer to the case where the first member 1 rotates and the third member 3 is stationary, the case where the first member 1 is stationary and the third member 3 rotates, and the case where both the first member 1 and the third member 3 rotate, but the rotational directions and rotational speeds of both are different.

It should be noted that, because the working principle of the clutch and the brake is similar, the difference is only that: both parts of the clutch connection are in a movable state; one of the two parts of the brake connection is in a fixed or stationary state. Thus, a brake may be defined as a clutch in a particular state. Thus, although the subject matter of the present invention is named as a dual clutch linkage, the term "clutch" should be understood broadly, and by combining the states of motion of the first, second and

third members

1, 2 and 3, a variety of types of linkages can be formed. For example, when the first component 1, the second component 2 and the third component 3 are in a rotatable state, the clutch-clutch linkage device is formed; when the first component 1 is in a rotatable state, one of the second component 2 and the third component 3 is in a rotatable state, and the other one is in a fixed or static state, the clutch-brake linkage device is formed; the present invention forms a brake-brake linkage when the first member 1 is in a fixed or stationary state and the second member 2 and the third member 3 are in a rotatable state.

Each type of linkage has a number of specific embodiments, which are further described below by way of examples.

Implementation mode one

FIG. 1 is a schematic structural diagram of an embodiment of a dual clutch linkage according to a first embodiment of the present invention. As shown in fig. 1, the double clutch linkage T includes a first member 1, a second member 2, a third member 3, a slider 4, an elastic member 5, and a driving mechanism 6. Wherein, the sliding part 4 is arranged on the first component 1 in a sliding way and is connected with the first component 1 through the elastic part 5, and the driving mechanism 6 is fixedly arranged on the third component 3. In one or more embodiments, the first component 1 can rotate about a central axis L, the second component 2 can rotate relative to the first component 1, and the third component 3 can rotate relative to the first component 1. The dual clutch linkage in this embodiment is a clutch-clutch linkage.

As shown in fig. 1, the first member 1 is disposed along a central axis L. In one or more embodiments, the body of the first component 1 is a solid shaft body. Alternatively, the body is a hollow shaft. In one or more embodiments, as shown in fig. 1, a first position-limiting portion 101 is provided on the left side of the main body. The first position-limiting portion 101 is annularly sleeved on the main body. Alternatively, the first position-limiting portion 101 is disposed in a sector shape or other suitable shape along the circumference of the main body. As shown in fig. 1, the first position-limiting portion 101 is integrally formed with the main body. Alternatively, the first stopper portion 101 is formed by folding the left end of the main body outward. Alternatively, the first stopper portion 101 is fixed to the main body by welding or other suitable process. Alternatively, the first stopper portion 101 may be detachably mounted to the main body by a screw, a pin, or other suitable connecting structure.

As shown in fig. 1, a first engagement portion 10 is provided on the right side of the main body. The first fitting portion 10 is integrally formed with the main body. Alternatively, the first fitting part 10 is fixed to the main body by welding or other suitable process. Alternatively, the first fitting part 10 is detachably fitted to the main body by a screw thread, a pin shaft, or other suitable connection structure. The radial dimension of the first fitting part 10 is greater than the radial dimension of the main body, and at this time, the first fitting part 10 forms a second limiting part of the first component. It is easily conceivable that the radial dimension of the first fitting part 10 may also be equal to the radial dimension of the main body.

As shown in fig. 1, a first engaging element 11 is provided on the first engaging portion 10. The first fitting part 11 comprises a plurality of friction ring segments arranged parallel to each other. The friction ring sheet can be specifically a rubber ring sheet, a paper-based ring sheet, a resin ring sheet, a carbon fiber ring sheet, a semi-metal ring sheet or other suitable ring sheets. As shown in fig. 1, the friction ring piece is fitted around the outside of the first fitting portion 10. Be equipped with the internal spline parallel with center pin L on the interior rampart of friction ring piece, be equipped with the external spline that matches with the internal spline at the periphery wall of first cooperation portion 10, form sliding connection through the spline between first cooperation portion 10 and the friction ring piece. Each friction ring piece is capable of rotating synchronously with the first engagement portion 10 about the central axis L, and the friction ring piece is capable of sliding reciprocally with respect to the first engagement portion 10 in a direction parallel to the central axis L. It is easily understood that the sliding connection between the first fitting portion 10 and the friction ring plate may be formed by other suitable structures, such as a sliding rod arranged in parallel with the central axis L in the circumferential direction of the first fitting portion 10, a sliding hole matched with the sliding rod arranged on the friction ring plate, and a sliding connection between the first fitting portion 10 and the friction ring plate formed by a sliding rod-sliding hole structure.

