A linkage interlocking shift actuator and working method thereof

Abstract

The present invention relates to a linkage interlocking shift actuator and a working method thereof, comprising a first clutch, the first clutch comprising a first clutch drum and a clutch hub located in the middle of the first clutch drum, the first clutch is engaged when the first clutch drum moves to the left, the first clutch drum is provided with a first outer plate, an inner plate and a second outer plate from left to right in sequence on the inner side, the inner plate is connected to the clutch hub and has through holes uniformly distributed along the circumferential direction, a first rolling body is provided in the through hole, the second outer plate is connected to the first clutch drum and a ramp-type annular raceway matching the first rolling body is provided on the left end face; and a second clutch is also provided; the second clutch comprises a second clutch drum located outside the first clutch drum and a third outer plate located on the right side of the first clutch drum. The present invention does not provide a friction pair, greatly reduces the cost of the clutch assembly, and does not cause the phenomenon of friction pair burning; it can reduce failures, extend the service life, and has a compact structure and a small assembly.

Description

Technical Field

[0001] The invention relates to the field of transmission shift actuators, in particular to a linkage interlocking shift actuator and a working method thereof. Background Art

[0002] In the field of traditional automobile transmission shift actuators, basically one clutch or brake corresponds to one actuator, and the clutch is basically provided with a friction pair, which is not only costly, energy-intensive, and large in size, but also generates a large amount of heat and wear debris during the sliding and grinding process of the friction pair, which has an adverse effect on the clutch, transmission, or related mechanical equipment. The one-to-one setting of the clutch and the actuator is prone to unnecessary simultaneous engagement or separation of two clutches, resulting in locking, friction pair burnout, or disengagement and inability to output power. In order to reduce consumption, reduce costs, and reduce volume, and at the same time prevent the harmful simultaneous engagement or separation of two clutches, a linkage shift actuator is used, but in the traditional linkage shift mechanism, one actuator needs to provide power to two actuators or still retain two actuators, and a friction pair also exists; in order to reduce the power requirements of the actuator, reduce costs and volume, the rolling ramp technology is also used, but the traditional rolling ramp technology only solves the problem of reducing the power requirements of the actuator, and other problems of the traditional shift actuator are not solved. Summary of the invention

[0003] In view of this, the purpose of the present invention is to provide a linkage interlocking shift actuator without a friction pair and a working method thereof, so as to reduce the cost of the clutch assembly, avoid the friction pair burning phenomenon, reduce energy loss and increase efficiency.

[0004] The present invention is implemented by the following scheme: a linkage interlocking shift actuator, including a first clutch, the first clutch including a first clutch drum and a clutch hub located in the middle of the first clutch drum, the first clutch is engaged when the first clutch drum moves to the left, the first clutch drum is provided with a first outer plate, an inner plate and a second outer plate from left to right in sequence on the inner side, the inner plate is connected to the clutch hub and has through holes uniformly distributed along the circumferential direction, a first rolling body is provided in the through hole, the second outer plate is connected to the first clutch drum and a ramp-type annular raceway cooperating with the first rolling body is provided on the left end face, the bottom surface of the ramp-type annular raceway is a wavy structure formed by a plurality of ramps uniformly distributed along the circumference and connected end to end.

[0005] Furthermore, a first elastic body is provided on the left side of the first outer plate, and two ends of the first elastic body respectively abut the first outer plate and the first clutch drum, a push plate is provided on the left side of the first clutch drum, and the first clutch drum can rotate relative to the push plate, and a thrust device for pushing the push plate and the first clutch drum to move to the right is provided on the left side of the push plate.

[0006] Furthermore, the first outer plate and the second outer plate are respectively slidably connected to the first clutch drum through outer splines, and a first retaining spring for limiting the maximum rightward movement distance of the second outer plate relative to the first clutch drum is arranged on the right side of the second outer plate, and the inner plate is fixedly connected to the clutch hub or slidably connected through inner splines; a baffle is arranged on the right side of the first outer plate, the first outer plate can rotate relative to the baffle, and the baffle is fixedly connected to the second clutch drum.

[0007] Furthermore, it also includes a second clutch; the second clutch includes a second clutch drum located outside the first clutch drum and a third outer plate located on the right side of the first clutch drum, a second elastomer is provided on the right side of the third outer plate, an elastomer baffle is provided on the right side of the second elastomer, two ends of the second elastomer respectively abut the third outer plate and the elastomer baffle, the third outer plate is connected to the second clutch drum through an outer spline, the elastomer baffle is slidingly connected to the second clutch drum through an outer spline, and a clutch structure is provided between the third outer plate and the right end of the first clutch drum to realize power transmission between the two when the second clutch drum moves to the right.

[0008] Furthermore, the clutch structure includes a second rolling body located between the third outer plate and the right end of the first clutch drum, the right end surface of the first clutch drum is evenly distributed along the circumference with limiting grooves that cooperate with the second rolling body, and the left end surface of the third outer plate is provided with a ramp-type annular raceway that cooperates with the second rolling body, and the bottom surface of the ramp-type annular raceway is a wavy structure formed by multiple ramps that are evenly distributed along the circumference and connected end to end; the clutch hub is fixedly connected to the first output shaft or connected in a spline sliding manner, the second outer plate is fixedly connected to the input shaft or connected in a spline sliding manner, and the second clutch drum is fixedly connected to the second output shaft or connected in a spline sliding manner.