As shown in fig. 1, a third stopper 103 capable of stopping the first engaging element 11 is provided on the right side of the first engaging element 10. The third stopper 103 is annularly disposed outside the first engaging portion 10. Alternatively, the third limiting portion 103 is distributed in a sector shape, a rectangular shape or other suitable shapes on the circumference of the first fitting portion 10. As shown in fig. 1, the third position-limiting portion 103 and the first engaging portion 10 are integrally formed. Alternatively, the third limiting portion 103 is formed by folding the end of the first matching portion 10 outward. Alternatively, the third stopper portion 103 is fixed to the first fitting portion 10 by welding or other suitable process. Alternatively, the third stopper portion 103 may be detachably mounted on the first fitting portion 10 by a screw thread, a pin shaft, or other suitable connecting structure.

As shown in fig. 1, the second member 2 is disposed on the right side of the first member 1. The second member 2 is provided with a second engagement portion 20. The second fitting portion 20 is disposed outside the first fitting portion 10 in a ring-cylindrical shape, and the second member 2 is partially disposed outside the first member 1. As shown in fig. 1, the second fitting portion 20 is integrally formed with the second member 2. Alternatively, the second fitting portion 20 is fixed to the second member 2 by welding or other suitable process. Alternatively, the second fitting portion 20 can be detachably fitted to the second member 2 by a screw thread, a pin shaft, or other suitable connecting structure. As shown in fig. 1, a second engaging element 21 is provided on the inner annular wall of the second engaging portion 20. The second fitting part 21 comprises a plurality of friction ring segments arranged parallel to each other. The friction ring sheet can be specifically a rubber ring sheet, a paper-based ring sheet, a resin ring sheet, a carbon fiber ring sheet, a semi-metal ring sheet or other suitable ring sheets. As shown in fig. 1, an inner annular wall of the second fitting portion 20 is provided with an inner spline extending along the central axis L, an outer annular wall of the friction ring piece is provided with an outer spline matching the inner spline, and the second fitting piece 21 and the second fitting portion 20 are slidably connected by the splines. Each friction ring piece is capable of rotating synchronously with the second member 2, and the friction ring pieces are capable of sliding reciprocally with respect to the second fitting portion 20 in a direction parallel to the central axis L. It is easily understood that the sliding connection between the second fitting portion 20 and the friction ring plate may be formed by other suitable structures, such as a sliding rod arranged in parallel with the central axis L at the circumference of the second fitting portion 20, a sliding hole matched with the sliding rod arranged on the friction ring plate, and a sliding connection between the second fitting portion 20 and the friction ring plate formed by a sliding rod-sliding hole structure.

As shown in fig. 1, the friction ring pieces of the first fitting piece 11 and the second fitting piece 21 are arranged at intervals, and accordingly, the first fitting piece 11 and the second fitting piece 21 form a friction-piece-type first clutch unit K1. When the friction ring pieces of the first mating member 11 and the second mating member 21 are closely fitted, the first clutch unit K1 is in an engaged state, and accordingly, the first member 1 and the second member 2 are engaged and rotate synchronously. When the friction ring pieces of the first mating member 11 and the second mating member 21 are separated from each other by a gap, the first clutch unit K1 is in a separated state, and accordingly, the first member 1 is separated from the second member 2.

As shown in fig. 1, the slider 4 has a nesting portion 42. The engaging portion 42 is disposed on the main body of the first member 1 in a cylindrical shape. FIG. 2 is a schematic cross-sectional view of the slider taken along line A-A in the embodiment of FIG. 1; fig. 3 is a schematic cross-sectional view of the first member along line a-a in the embodiment of fig. 1. As shown in fig. 2 and 3, an inner ring wall of the fitting portion 42 is provided with an inner spline 4a parallel to the central axis L, a main body of the first member 1 is provided with an outer spline 1a matching the inner spline 4a, and the slider 4 and the first member 1 are slidably connected by the splines. The slider 4 is capable of rotating synchronously with the first member 1, and the slider 4 is capable of reciprocating sliding with respect to the first member 1 in a direction parallel to the center axis L. It will be readily appreciated that the sliding connection between the socket 42 and the first component 1 may be formed by other suitable arrangements.

As shown in fig. 1, the engaging portion 42 is located between the first position-limiting portion 101 and the first engaging portion 10. The engaging portion 42 is connected to the first position-limiting portion 101 via an elastic member 5. The elastic member 5 is a coil spring. Alternatively, the elastic member 5 is a disc spring, an elastic rubber cylinder, an elastic column, or other suitable elastic member. As shown in fig. 1, the elastic members 5 extend in a direction parallel to the central axis L, and a plurality of elastic members 5 are arranged at equal intervals in the circumferential direction of the main body of the first member 1. One end of the elastic member 5 is fixedly mounted on the engaging portion 42, and the other end is fixedly mounted on the first stopper 101. The elastic member 5 has a pre-tightening thrust. It is easily conceived that when the elastic member 5 is a disc spring, the disc spring is fitted over the outside of the main body. When it is necessary to adjust the biasing force of the elastic member 5, a biasing force adjusting portion (the biasing force adjusting portion is small in size, and is not shown in fig. 1 for the sake of simplicity of the illustrated structure) may be fitted to an end portion of the elastic member 5. Alternatively, the preload adjustment section includes an adjustment handle, an adjustment screw parallel to the central axis L, and a connection plate, wherein the adjustment screw is fitted to the nesting section 42 or the first stopper section 101, the adjustment handle is engaged with the adjustment screw, the connection plate is fixed to the adjustment screw, and the end of the elastic member 5 is connected to the connection plate. The adjusting screw rod can move in the self axial direction by rotating the adjusting handle, and then the adjusting plate is driven to move for a preset distance along the direction parallel to the central shaft L, so that the initial length of the elastic part 5 is changed, and correspondingly, the pre-tightening thrust of the elastic part 5 is changed. It is contemplated that the pretension adjustment portion may also be a combination of structures including a sliding post, a sliding plate, and a pin, or other suitable structures.