[0009] Furthermore, the clutch structure includes at least two first ratchet blocks evenly distributed in the circumferential direction on the right end surface of the first clutch drum, and at least two second ratchet blocks evenly distributed in the circumferential direction are provided on the left side surface of the third outer plate, and the first ratchet blocks and the second ratchet blocks are provided with matching inclined surfaces; a first slot for the second ratchet block to enter is formed between two adjacent first ratchet blocks on the right end surface of the first clutch drum, and a first high blocking surface and a first low blocking surface for clamping the second ratchet block are formed at both ends of the first slot between two adjacent first ratchet blocks, and a second slot for the first ratchet block to enter is formed between two adjacent second ratchet blocks on the left side surface of the third outer plate, and a second high blocking surface and a second low blocking surface for clamping the first ratchet block are formed at both ends of the second slot between two adjacent second ratchet blocks.

[0010] Furthermore, a planetary gear train is provided on the right side of the clutch hub, the second outer plate is slidably connected to the ring gear of the planetary gear train via a spline, the clutch hub is fixedly connected to the sun gear of the planetary gear train or slidably connected via a spline, one of the sun gear and the planetary carrier of the planetary gear train is fixedly connected to the input shaft or slidably connected via a spline, and the other is fixedly connected to the output shaft or slidably connected via a spline.

[0011] Furthermore, an annular raceway of equal height matching with the first rolling element is arranged on the right end surface of the first outer plate in the circumferential direction; the number N1 of the first rolling element and the number N2 of the ramps satisfy the relationship N2=1 / 2 N1*n, wherein N1 is an even number and n is an integer; the depth A1 of the annular raceway of the first outer plate from the plate surface, the maximum diameter D of the first rolling element, the depth A2 of the second outer plate slope peak from the plate surface, the depth A3 of the second outer plate slope valley from the plate surface, the inner plate thickness H, when all the rolling elements are in the middle of the ramp, the total clearance S0 between the inner plate and the first outer plate and the second outer plate, the maximum displacement S to the right from the initial state of the first clutch drum satisfies the following relationship: D> A1+A3+H, A1<1 / 2D, A3<1 / 2D, D-S0>S≥1 / 2(A3-A2).

[0012] Another technical solution of the present invention is: a working method of the linkage interlocking shift actuator as described above,

[0013] (1) In the initial state, the thrust device does not work, the first clutch drum is not subjected to the force from the push plate, the first elastic body pushes the first outer plate to the right, and squeezes the first rolling body to the left through the first clutch drum, the first retaining spring and the second outer plate. The first rolling body cannot rotate relative to the first outer plate and the second outer plate due to the obstruction of the ramp, and the first clutch is in the engaged state. At this time, if the input shaft has power input, the power is transmitted to the first output shaft through the second outer plate, the first rolling body, the inner plate and the clutch hub in sequence;

[0014] (2) The thrust device provides thrust, and the push plate pushes the first clutch to move right. When the first outer plate passes through the second ball to abut the baffle, the first outer plate cannot continue to move right. Thereafter, the thrust device continues to push the first clutch drum to compress the first elastic body through the push plate, and the first clutch drum continues to move right to the designed limit position. Correspondingly, the first clutch drum pushes the third outer plate to squeeze the second elastic body, and the third outer plate moves right to the designed limit position. During this process, the first clutch is first in a sliding state, and the inner plate can rotate with a small displacement relative to the first outer plate and the second outer plate. After that, the first clutch is in a completely separated state, and the inner plate can rotate without constraint relative to the first outer plate and the second outer plate. When the second outer plate rotates, the input shaft will not transmit power to the first output shaft through the first clutch. When the first clutch enters the disengagement state from sliding friction, the second clutch simultaneously enters the engagement state from sliding friction. During the sliding friction process, the first clutch drum squeezes the second elastic body through the second rolling body and the third outer plate, and the third outer plate moves right to the designed limit position. The second rolling body is blocked by the ramp, so that the first clutch drum cannot rotate relative to the third outer plate. The first clutch drum drives the third outer plate to rotate through the second rolling body. Therefore, the power of the input shaft is transmitted to the second output shaft through the second outer plate, the first clutch drum, the second rolling body, the third outer plate and the second clutch drum in sequence.

[0015] (3) The thrust device gradually removes the thrust, and the first clutch drum pushes the push plate to the left under the action of the first elastic body until the first clutch is fully engaged. In this process, as the pressure of the push plate on the first clutch drum gradually decreases, the first clutch is first in a sliding state, and the inner plate can rotate with a small displacement relative to the first outer plate and the second outer plate. Then the first clutch is in an engaged state, and the first rolling body is blocked by the ramp, so that the inner plate cannot rotate relative to the first outer plate and the second outer plate, and the second outer plate drives the inner plate to rotate through the first rolling body. Therefore, the input shaft transmits power to the first output shaft through the second outer plate, the first rolling body, the inner plate, and the clutch hub in sequence. During the sliding engagement process of the first clutch, the second clutch completes the process from the sliding process to the fully separated state, and the second output shaft has no power output.

[0016] Compared with the prior art, the present invention has the following beneficial effects: the interlocking shift actuator of the present invention does not have a friction pair, which greatly reduces the cost of the clutch assembly and does not cause the friction pair to burn; the energy loss is small and the efficiency is high; the amount of wear and heat is reduced, which can reduce failures, extend the service life, reduce actuators and other parts, have a compact structure, a small assembly body, and a wide range of applications.