As shown in fig. 1, a first pressing portion 401 is provided on the right side of the slider 4. The first pressing portion 401 is annularly provided on the first member 1. The first pressing portion 401 is integrally formed with the slider 4. Alternatively, the first pressing portion 401 is formed by folding the end of the slider 4 outward. Alternatively, the first pressing portion 401 is detachably fitted on the slider 4. As shown in fig. 1, the first pressing portion 401 is opposite to the third stopper portion 103 and can press the first clutch unit K1. Alternatively, when the first clutch unit K1 is pressed, the first pressing portion 401 is engaged with the first mating member 11, and the third limiting portion 103 is engaged with the first mating member 11. It is easily understood that the pretension adjusting portion may also be provided on the third stopper portion 103. Alternatively, the pretension adjustment portion can be brought into abutment with the first fitting member 11. By moving the preload adjustment portion by a predetermined distance in a direction parallel to the center axis L, the initial positions of the first mating member 11, the second mating member 21, and the slider 4 are changed, so that the initial length of the elastic member 5 is changed, thereby adjusting the preload thrust of the elastic member.

As shown in fig. 1, a fourth engaging portion 40 is provided on the left side of the slider 4. The fourth engaging portion 40 is integrally formed with the slider 4. Alternatively, the fourth mating portion 40 is fixed to the slider 4 by welding or other suitable process. Alternatively, the fourth fitting portion 40 is detachably fitted on the slider 4. As shown in fig. 1, a fourth fitting 41 is provided on the fourth fitting portion 40. The fourth fitting member 41 includes a plurality of friction ring pieces arranged in parallel with each other. The friction ring sheet can be specifically a rubber ring sheet, a paper-based ring sheet, a resin ring sheet, a carbon fiber ring sheet, a semi-metal ring sheet or other suitable ring sheets. As shown in fig. 1, the friction ring piece is fitted around the outside of the fourth fitting portion 40. The periphery wall of the fourth matching portion 40 is provided with an external spline parallel to the central shaft L, the inner ring wall of the friction ring piece is provided with an internal spline matched with the external spline, and the fourth matching portion 40 and the friction ring piece are in sliding connection through the splines. Each friction ring piece is capable of rotating synchronously with the fourth engagement portion 40 about the central axis L, and the friction ring piece is capable of sliding reciprocally with respect to the fourth engagement portion 40 in a direction parallel to the central axis L. It will be readily appreciated that the fourth mating portion 40 and the friction ring plate may be slidably connected by other suitable structures.

As shown in fig. 1, a second pressing portion 402 is provided on the left side of the fourth mating portion 40, and the second pressing portion 402 can limit the sliding range of the fourth mating member 41. The second pressing portion 402 has a ring shape. Optionally, the second pressing portion 402 is disposed in parallel with the fourth fitting 41. The second pressing portion 402 is integrally formed with the fourth mating portion 40. Alternatively, the second pressing portion 402 is formed by folding the end of the fourth fitting portion 40 outward, and the folding angle may be 90 degrees. Alternatively, the second compression part 402 is fixed to the fourth mating part 40 by welding or other suitable process. Alternatively, the second pressing portion 402 is detachably fitted on the fourth fitting portion 40.

As shown in fig. 1, a third engaging portion 30 is provided on the third member 3. The third fitting portion 30 is formed by integral molding with the third member 3. Alternatively, the third fitting portion 30 is fixed to the third member 3 by welding or other suitable process. Alternatively, the third fitting portion 30 is detachably fitted on the third member 3. As shown in fig. 1, the third engaging portion 30 is annularly sleeved on the outside of the fourth engaging portion 40. Correspondingly, the third part 3 is partly fitted over the first part 1. A third fitting member 31 is provided on an inner annular wall of the third fitting portion 30. The third fitting member 31 includes a plurality of friction ring pieces arranged in parallel with each other. The friction ring sheet can be specifically a rubber ring sheet, a paper-based ring sheet, a resin ring sheet, a carbon fiber ring sheet, a semi-metal ring sheet or other suitable ring sheets. As shown in fig. 1, an inner spline extending along the central axis L is provided on an inner annular wall of the third fitting portion 30, an outer spline matching the inner spline is provided on an outer annular wall of the friction ring piece, and the third fitting piece 31 and the third fitting portion 30 are slidably connected by the spline. Each friction ring piece is capable of rotating synchronously with the third member 3, and the friction ring pieces are capable of sliding reciprocally with respect to the third fitting portion 30 in a direction parallel to the central axis L. It will be readily appreciated that the sliding connection between the third fitting 30 and the friction ring plate may be formed by other suitable structures.