[0017] In order to make the objectives, technical solutions and advantages of the present invention more clearly understood, the present invention will be further described in detail below through specific embodiments and related drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1is a cross-sectional view of an embodiment of the present invention;

[0019] Figure 2 is a three-dimensional diagram of the first outer panel in the first embodiment of the present invention;

[0020] Figure 3 is a three-dimensional diagram of the inner panel in the first embodiment of the present invention;

[0021] Figure 4 is a three-dimensional diagram of the second outer panel in the first embodiment of the present invention;

[0022] Figure 5 is an expanded view of the first clutch in the disengaged state in the first embodiment of the present invention;

[0023] Figure 6 is an expanded view of the first clutch in the first embodiment of the present invention;

[0024] Figure 7 is a cross-sectional view of a second embodiment of the present invention;

[0025] Figure 8 is a three-dimensional diagram of a first clutch drum in a second embodiment of the present invention;

[0026] Fig. 9 It is a three-dimensional diagram of the third outer panel in the second embodiment of the present invention;

[0027] Explanation of the reference numerals in the figure: 1-first clutch drum, 2-clutch hub, 3-first outer plate, 4-inner plate, 5-second outer plate, 6-first rolling element, 7-ramp-type annular raceway, 8-first elastic body, 9-push plate, 10-first retaining spring, 11-baffle plate, 12-first round ball, 13-second round ball, 14-congruent annular raceway, 15-second clutch drum, 16-third outer plate, 17-second elastic body, 18-elastic body baffle plate, 19- The second rolling body, 20-piston chamber, 21-piston, 22-return spring, 23-first ratchet block, 24-second ratchet block, 25-gear ring, 26-sun gear, 27-planet carrier, 28-input shaft, 29-output shaft, 30-first output shaft, 31-second output shaft, 32-first slot, 33-first high blocking surface, 34-first low blocking surface, 35-second slot, 36-second high blocking surface, 37-second low blocking surface. DETAILED DESCRIPTION

[0028] It should be noted that the following detailed descriptions are exemplary and are intended to provide further explanation of the present application. Unless otherwise specified, all technical and scientific terms used herein have the same meanings as those commonly understood by those skilled in the art to which the present application belongs.

[0029] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, it indicates the presence of features, steps, operations, devices, components and / or combinations thereof.

[0030] Embodiment 1: Figures 1 to 6 As shown, a linkage interlocking shift actuator is suitable for a general dual clutch, including a first clutch, wherein the first clutch includes a first clutch drum 1 and a clutch hub 2 located in the middle of the first clutch drum, and the first clutch is engaged when the first clutch drum 1 moves to the left. A first outer plate 3, an inner plate 4 and a second outer plate 5 are provided on the inner side of the first clutch drum 1 from left to right, wherein the inner plate 4 is connected to the clutch hub 2 and has through holes uniformly distributed in the circumferential direction, wherein first rolling bodies 6 are provided in the through holes, and the first rolling bodies 6 are arranged in one or more groups. When multiple groups of first rolling bodies 6 are arranged, the multiple groups of first rolling bodies 6 are uniformly distributed in the circumferential direction, and each group consists of two or more first rolling bodies 6. When two are in a group, the two first rolling bodies 6 are spaced a certain distance apart in the circumferential direction, and when multiple groups are in a group, the multiple first rolling bodies 6 are spaced at equal distances apart in the circumferential direction. It is preferred that two are in a group and the spacing distance between the two first rolling bodies 6 in a group is equal to the spacing distance between the two adjacent groups. The first rolling body 6 may be spherical, cylindrical or conical. The second outer plate 5 is connected to the first clutch drum 1 and has a ramp-type annular raceway 7 on its left end face that cooperates with the first rolling element. The bottom surface of the ramp-type annular raceway is a wavy structure formed by a plurality of ramps that are evenly distributed along the circumference and connected end to end. The right end face of the first outer plate is a plane, and an annular raceway 14 of equal height that cooperates with the first rolling element may also be provided along the circumferential direction.

[0031] In this embodiment, a first elastic body 8 is provided on the left side of the first outer plate 3. The first elastic body can be a helical compression spring, a wave spring, a butterfly spring, or a rubber block with a certain elasticity, preferably a helical compression spring. In the initial state, the first outer plate and the second outer plate press the first rolling body 6 under the elastic force of the first elastic body, and limit the inner plate from rotating relative to the first outer plate and the second outer plate under the action of the ramp. The two ends of the first elastic body 8 abut against the first outer plate and the first clutch drum respectively. A push plate 9 is provided on the left side of the first clutch drum. The first clutch drum can rotate relative to the push plate. A thrust device for pushing the push plate and the first clutch drum to move rightward is provided on the left side of the push plate 9.

[0032] In this embodiment, the first outer plate 3 and the second outer plate 5 are respectively slidably connected to the first clutch drum through outer splines, and a first retaining spring 10 for limiting the maximum rightward movement distance of the second outer plate relative to the first clutch drum is provided on the right side of the second outer plate, and the inner plate is fixedly connected to the clutch hub or slidably connected through inner splines; a baffle 11 is provided on the right side of the first outer plate, and the first outer plate can rotate relative to the baffle, and the position of the baffle 11 and the position of the inner plate 4 are staggered inside and outside, and the baffle 11 is fixedly connected to the second clutch drum.

[0033] In this embodiment, the left end surface of the first clutch drum has at least two first arc grooves evenly distributed in the circumferential direction, and a first ball 12 is arranged in each first arc groove. The shape and size of the first arc groove correspond to the first ball, and the first ball can roll in the first arc groove. A first annular rolling groove is arranged on the push plate at a position corresponding to the first arc groove. The cross-sectional shape and size of the first annular rolling groove correspond to the first ball. The first ball can rotate with the first clutch drum and can roll along the first annular rolling groove at the same time; the sum of the depth of the first arc groove and the depth of the first annular rolling groove on the push plate is less than the diameter of the first ball, so as to prevent the first clutch drum from rubbing against the push plate.

[0034] In this embodiment, the right side of the first outer plate and the matching part of the baffle plate have at least two second arc grooves evenly distributed in the circumferential direction, and a second ball 13 is arranged in each second arc groove. The shape and size of the second arc groove correspond to the second ball, and the second ball can roll in the second arc groove. A second annular rolling groove is arranged at a position corresponding to the second arc groove on the baffle plate, and the cross-sectional shape and size of the second annular rolling groove correspond to the second ball. The second ball can rotate with the first outer plate and can roll along the first annular rolling groove at the same time. The sum of the depth of the second arc groove and the depth of the second annular rolling groove on the baffle plate is less than the diameter of the second ball, so as to prevent friction between the first outer plate and the baffle plate.