As shown in fig. 1, the friction ring pieces of the third fitting piece 31 and the fourth fitting piece 41 are arranged at intervals, and accordingly, the third fitting piece 31 and the fourth fitting piece 41 form a friction-piece-type second clutch unit K2. When the friction ring pieces of the third mating member 31 and the fourth mating member 41 are closely fitted, the second clutch unit K2 is in an engaged state, and accordingly, the third member 3 is engaged with the sliding member 4 and the first member 1, and keeps rotating synchronously with each other. When the friction ring pieces of the third fitting member 31 and the fourth fitting member 41 are separated from each other by a gap, the second clutch unit K2 is in a separated state, and accordingly, the third member 3 is separated from the slider 4.

As shown in fig. 1, in the first embodiment, the drive mechanism 6 is mounted on the third member 3. The drive mechanism 6 may be a hydraulic actuator including a piston 61, an oil passage, a pressure chamber 62, and an oil inlet 63. An oil inlet 63 is provided in a surface of the third member 3, an oil passage is arranged inside the third member 3, a pressure chamber 62 extends in a direction parallel to the center axis L, and the piston 61 forms a driving end and is capable of reciprocating in the pressure chamber 62 by the driving of hydraulic oil. Alternatively, the pressure chamber 62 and the piston 61 are in the shape of matching cylinders. As shown in fig. 1, the piston 61 is located at the right side of the second clutch unit K2, and the piston 61 is opposite to the third engaging element 31 and can press the second clutch unit K2. When the second clutch unit K2 is pressed, the piston 61 engages with the third mating member 31, and the second pressing portion 402 can engage with the fourth mating member 41. It is easily conceivable that the drive mechanism 6 can also be a pneumatic drive. Alternatively, the driving mechanism 6 may also be a mechanical transmission structure, for example, the driving mechanism 6 includes a driving rod, and an end portion of the driving rod forms a driving end, and the driving end can be driven by the driving rod to move back and forth along a direction parallel to the central axis L. The drive mechanism 6 may be attached to the first member 1 as required by design. Taking the driving mechanism 6 as an example of a hydraulic actuator, when the driving mechanism 6 is mounted on the first member 1, the oil inlet is provided on the first member 1, the oil passage is arranged inside the first member 1, the pressure chamber 62 extends in a direction parallel to the central axis L, and the piston 61 forms a driving end and is capable of reciprocating in the pressure chamber 62 under the driving of hydraulic oil. Optionally, the piston 61 is opposite the first fitting 11.

As shown in fig. 1, a fourth stopper 301 is provided on the right side of the third member 3. The fourth position-limiting portion 301 is formed by integral molding with the third member 3. Alternatively, the fourth position restricting portion 301 is fixed to the third member 3 by welding or other suitable process. Alternatively, the fourth stopper portion 301 is detachably fitted to the third member 3. As shown in fig. 1, the fourth limiting portion 301 is opposite to the first pressing portion 401, and when the slider 4 slides leftward by a predetermined distance, the first pressing portion 401 can abut on the fourth limiting portion 301.

As shown in fig. 1, a fifth stopper 302 is provided on the left side of the third member 3. The fifth position-limiting portion 302 is integrally formed with the third member 3. Alternatively, the fifth position restricting portion 302 is fixed to the third member 3 by welding or other suitable process. Alternatively, the fifth stopper portion 302 is detachably fitted to the third member 3. As shown in fig. 1, the fifth stopper 302 is annularly provided on the inner circumferential wall of the third member 3. The fifth limiting portion 302 is parallel to and opposite to the second pressing portion 402. When the slider 4 slides leftward by a predetermined distance, the second pressing portion 402 can abut against the fifth stopper portion 302. It is easily understood that the fourth position-limiting portion 301 and the fifth position-limiting portion 302 may be disposed at the same time, may be disposed alternatively, or may be omitted if structural stability permits.

When the double clutch linkage T according to the first embodiment of the present invention is used for a transmission mechanism, the ring gear of the transmission mechanism is connected to the first member 1 of the double clutch linkage T, the carrier of the transmission mechanism is connected to the second member 2 of the double clutch linkage T, and the housing of the transmission mechanism is connected to the third member 3 of the double clutch linkage T. The speed change mechanism is simple in control structure, has the characteristics of continuous power transmission and uninterrupted power during gear shifting, and has obvious technical advantages.

The operation of the dual clutch linkage T in the embodiment of the present invention will be further described with reference to the accompanying drawings. FIG. 7 is a force analysis diagram of the components during engagement of the second clutch unit in an embodiment of the first dual clutch linkage embodiment of the present invention. During the gradual engagement of the second clutch unit K2, the dual clutch linkage T goes through the state two, the state three, and the state four in order from the initial state (state one) to the steady state (state five), and goes through the periods T1, (T1, T2), T2 to (T2, T3) in order from the time point 0 corresponding to the time T in fig. 7, respectively.