[0035] In this embodiment, a second clutch is also included; the second clutch includes a second clutch drum 15 located on the periphery of the first clutch drum 1 and a third outer plate 16 located on the right side of the first clutch drum, a second elastomer 17 is provided on the right side of the third outer plate 16, an elastomer baffle 18 is provided on the right side of the second elastomer, two ends of the second elastomer are respectively abutted against the third outer plate and the elastomer baffle, the third outer plate is connected to the second clutch drum through an outer spline, the elastomer baffle is slidingly connected to the second clutch drum through an outer spline, and a clutch structure is provided between the third outer plate and the right end of the second clutch drum to realize power transmission between the two when the first clutch drum moves to the right.

[0036] In this embodiment, a second retaining spring for limiting the leftward movement of the third outer plate is arranged on the left side of the third outer plate, and a third retaining spring for limiting the rightward movement of the elastic baffle is arranged on the right side of the elastic baffle.

[0037] In this embodiment, the clutch structure includes a second rolling element 19 located between the third outer plate and the right end of the first clutch drum. The right end face of the first clutch drum is circumferentially and uniformly provided with limiting grooves that cooperate with the second rolling element. The second rolling element can be a spherical body, a conical body, a cylindrical body or other rolling elements. The limiting grooves can be spherical surface grooves, conical grooves, cylindrical body grooves or other rolling element grooves corresponding to the second rolling element. The left end face of the third outer plate is provided with a ramped annular raceway that cooperates with the second rolling element. The bottom surface of the ramped annular raceway is a wavy structure formed by a plurality of ramps that are circumferentially and uniformly distributed and connected end to end. The clutch hub is fixedly connected to the first output shaft or is slidably connected by a spline. The second outer plate is fixedly connected to the input shaft or is slidably connected by a spline. The second clutch drum is fixedly connected to the second output shaft or is slidably connected by a spline. When any two adjacent second rolling elements face the ramp, if one is at the peak of the ramp, the other is at the valley of the ramp.

[0038] When the second rolling element is a spherical ball, the diameter D2 of the second rolling element, the depth B1 of the limiting groove, the depth B2 of the peak of the ramp of the third outer plate, the depth B3 of the valley of the ramp. In the free state, the distance L between the first clutch drum and the third outer plate satisfies the relational expression L < D2 - B3 to prevent the fourth spherical ball from sliding out of the fourth arc groove, B1 + B3 < D2 to prevent friction between the first clutch drum and the third outer plate, and D2 < B1 + B2 + L to ensure that the second clutch drum can be completely separated.

[0039] The maximum thrust Fmax of the push plate on the first clutch drum, the elastic force Nmax of the first elastic body on the first clutch drum. When the first clutch drum rotates relative to the third outer plate or has a relative rotation tendency, the axial acting force T3max on the second rolling element. On the premise of not considering gravity and the friction force of the rolling element on the ramp, Fmax - Nmax > T3max (absolute value comparison).

[0040] In this embodiment, the thrust device includes a piston chamber 20 provided inside the second clutch drum and located on the left side of the push plate. A piston 21 is provided in the piston chamber. The push plate is slidably connected to the second clutch drum through a spline on the outside. A return spring 22 for pushing the push plate to reset is provided on the right side of the push plate. Both ends of the return spring are respectively abutted against the push plate and the second clutch drum.

[0041] In this embodiment, when any two adjacent first rolling elements face the ramp, if one is at the peak of the ramp, the other is at the valley of the ramp. The ramp is symmetric along the circumferential direction on both sides with the axis parallel to the input axis as the center line at the highest point. No matter which direction the input shaft rotates, if one of any two adjacent first rolling elements is on the uphill ramp, the other is on the downhill ramp on the other side. The number of ramps can be equal to or not equal to the number of first rolling elements. The right end face of the first outer plate is provided with an equal-height annular raceway that cooperates with the first rolling elements along the circumferential direction; the number N1 of the first rolling elements and the number N2 of the ramps satisfy the relationship N2 = 1 / 2 N1 * n, where N1 is an even number and n is an integer; the depth A1 of the equal-height annular raceway of the first outer plate from the plate surface, the maximum diameter D of the first rolling element, the depth A2 of the peak of the second outer plate from the plate surface, the depth A3 of the valley of the second outer plate from the plate surface, the inner plate thickness H, and when all the rolling elements are in the middle of the ramp, the total clearance S0 between the inner plate and the first outer plate and the second outer plate. The maximum displacement S of the first clutch drum to the right from the initial state satisfies the following relationship: D > A1 + A3 + H, to prevent the first outer plate and the second outer plate from clamping the inner plate, causing the first rolling elements to be ineffective and generating friction; A1 < 1 / 2D, A3 < 1 / 2D, to reduce the processing difficulty of the second outer plate and the inner plate; D - S0 > S ≥ 1 / 2(A3 - A2), ensuring that after the first clutch drum moves to the right to the end, the first ball will not slide out through the inner plate, and at the same time ensuring that the first clutch can be completely disengaged.

[0042] After the first clutch is installed, assuming that all the rolling elements are in the middle of the ramp slope, the initial force N0 exerted by the elastic body and the push plate on the rolling elements in the rotation direction of the inner plate through the second outer plate. The force Nt exerted by the elastic body and the push plate on the rolling elements in the rotation direction of the inner plate through the first outer plate and the second outer plate during the rolling process of the rolling elements on the ramp is variable. When some rolling elements are at the peak, it is Nmax, and the force exerted by the input shaft on the rolling elements in the rotation direction of the inner plate through the second outer plate is Tt, with a maximum of Tmax. Without considering gravity and friction, N0 > Tmax. When Nt < Tt, the first clutch is in the slip grinding state. When Nt = 0, the first clutch is in the completely disengaged state. When Nt > Tt, the first clutch is in the engaged state. When the inner plate rotates relative to the first outer plate and the second outer plate and Nt = Tt, the first clutch remains in the disengaged state. When the inner plate does not rotate relative to the first outer plate and the second outer plate and Nt = Tt, the first clutch remains in the engaged state.

[0043] For the first clutch and the second clutch, since the ramp is symmetrical and continuous, and when one of any two adjacent rolling elements is at the peak of the slope, the other is at the valley. Therefore, during the clutch engagement or disengagement process, half of the process is downhill and the other half is uphill, ensuring that during the first clutch engagement and disengagement process, half of the first rolling elements push the second outer plate to rotate in the same direction or are pushed by the second outer plate to rotate in the same direction, ensuring that during the second clutch engagement and disengagement process, half of the second rolling elements push the third outer plate to rotate in the same direction or are pushed by the third outer plate to rotate in the same direction, ensuring that the gear shifting process is basically smooth, reducing impact or setbacks, and that the gear shifting can be basically normal and smooth when the input shaft rotates in the opposite direction.

[0044] A working method of the linkage interlocking shift actuator as described above,

[0045] (1) In the initial state, the thrust device does not work. The push plate presses the piston to the leftmost position under the action of the return spring. The first clutch drum is not subjected to the force from the push plate. The first elastic body pushes the first outer plate to the right and squeezes the first rolling body to the left through the first clutch drum, the first retaining spring and the second outer plate. The first rolling body cannot rotate relative to the first outer plate and the second outer plate due to the obstruction of the ramp. The first clutch is in the engaged state. At this time, if the input shaft has power input, the power is transmitted to the first output shaft through the second outer plate, the first rolling body, the inner plate and the clutch hub in sequence. At this time, the first clutch drum can rotate relative to the push plate, the first outer plate and the first outer plate. The baffle plate and the third outer plate rotate, the first clutch drum and the first ball and push plate on its left side form a first thrust bearing, the first outer plate and the second ball and baffle plate on its lower right side form a second thrust bearing, the existence of the first thrust bearing and the second thrust bearing avoids the friction between the first clutch drum and the push plate and the baffle plate, and also reduces the extra friction of the clutch drum during the gear shifting process, the first race on the push plate and the second race on the baffle plate radially block the corresponding balls, in fact, play the role of deep groove ball bearings, avoid eccentric movement during the rotation of the first clutch drum, the second clutch is in a disengaged state, and the second output shaft has no power output;

[0046] (2) The thrust device provides thrust, and the push plate pushes the first clutch to move right. When the first outer plate contacts the baffle through the second ball, the first outer plate cannot continue to move right. After that, the thrust device continues to push the first clutch drum to compress the first elastic body through the push plate, and the first clutch drum continues to move right to the designed limit position. Correspondingly, the first clutch drum pushes the third outer plate to squeeze the second elastic body, and the third outer plate moves right to the designed limit position. In this process, when Nt≠0, the first clutch is first in a sliding state, and the inner plate can rotate with a small displacement relative to the first outer plate and the second outer plate. After that, Nt=0, the first clutch is in a completely separated state, and the inner plate can rotate relative to the first outer plate and the second outer plate without constraint. When the first outer plate and the second outer plate rotate, the input shaft will not transmit power to the first output shaft through the first clutch. When the first clutch enters the disengagement state from sliding friction, the second clutch enters the engagement state from sliding friction at the same time. During the sliding friction process, the first clutch drum squeezes the second elastic body through the second rolling body and the third outer plate, and the third outer plate moves right to the designed limit position. The second rolling body is blocked by the ramp, so that the first clutch drum cannot rotate relative to the third outer plate. The first clutch drum drives the third outer plate to rotate through the second rolling body. Therefore, the power of the input shaft is transmitted to the second output shaft through the second outer plate, the first clutch drum, the second rolling body, the third outer plate and the second clutch drum in sequence.

[0047] (3) The thrust device gradually withdraws the thrust. Under the action of the first elastic body, the first clutch drum pushes the push plate to move left until the first clutch is fully engaged. During this process, as the pressure of the push plate on the first clutch drum gradually decreases, Nt gradually increases. When Nt ≤ Tt, the first clutch is in a slipping state first, and the inner plate can rotate with a relatively small displacement relative to the first outer plate and the second outer plate. Then when Tt < Nt, the first clutch is in an engaged state. Blocked by the ramp, the first rolling body prevents the inner plate from rotating relative to the first outer plate and the second outer plate. The second outer plate drives the inner plate to rotate through the first rolling body. Thus, the input shaft transmits power to the first output shaft successively through the second outer plate, the first rolling body, the inner plate, and the clutch hub. During the slipping engagement process of the first clutch, the second clutch completes the process from slipping to full separation, and there is no power output from the second output shaft. At this time, the first clutch drum can rotate relative to the push plate, the baffle plate, and the third outer plate. The first clutch drum and the first spherical ball on its left side and the push plate form a first thrust bearing. The second spherical ball on the lower right side of the first outer plate and the baffle plate form a second thrust bearing. The existence of the first thrust bearing and the second thrust bearing avoids the friction between the first clutch and the push plate and the baffle plate, and also reduces the friction force on the clutch during the shifting process. The radial blocking of the corresponding spherical balls by the first annular groove on the push plate and the second annular groove on the baffle plate actually plays the role of a deep groove ball bearing, avoiding the eccentric movement during the rotation of the first clutch drum. During the slipping engagement process of the first clutch; and during the leftward movement of the first clutch drum, the acting force of the first clutch drum on the third outer plate through the second rolling body gradually decreases, and the second elastic body is gradually released to the left until the third outer plate is blocked by the second snap ring. The acting force of the ramp of the third outer plate on the first clutch drum blocked by the second rolling body gradually decreases until the distance from the peak of the ramp of the third outer plate to the bottom of the second rolling body is greater than the diameter of the second rolling body. The second clutch completes the process from slipping to full separation, and there is no power output from the second output shaft.