FIG. 4 is a schematic structural diagram of an embodiment of a dual clutch linkage according to the present invention in state one. As shown in fig. 4, in the initial state (state one), the slider 4 abuts against the first clutch unit K1 by being driven by the biasing thrust F0 (F0 = F) of the elastic member 5, and the first mating member 11 is press-engaged with the second mating member 21 by the mating of the first pressing portion 401 and the third stopper portion 103. At this time, the first clutch unit K1 is in the fully engaged state, and accordingly, the pressing force F1= F of the first clutch unit K1. In this state, the driving force of the driving mechanism 6 is zero, there is no pressure between the third engaging element 31 and the fourth engaging element 41, and accordingly, the pressing force F2=0 of the second clutch unit K2. When the slider 4 rotates synchronously with the first component 1 relative to the third component 3, there is a gap between the third fitting element 31 and the fourth fitting element 41, and accordingly, the second clutch unit K2 is in a completely disengaged state. In this initial state, the first clutch unit K1 is normally engaged, the second clutch unit K2 is normally disengaged, and the driving force of the drive mechanism 6 is zero. This state one corresponds to the time instant on the abscissa t =0 in fig. 9. It is to be emphasized that in this state, by moving the pretension adjusting portion by a predetermined distance in a direction parallel to the central axis L, changing the initial length of the elastic member 5, the pretension thrust of the elastic member 5 can be adjusted, and thus the engaging capability of the first clutch unit K1 in the initial state is adjusted, so that the dual clutch linkage device of the embodiment of the present invention is applicable to various apparatuses such as vehicles, ships, airplanes, and the like.

When the control state needs to be switched to the first clutch unit K1 disengaged and the second clutch unit K2 engaged, the driving force needs only to be applied to the second clutch unit K2 by the driving mechanism 6. Taking the driving mechanism 6 as a hydraulic driver as an example for analysis, the specific switching process is as follows:

fig. 5 is a schematic structural diagram of an embodiment of the dual clutch linkage according to the first embodiment of the present invention in states two, three, and four. As shown in fig. 5, when the hydraulic oil enters from the oil inlet 63, passes through the oil path, and enters the pressure chamber 62, the piston 61 is pushed to move leftward in a direction parallel to the central axis L, and pushes the third mating member 31 and the fourth mating member 41 to be attached together, at this time, the third mating member 31 and the fourth mating member 41 are only in contact, and the pressing force F2=0 of the second clutch unit K2, at this time, the dual clutch linkage T enters the second state. In the second state, the pressing force of the first clutch unit K1 is not changed, and the pressing force F1= F; the spring force F0 of the spring 5 does not change and its length remains unchanged. This state two corresponds to the time on the abscissa t = t1 in fig. 9.

As the oil pressure in pressure chamber 62 increases, dual clutch linkage T enters state three. In this state three, the third fitting member 31 and the fourth fitting member 41 are pressed together by the second pressing portion 402 and the piston 61, and the pressing force F2 of the second clutch unit K2 gradually increases from 0. Force analysis was performed on slider 4, F0= F1+ F2. Since F2 gradually increases, the pressing force F1 of the first clutch unit K1 gradually decreases from F. While the pressing force F2 of the second clutch unit K2 is increased, the pressing force F1 of the first clutch unit K1 is synchronously decreased, and the variation relationship is inversely correlated. This process achieves that the first clutch unit K1 is gradually released in synchronization with the process of gradually engaging the second clutch unit K2. In the process, the elastic force F0 of the elastic member 5 is not changed, the length thereof is kept unchanged, and the sliding member 4 and the first member 1 do not slide relatively. This state three corresponds to a stage in fig. 9 where the abscissa t is at (t1, t 2).

As the oil pressure in the pressure chamber 62 further increases, the double clutch linkage T enters the state four when the pressing force F2 of the second clutch unit K2 increases to F. In this state four, the pressing force F1 of the first clutch unit K1 is reduced to 0, and accordingly, there is no pressing force between the first engaging element 11 and the second engaging element 21, which are held in zero-pressure contact. In this state four, the spring force F0 of the elastic member 5 does not change, the length thereof remains unchanged, and the slider 4 and the first member 1 do not slide relative to each other. This state four corresponds to the time on the abscissa t = t2 in fig. 9.

As the oil pressure in pressure chamber 62 continues to increase, the dual clutch linkage T enters state five. Fig. 6 is a schematic structural view of an embodiment of the dual clutch linkage according to the first embodiment of the present invention in state five. As shown in fig. 6, the pressing force F2 provided by the piston 61 to the second clutch unit K2 is greater than the pre-tightening force F of the elastic member 5, and the piston 61 drives the third engaging element 31, the fourth engaging element 41, the second pressing portion 402 and the sliding member 4 to move together, so as to cause the elastic member 5 to deform and change in size. In this state five, the elastic force F0 of the elastic member 5 is increased from F to F + Δ F, the pressing force F2 of the second clutch unit K2 is increased from F to F + Δ F, and the pressing force of the first clutch unit K1 is 0. Since the slider 4 moves leftward in a direction parallel to the center axis L, a gap is generated between the first pressing portion 401 and the first clutch unit K1. During the relative rotation of the first component 1 and the second component 2, the first counterpart 11 and the second counterpart 21 are completely disengaged, and accordingly the first clutch unit K1 is completely disengaged and the second clutch unit K2 is completely engaged. This state five corresponds to a stage in fig. 7 where the abscissa t is at (t 2, t 3).