[0048] Compared with the traditional technology, the linkage interlock shifting actuator of the present invention:

[0049] 1. No friction pair is set anymore, greatly reducing the cost of the clutch assembly. Without a friction pair, there will be no phenomenon of friction pair burning.

[0050] 2. It no longer completely relies on friction to transmit power, and the rolling friction coefficient of the rolling body is much lower than that of the friction pair. The energy loss during the shifting process due to slipping is small, and the drag torque during clutch separation is small. Therefore, the energy loss is small and the efficiency is high.

[0051] 3. Without the slipping of the friction pair, the clutch will not bring a large amount of wear debris to the transmission or related mechanical equipment, reduce the heat generation, which is beneficial to optimizing the working environment of the clutch, transmission or related mechanical equipment, can reduce failures and extend the service life.

[0052] 4. The linkage interlocking function reduces the actuator and other parts, uses the ramp blocking effect to reduce the actuator power requirement, and uses the clutch parts as bearing retainers and bearing raceways to further reduce parts, so the assembly is small and the cost is low.

[0053] Embodiment 2: Figures 7-9 As shown, the difference between the second embodiment and the first embodiment lies in the clutch structure in the second clutch and the connection mode with the input shaft and the output shaft, and is suitable for the one-brake-one-clutch shift actuator of the planetary gear transmission; in this embodiment, the clutch structure includes at least two first ratchet blocks 23 uniformly distributed in the circumferential direction on the right end face of the first clutch drum, and at least two second ratchet blocks 24 uniformly distributed in the circumferential direction are provided on the left side face of the third outer plate, and the first ratchet blocks and the second ratchet blocks are provided with matching inclined surfaces; a first slot 32 for the second ratchet block to enter is formed between two adjacent first ratchet blocks on the right end face of the first clutch drum, and a first high blocking surface 33 and a first low blocking surface 34 for clamping the second ratchet block are formed at both ends of the first slot 32 between the two adjacent first ratchet blocks, and a second slot 35 for the first ratchet block to enter is formed between the two adjacent second ratchet blocks on the left side face of the third outer plate, and a second high blocking surface 36 and a second low blocking surface 37 for clamping the first ratchet block are formed at both ends of the second slot.

[0054] In this embodiment, a planetary gear train is provided on the right side of the clutch hub, the second outer plate is connected to the ring gear 25 of the planetary gear train through a spline sliding connection, the clutch hub is fixedly connected to the sun gear 26 of the planetary gear train or connected through a spline sliding connection, one of the sun gear and the planet carrier 27 of the planetary gear train is fixedly connected to the input shaft or connected through a spline sliding connection, and the other is fixedly connected to the output shaft or connected through a spline sliding connection.

[0055] Working process of the linkage interlocking shift actuator of embodiment 2:

[0056] In the initial state, there is no power input to the input shaft, and the push plate pushes the first clutch drum to the limit. Correspondingly, the first clutch drum pushes the third outer plate to squeeze the second elastic body, and the third outer plate is pushed to the right limit position, and the first clutch is disengaged. At this time, if the first ratchet block and the second ratchet block do not enter the second slot and the first slot respectively, when the input shaft rotates, the input shaft will drive the second outer plate through the planetary gear train, thereby driving the first clutch drum to rotate relative to the third outer plate, and will also make the first ratchet block and the second ratchet block enter the second slot and the first slot respectively, and the high blocking surface of the first ratchet block and the high blocking surface of the second ratchet block can abut, and the low blocking surface of the first ratchet block and the low blocking surface of the second ratchet block can abut, and then the first clutch drum is braked by the third outer plate through the housing, and correspondingly, the first clutch drum brakes the ring gear through the second outer plate; according to the movement law of planetary gears, the ring gear is braked, and when the input is reversed, the output is also reversed, and it is in reverse gear at this time, and when the input is forward, the output is also forward, and it is in forward gear at this time.

[0057] During the forward rotation of the input shaft, when the push plate moves left, the first clutch drum moves left under the action of the first elastic body, and the first ratchet block and the second ratchet block are separated from the second slot and the first slot respectively. When the ratchet block is just separated from the slot, the high blocking surfaces of the two ratchet blocks can still partially abut, and the reverse rotation of the ring gear can still be braked, and the low blocking surfaces of the two ratchet blocks are disengaged. Thereafter, the first clutch is gradually engaged. During the first clutch engagement process, it will drive the ring gear to gradually rotate forward from 0 speed, so that the ring gear drives the first clutch drum to rotate forward. When the inclined surface of the first ratchet block slides from low to high along the inclined surface of the second ratchet block, it pushes the third outer plate to squeeze the second elastic body, and the third outer plate moves right. The first clutch drum rotates relative to the third outer plate, and the second clutch is separated during the sliding process. Subsequently, the first clutch is fully engaged, and the ring gear is synchronized with the sun gear, thereby holding the planetary carrier synchronized. The input and output have the same speed, and the clutch is in direct gear state.