Therefore, in switching the control state, the dual clutch linkage of the embodiment of the invention can achieve the complete disengagement of the first clutch unit K1 and the complete engagement of the second clutch unit K2 only by controlling the drive end to move leftward by the drive mechanism 6 to gradually increase the driving force applied to the second clutch unit K2.

It is to be emphasized that, as shown in fig. 7, the abscissa t is at the stage of (t 3, t 4), the engaging capability of the second clutch unit K2 can be further enhanced by continuously increasing the acting force of the driving mechanism 6 on the second clutch unit K2, so that the dual clutch linkage device according to the embodiment of the present invention is applicable to various apparatuses such as vehicles, ships, and airplanes. When the driving force of the driving mechanism 6 is large, the first pressing portion 401 abuts against the fourth limiting portion 301, and the second pressing portion 402 abuts against the fifth limiting portion 302, so that the acting force of the driving mechanism 6 is transmitted to the third component, the design can avoid the first component 1 from being stressed too much, and the connection stability of the first component 1 is ensured. It is easy to understand that when the driving mechanism 6 is mounted on the first member 1, the force applied by the driving mechanism 6 to the first member 1 through the second clutch unit K2 and the second pressing portion 402 will be the internal force of the first member 1, and the force of the driving mechanism 6 will not affect the stability of the connection between the first member 1 and the third member 3. The arrangement of the drive mechanism 6 on the first part 1 therefore enables the structural stability of the embodiment of the invention to be further improved.

When the dual clutch linkage device is switched from the state of the first clutch unit K1 being disengaged and the state of the second clutch unit K2 being engaged to the state of the first clutch unit K1 being engaged and the state of the second clutch unit K2 being disengaged, the piston 61 is moved rightward gradually, and the acting force of the driving mechanism 6 on the second clutch unit K2 is reduced gradually, so that the dual clutch linkage device T correspondingly goes from the state five to the state four, the state three and the state two and then to the state one. FIG. 8 is a force analysis diagram of the components during engagement of the first clutch unit in an embodiment of the first dual clutch linkage embodiment of the present invention. Taking the driving mechanism 6 as an example of a hydraulic actuator, as shown in fig. 8, state five corresponds to a stage where the abscissa t in fig. 8 is (0, t 1), state four corresponds to a stage where the abscissa t = t1 in fig. 8, state three corresponds to a stage where the abscissa t in fig. 8 is (t1, t 2), state two corresponds to a stage where the abscissa t = t2 in fig. 8, and state one corresponds to a stage where the abscissa t in fig. 8 is t = t 3. It is easy to understand that, in the above time periods, the motion state and the stress state of each component are opposite to the state when the second clutch unit K2 is engaged, and the detailed description is omitted here.

Second embodiment

Fig. 9 is a schematic structural view of an embodiment of a dual clutch linkage according to a second embodiment of the present invention. As shown in fig. 9, unlike the first embodiment, in the second embodiment, the radial dimension of the first fitting portion 10 is larger than that of the main body, and the first fitting portion 10 can have a stopper function, and thus can be used as the second stopper portion 102 to simplify the structure. Alternatively, the second position-limiting portion 102 is welded to the first fitting portion 10. As shown in fig. 9, the elastic member 5 is connected between the nesting portion 42 and the second position-limiting portion 102, that is, the elastic member 5 is connected between the nesting portion 42 and the first matching portion 10. The elastic members 5 extend in a direction parallel to the central axis L, and a plurality of elastic members 5 are arranged at equal intervals in the circumferential direction of the main body of the first member 1. One end of the elastic member 5 is fixedly mounted on the engaging portion 42, and the other end is fixedly mounted on the first fitting portion 10. The elastic element 5 has a pretension force. It is easily understood that, when it is necessary to adjust the pretension force of the elastic member 5, a pretension adjusting portion, to which the end of the elastic member 5 is connected, may be fitted on the fitting portion 42 or the second stopper portion 102. The initial length of the elastic member 5 is changed by moving the pretension adjusting portion by a predetermined distance in a direction parallel to the central axis L, thereby achieving adjustment of the pretension force of the elastic member 5. It is easily understood that the pretension adjusting portion may also be provided on the third stopper portion 103. In the second embodiment, the first stopper 101 can restrict the sliding range of the engaging portion 42 and prevent the engaging portion 42 from slipping off the body of the first member 1. It is easily understood that the first stopper portion 101 may be omitted to simplify the structure if the design requirement permits.

Third embodiment

Unlike the first or second embodiment, in the third embodiment, the first engagement portion 10 is fitted around the outside of the second engagement portion 20. Accordingly, the first part 1 is partly nested outside the second part 2.

The first fitting portion 10 is fixed to the main body of the first member 1 in an annular shape. The first fitting member 11 is provided on the inner annular wall of the first fitting portion 10. An inner annular wall of the first matching part 10 is provided with an inner spline parallel to the central axis L, an outer spline matched with the inner spline is arranged on the first matching piece 11, and the first matching piece 11 and the first matching part 10 are in sliding connection through the splines. The first engaging piece 11 is capable of rotating synchronously with the first member 1 about the central axis L, and the first engaging piece 11 is capable of sliding reciprocally with respect to the first engaging portion 10 in a direction parallel to the central axis L. It is easily conceivable that the first fitting element 11 and the first fitting part 10 may also form a rotatable sliding connection in other suitable ways.

The second mating portion 20 is a solid shaft. Alternatively, the second fitting part 20 is a hollow cylinder. The second fitting member 21 is fitted around the outside of the second fitting portion 20. The second fitting part 20 is provided with an external spline parallel to the central axis L, the inner annular wall of the second fitting part 21 is provided with an internal spline matched with the external spline, and the second fitting part 21 and the second fitting part 20 are in sliding connection through the splines. The second engaging element 21 can rotate synchronously with the second member 2, and the second engaging element 21 can slide reciprocally with respect to the second engaging portion 20 in a direction parallel to the central axis L. It is easily conceivable that the second fitting member 21 and the second fitting part 20 may also form a rotatable sliding connection in other suitable ways.

The first fitting piece 11 and the second fitting piece 21 both include a plurality of friction ring pieces, the friction ring pieces on the first fitting piece 11 and the second fitting piece 21 are arranged at intervals, and the first fitting piece 11 and the second fitting piece 21 form a friction piece type first clutch unit K1.

Example IV

Unlike the first, second, or third embodiment, in the fourth embodiment, the fourth engagement portion 40 is fitted around the outside of the third engagement portion 30. Correspondingly, the slide 4 is partly fitted outside the third part 3.

An inner annular wall of the fourth fitting portion 40 is provided with an inner spline parallel to the central axis L, and the fourth fitting 41 is provided with an outer spline matching the inner spline. The fourth mating part 40 and the fourth mating member 41 form a sliding connection through splines. The fourth fitting member 41 is capable of rotating synchronously with the fourth fitting portion 40 about the central axis L, and the fourth fitting member 41 is capable of sliding reciprocally with respect to the fourth fitting portion 40 in a direction parallel to the central axis L. Alternatively, the second pressing portion 402 is formed by folding the end of the fourth fitting portion 40 inward, and the folding angle may be 90 degrees. The fifth position-limiting portion 302 is disposed on the third engaging portion 30 in a ring shape. Optionally, the fifth position-limiting part 302 is parallel to and matched with the second pressing part 402 oppositely.

The third fitting part 30 is provided with an external spline parallel to the central axis L, and the third fitting part 31 is provided with an internal spline matching the external spline. The third fitting member 31 and the third fitting portion 30 are slidably connected by splines. The third fitting member 31 is fitted around the outside of the third fitting portion 30. The third engaging piece 31 can rotate in synchronization with the third member 3, and the third engaging piece 31 can slide reciprocally in a direction parallel to the center axis L with respect to the third engaging portion 30.

The third fitting piece 31 and the fourth fitting piece 41 each include a plurality of friction ring pieces, the friction ring pieces on the third fitting piece 31 and the fourth fitting piece 41 are arranged at intervals, and the third fitting piece 31 and the fourth fitting piece 41 form a friction plate type second clutch unit K2.

The drive mechanism 6 may be mounted on the third part 3. Alternatively, the drive mechanism 6 is mounted on the first part 1. When the driving mechanism 6 is mounted on the first member 1, taking the driving mechanism 6 as an example of a hydraulic actuator, an oil inlet 63 is provided on the surface of the first member 1, an oil path is arranged inside the first member 1, a pressure chamber 62 extends in a direction parallel to the central axis L, and the piston 61 forms a driving end and can reciprocate in the pressure chamber 62 under the driving of hydraulic oil. The piston 61 is formed with a driving end that is fitted opposite to the second clutch unit K2.

So far, the technical solutions of the present invention have been described in connection with the preferred embodiments shown in the drawings, but it is easily understood by those skilled in the art that the scope of the present invention is obviously not limited to these specific embodiments. Equivalent changes or substitutions of related technical features can be made by those skilled in the art without departing from the principle of the invention, and the technical scheme after the changes or substitutions can fall into the protection scope of the invention.