[0058] In the direct gear state, the thrust device pushes the push plate to move right, and the first clutch drum is pushed to move right through the push plate. After the first outer plate abuts the baffle plate through the second ball, the first outer plate cannot continue to move right, and the thrust device continues to push the first clutch drum to compress the first elastic body through the push plate. The first clutch drum continues to move right. When the right side of the first clutch drum abuts the third outer plate, the inclined surface of the first ratchet block slides from low to high along the inclined surface of the second ratchet block, pushing the third outer plate to squeeze the second elastic body. The third outer plate moves right, and the first clutch drum continues to rotate relative to the third outer plate. After the first clutch drum moves a certain distance to the right, the first clutch is disengaged, and the force of the planetary gear on the ring gear is opposite to that of the input shaft. The ring gear gradually decreases from the same speed as the input shaft to 0. Thereafter, the ring gear starts to reverse, and the ring gear drives the third outer plate through the second outer plate. A clutch drum reverses. When the first clutch drum reverses, the high blocking surface of the first ratchet block on the first clutch drum abuts against the high blocking surface of the second ratchet block on the third outer plate, and the first clutch drum is braked by the third outer plate through the housing, thereby braking the ring gear through the second outer plate. According to the movement law of planetary gears, power is input from the input shaft and output from the output shaft at this time. When the input shaft is connected to the sun gear, the planetary row is in a deceleration state. When the input shaft is connected to the planetary carrier, the planetary row is in a speed-up state. When the first clutch drum continues to move right to the designed extreme position, the first ratchet block enters the second slot, the second ratchet block enters the first slot, the high blocking surface of the first ratchet block abuts against the high blocking surface of the second ratchet block, and the low blocking surface of the first ratchet block abuts against the low blocking surface of the second ratchet block, so that the ring gear brake is locked.

[0059] Unless otherwise stated, any technical solution disclosed in the present invention disclosed above, if it discloses a numerical range, then the disclosed numerical range is a preferred numerical range, and any technician in the field should understand that the preferred numerical range is only a numerical value with a more obvious technical effect or representative value among many implementable numerical values. Since there are too many numerical values ​​to be exhaustive, the present invention discloses some numerical values ​​to illustrate the technical solution of the present invention, and the numerical values ​​listed above should not constitute a limitation on the scope of protection of the present invention.

[0060] If the present invention discloses or involves components or structures that are fixedly connected to each other, then, unless otherwise stated, the fixed connection can be understood as: a detachable fixed connection (for example, connection using bolts or screws), and can also be understood as: a non-detachable fixed connection (for example, riveting, welding). Of course, the mutual fixed connection can also be replaced by an integrated structure (for example, manufactured by integrated molding using a casting process) (except when it is obviously impossible to use an integrated molding process).

[0061] In addition, unless otherwise stated, the terms used to indicate positional relationships or shapes in any of the technical solutions disclosed in the present invention include states or shapes that are approximate, similar, or close to them.

[0062] Any component provided by the present invention may be assembled from a plurality of separate components, or may be a separate component manufactured by an integral forming process.

[0063] The above is only a preferred embodiment of the present invention, and does not limit the present invention in other forms. Any technician familiar with the profession may use the above disclosed technical content to change or modify it into an equivalent embodiment with equivalent changes. However, any simple modification, equivalent change and modification made to the above embodiment according to the technical essence of the present invention without departing from the technical solution of the present invention still belongs to the protection scope of the technical solution of the present invention.

Claims

1. A linkage interlocking shift actuator, characterized in that: The clutch assembly of claim 1, wherein the first clutch comprises a first clutch drum and a clutch hub located in the middle of the first clutch drum, wherein the first clutch is engaged when the first clutch drum moves to the left, wherein a first outer plate, an inner plate, and a second outer plate are sequentially arranged on the inner side of the first clutch drum from left to right, wherein the inner plate is connected to the clutch hub and has through holes evenly distributed in the circumferential direction, wherein a first rolling body is arranged in the through hole, and the second outer plate is connected to the first clutch drum and a ramp-type annular raceway cooperating with the first rolling body is arranged on the left end face, wherein the bottom surface of the ramp-type annular raceway is a wavy structure formed by a plurality of ramps evenly distributed along the circumference and connected end to end; a first elastic body is arranged on the left side of the first outer plate, and the two ends of the first elastic body respectively abut against the first outer plate and the first clutch drum, a push plate is arranged on the left side of the first clutch drum, and the first clutch drum can rotate relative to the push plate, and a thrust device for pushing the push plate and the first clutch drum to move to the right is arranged on the left side of the push plate; the first outer plate and the second outer plate are respectively slidably connected to the first clutch drum through outer splines, and the right side of the second outer plate A first retaining spring is provided for limiting the maximum distance that the second outer plate moves to the right relative to the first clutch drum, and the inner plate is fixedly connected to the clutch hub or slidably connected via an inner spline; a baffle is provided on the right side of the first outer plate, the first outer plate can rotate relative to the baffle, and the baffle is fixedly connected to the second clutch drum; it also includes a second clutch; the second clutch includes a second clutch drum located at the periphery of the first clutch drum and a third outer plate located on the right side of the first clutch drum, a second elastomer is provided on the right side of the third outer plate, an elastomer baffle is provided on the right side of the second elastomer, two ends of the second elastomer respectively abut against the third outer plate and the elastomer baffle, the third outer plate is slidably connected to the second clutch drum via an outer spline, the elastomer baffle is connected to the second clutch drum via an outer spline, and a clutch structure is provided between the right ends of the third outer plate and the second clutch drum to realize power transmission between the two when the second clutch drum moves to the right; an equi-height annular raceway cooperating with the first rolling body is provided along the circumferential direction on the right end surface of the first outer plate; the number N1 of the first rolling body and the number N2 of the ramps satisfy the relationship N2=1 / 2 N1*n, where N1 is an even number and n is an integer; the depth of the first outer plate equal height annular raceway from the plate surface A1, the maximum diameter of the first rolling element D, the depth of the second outer plate slope peak from the plate surface A2, the depth of the second outer plate slope valley from the plate surface A3, the inner plate thickness H, when all rolling elements are in the middle of the ramp, the total clearance between the inner plate and the first outer plate and the second outer plate S0, the maximum displacement S to the right from the initial state of the first clutch drum satisfies the following relationship: D> A1+ A3+H, A1<1 / 2D, A3<1 / 2D, D-S0>S≥1 / 2(A3-A2).

2. The linkage interlocking shift actuator according to claim 1, characterized in that: The left end surface of the first clutch drum has at least two first arc grooves evenly distributed in the circumferential direction, a first ball is arranged in each first arc groove, and a first annular rolling groove is arranged on the push plate at a position corresponding to the first arc groove; the right side of the first outer plate and the matching part with the baffle plate have at least two second arc grooves evenly distributed in the circumferential direction, a second ball is arranged in each second arc groove, and a second annular rolling groove is arranged on the baffle plate at a position corresponding to the second arc groove.

3. The linkage interlocking shift actuator according to claim 1, characterized in that: The clutch structure includes a second rolling body located between the third outer plate and the right end of the first clutch drum, the right end surface of the first clutch drum is evenly distributed with limiting grooves that cooperate with the second rolling body along the circumference, and the left end surface of the third outer plate is provided with a ramp-type annular raceway that cooperates with the second rolling body. The bottom surface of the ramp-type annular raceway is a wavy structure formed by multiple ramps that are evenly distributed along the circumference and connected end to end; the clutch hub is fixedly connected to the first output shaft or connected in a spline sliding manner, the second outer plate is fixedly connected to the input shaft or connected in a spline sliding manner, and the second clutch drum is fixedly connected to the second output shaft or connected in a spline sliding manner.

4. The linkage interlocking shift actuator according to claim 1, characterized in that: The clutch structure includes at least two first ratchet blocks evenly distributed in the circumferential direction on the right end surface of the first clutch drum, and at least two second ratchet blocks evenly distributed in the circumferential direction are provided on the left side surface of the third outer plate, and the first ratchet blocks and the second ratchet blocks are provided with matching inclined surfaces; a first slot for the second ratchet block to enter is formed between two adjacent first ratchet blocks on the right end surface of the first clutch drum, and a first high blocking surface and a first low blocking surface for clamping the second ratchet block are formed at both ends of the first slot between two adjacent first ratchet blocks, and a second slot for the first ratchet block to enter is formed between two adjacent second ratchet blocks on the left side surface of the third outer plate, and a second high blocking surface and a second low blocking surface for clamping the first ratchet block are formed at both ends of the second slot between two adjacent second ratchet blocks.

5. The linkage interlocking shift actuator according to claim 4, characterized in that: A planetary gear train is provided on the right side of the clutch hub, the second outer plate is slidably connected to the ring gear of the planetary gear train through a spline, the clutch hub is fixedly connected to the sun gear of the planetary gear train or slidably connected through a spline, one of the sun gear and the planet carrier of the planetary gear train is fixedly connected to the input shaft or slidably connected through a spline, and the other is fixedly connected to the output shaft or slidably connected through a spline.

6. A working method of the linkage interlocking shift actuator as claimed in claim 1, characterized in that: In the initial state, the thrust device does not work, the first clutch drum is not subjected to the force from the push plate, the first elastic body pushes the first outer plate to the right, and squeezes the first rolling body to the left through the first clutch drum, the first retaining spring and the second outer plate. The first rolling body cannot rotate relative to the first outer plate and the second outer plate under the obstruction of the ramp, and the first clutch is in a engaged state. At this time, if the input shaft has power input, the power is transmitted to the first output shaft through the second outer plate, the first rolling body, the inner plate and the clutch hub in sequence; The thrust device provides thrust, and the push plate pushes the first clutch to move right. When the first outer plate abuts the baffle through the second ball, the first outer plate cannot continue to move right. Thereafter, the thrust device continues to push the first clutch drum to compress the first elastic body through the push plate, and the first clutch drum continues to move right to the designed limit position. Correspondingly, the first clutch drum pushes the third outer plate to squeeze the second elastic body, and the third outer plate moves right to the designed limit position. During this process, the first clutch is first in a sliding state, and the inner plate can rotate with a small displacement relative to the first outer plate and the second outer plate. After that, the first clutch is in a completely separated state, and the inner plate can rotate relative to the first outer plate and the second outer plate without constraint. When the outer plate rotates, the input shaft will not transmit power to the first output shaft through the first clutch. When the first clutch enters the disengagement state from sliding friction, the second clutch simultaneously enters the engagement state from sliding friction. During the sliding friction process, the first clutch drum squeezes the second elastic body through the second rolling body and the third outer plate, and the third outer plate moves right to the designed limit position. The second rolling body is blocked by the ramp, so that the first clutch drum cannot rotate relative to the third outer plate. The first clutch drum drives the third outer plate to rotate through the second rolling body. Therefore, the power of the input shaft is transmitted to the second output shaft through the second outer plate, the first clutch drum, the second rolling body, the third outer plate and the second clutch drum in sequence. The thrust device gradually removes the thrust, and the first clutch drum pushes the push plate to the left under the action of the first elastic body until the first clutch is fully engaged. In this process, as the pressure of the push plate on the first clutch drum gradually decreases, the first clutch is first in a sliding state, and the inner plate can rotate with a small displacement relative to the first outer plate and the second outer plate. Then the first clutch is in an engaged state, and the first rolling body is blocked by the ramp, so that the inner plate cannot rotate relative to the first outer plate and the second outer plate, and the second outer plate drives the inner plate to rotate through the first rolling body. Therefore, the input shaft transmits power to the first output shaft through the second outer plate, the first rolling body, the inner plate, and the clutch hub in sequence. During the sliding engagement process of the first clutch, the second clutch completes the process from the sliding process to the fully separated state, and the second output shaft has no power output.

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