Claims

1. A dual clutch linkage, comprising:

a first member;

a second part relatively rotatable with the first part about a central axis;

a third part relatively rotatable with the first part about the central axis;

a slider provided on the first member and configured to be capable of rotating synchronously with the first member and capable of sliding reciprocally with respect to the first member in a direction parallel to the central axis;

a first mating member disposed on the first member and configured to rotate synchronously with the first member and to slide reciprocally relative to the first member in a direction parallel to the central axis;

a second mating member disposed on the second component and configured to rotate synchronously with the second component and to slide reciprocally relative to the second component in a direction parallel to the central axis;

a third mating member provided on the third member and configured to be synchronously rotatable with the third member and reciprocally slidable with respect to the third member in a direction parallel to the central axis;

a fourth mating member provided on the slider and configured to be capable of rotating synchronously with the slider and capable of sliding reciprocally with respect to the slider in a direction parallel to the central axis;

an elastic member provided between the first member and the slider and configured to be capable of engaging the first mating member and the second mating member via the slider;

the driving mechanism is arranged on the third component and is configured to control the third matching piece and the fourth matching piece to be connected or separated and control the first matching piece and the second matching piece to be separated or connected through the sliding piece.

2. The dual clutch linkage as claimed in claim 1, wherein the first member is rotatable about the central axis.

3. The dual clutch linkage as claimed in claim 2, wherein the second member remains stationary.

4. The dual clutch linkage as claimed in claim 2, wherein the third member remains stationary.

5. The dual clutch linkage as claimed in claim 1, wherein the first member remains stationary.

6. The dual clutch linkage assembly according to any one of claims 1-5, wherein the first member includes a first engagement portion, the first engagement member being disposed on the first engagement portion, and the second member includes a second engagement portion, the second engagement member being disposed on the second engagement portion, the second engagement portion being disposed around an exterior of the first engagement portion.

7. The dual clutch linkage assembly according to any one of claims 1-5, wherein the first member includes a first engagement portion, the first engagement member being disposed on the first engagement portion, and the second member includes a second engagement portion, the second engagement member being disposed on the second engagement portion, and the first engagement portion being disposed around an exterior of the second engagement portion.

8. The dual clutch linkage assembly according to any one of claims 1-5, wherein the third member includes a third engagement portion, the third engagement element being disposed on the third engagement portion, the slider includes a fourth engagement portion, the fourth engagement element being disposed on the fourth engagement portion, and the third engagement portion being disposed around an exterior of the fourth engagement portion.

9. The dual clutch linkage assembly according to any one of claims 1-5, wherein the third member includes a third engagement portion, the third engagement element being disposed on the third engagement portion, the slider includes a fourth engagement portion, the fourth engagement element being disposed on the fourth engagement portion, and the fourth engagement portion being disposed around an exterior of the third engagement portion.

10. The dual clutch linkage as claimed in any one of claims 1 to 5, wherein the slider includes a socket portion, the socket portion being splined to the first member.

11. The dual clutch linkage assembly of claim 10, wherein the first member includes a first stop portion, the resilient member having a pre-tensioned urging force and having one end connected to the first stop portion and another end connected to the nesting portion.

12. The dual clutch linkage of claim 11, wherein a preload adjustment is provided at an end of the resilient member.

13. The dual clutch linkage assembly of claim 10, wherein the first member includes a second stop portion, the resilient member having a pre-tensioning force and having one end connected to the second stop portion and another end connected to the nesting portion.

14. The dual clutch linkage assembly of any one of claims 1-5, wherein the first, second, third, and fourth mating members each include a plurality of friction ring segments, the friction ring segments of the first and second mating members being spaced apart, and the friction ring segments of the third and fourth mating members being spaced apart.

15. The dual clutch linkage as claimed in claim 14, wherein the friction ring of the first mating member is splined to the first member, the friction ring of the second mating member is splined to the second member, the friction ring of the third mating member is splined to the third member, and the friction ring of the fourth mating member is splined to the slider.

16. The dual clutch linkage as claimed in claim 14, wherein the slider includes a first compression portion and the first member includes a third limiting portion opposite the first compression portion and disposed on either side of the first and second mating members, respectively.

17. The dual clutch linkage assembly of claim 16, wherein a pre-tightening adjustment portion is provided on the third limit portion, the pre-tightening adjustment portion engaging the first engagement member and being movable relative to the third limit portion in a direction parallel to the central axis.

18. The dual clutch linkage of claim 16, wherein the third member includes a fourth limit stop opposite the first hold down portion.

19. The dual clutch linkage as claimed in claim 14, wherein the slider includes a second compression portion; the driving mechanism comprises a driving end, the driving end can move along the direction parallel to the central shaft, and the driving end is opposite to the second pressing part and is respectively positioned on two sides of the third matching piece and the fourth matching piece.

20. The dual clutch linkage of claim 19, wherein the third member includes a fifth stop portion opposite the drive end and on either side of the second compression portion.

21. A dual clutch linkage according to any one of claims 1 to 5, wherein the drive mechanism is located on the first member instead of on the third member.

22. A shifting mechanism, characterized by comprising:

a housing;

a planet carrier;

a ring gear; and

the dual clutch linkage of any one of claims 1-21, the ring gear connected to a first component of the dual clutch linkage, the planet carrier connected to a second component of the dual clutch linkage, and the housing connected to a third component of the dual clutch linkage.