Torque damping device

Abstract

The present disclosure relates to a torque damping device comprising: a torque limiter; the torsional vibration damper comprises a single flange plate and a friction control plate, the friction control plate is located on one axial side of the single flange plate in the axial direction and abuts against the torque limiter in a friction mode, an axial plate is arranged on the other axial side of the friction control plate, and the single flange plate is provided with a containing groove extending in the circumferential direction. The axial plate is inserted into the containing groove, when torque is transmitted in the reverse direction, the axial plate abuts against the abutting wall of the containing groove, the single flange plate drives the friction control plate to rotate so as to increase damping between the single flange plate and the first cover plate, and when torque is transmitted in the forward direction, the axial plate abuts against the abutting wall of the containing groove. The axial plate is separated from the abutting wall of the containing groove, and the single flange plate rotates relative to the friction control plate. Through the structural design of the axial plate and the containing groove of the friction control plate, damping between the single flange plate and the first cover plate can be increased when torque is transmitted reversely.

Description

Technical Field

[0001] The invention relates to the technical field of vehicle shock absorption, and in particular to a torque vibration reduction device. Background Art

[0002] The torque damping device usually includes a damper, which can be divided into a double flange damper and a single flange damper. However, the disadvantages of the double flange damper design in the related art are that it has many components and high cost. The gap between the wheel hub and the flange causes NVH problems, and it is easy to make rattles and generate noise problems during traction start working. The disadvantages of the existing single flange damper design are that the radial dimension of the Friction Control Panel (FCP) structure is large and the cost is high. In addition, the axial dimension of the damper is also large, the rotation angle is small, and the application range is narrow. Summary of the invention

[0003] In order to overcome the problems existing in the related art, the present disclosure provides a torque vibration reduction device.

[0004] According to a first aspect of an embodiment of the present disclosure, the present disclosure provides a torque damping device, comprising: a torque limiter; a torsional vibration damper, comprising a single flange and a friction control plate, wherein the friction control plate is axially located on one axial side of the single flange and frictionally abuts against the torque limiter, wherein an axial plate is provided on the other axial side of the friction control plate, the single flange is provided with a circumferentially extending accommodating groove, the axial plate is inserted into the accommodating groove, when the torque is transmitted in the reverse direction, the axial plate abuts against the abutting wall of the accommodating groove, the single flange drives the friction control plate to rotate to increase the damping between the single flange and the first cover plate, and when the torque is transmitted in the forward direction, the axial plate is separated from the abutting wall of the accommodating groove, and the single flange rotates relative to the friction control plate.

[0005] In some embodiments, the torque limiter includes a retaining plate, two friction plates, a pressure plate, a first diaphragm spring, a first cover plate and a second cover plate, the radial inner side of the retaining plate is clamped between the two friction plates, the two friction plates are clamped between the first cover plate and the pressure plate, and the first diaphragm spring is axially abutted between the pressure plate and the second cover plate, wherein a plurality of stop grooves are circumferentially arranged on the radial outer side of the single flange, a plurality of stop plates are circumferentially arranged on the radial inner side of the pressure plate, the stop plates are located in the stop grooves, and the stop plates are circumferentially abutted against the stop grooves to limit the circumferential rotation angle of the single flange.

[0006] In some embodiments, the stop plate is radially located radially inward of the retaining plate and at least partially overlaps with the retaining plate in the axial direction, so as to limit the radial movement of the retaining plate toward the single flange.

[0007] In some embodiments, the stop plate and the pressure plate are fixedly connected via fasteners.

[0008] In some embodiments, the torsional vibration damper further includes a coil spring, the single flange has a first window for accommodating the coil spring, and the radially inner inner wall of the first window is recessed radially inward to form the accommodating groove.

[0009] In some embodiments, the friction control plate further includes a reset protrusion, the reset protrusion radially protrudes from the friction control plate, and the reset protrusion circumferentially abuts against one end of the coil spring close to the abutment wall of the accommodating groove.

[0010] In some embodiments, the torsional vibration damper further includes a first friction pad, which is axially frictionally abutted between the friction control plate and the single flange, and is used to increase the damping between the single flange and the friction control plate when transmitting torque in a positive direction.

[0011] In some embodiments, the axial plate is formed by axially bending the radial outer end of the friction control plate.

[0012] In some embodiments, the torsional vibration damper also includes: a second friction gasket, which is frictionally abutted against the other axial side of the single flange, the second friction gasket portion protrudes toward the second cover plate to form a hollow protrusion, and a second diaphragm spring, the second diaphragm spring elastically abuts between the protrusion and the second cover plate.

[0013] In some embodiments, spring covers are provided at both circumferential ends of the coil spring, and the spring covers include: a plug-in portion, which is inserted into the inner ring of the coil spring; and a cap, which is located outside the coil spring and has a diameter greater than the outer ring diameter of the coil spring, and the cap is non-fixedly abutted against the first window of the single flange at one side away from the plug-in portion. The spring cover abuts against the first window of the single flange and isolates the coil spring from the first window in the radial direction and the circumferential direction.

[0014] In some embodiments, the plug-in portion is provided with a crushing rib, and the plug-in portion is interference-fitted with the inner ring of the coil spring via the crushing rib.

[0015] In some embodiments, the spring cover is made of plastic material, and the friction coefficient between the spring cover and the first window is smaller than the friction coefficient between the coil spring and the first window.

[0016] The technical solution provided by the embodiment of the present disclosure may include the following beneficial effects: when transmitting torque in the reverse direction, the single flange can drive the friction control plate to rotate relative to the first cover plate through the axial plate of the friction control plate and the receiving groove of the single flange, so that the damping of the single flange can be increased to reduce the torque vibration caused by the torque impact, so that the meshing of the inner gear of the single flange and the outer gear of the wheel hub is smoother and the noise is reduced. When transmitting torque in the forward direction, the single flange cannot drive the friction control plate to rotate together, and the damping of the single flange cannot be increased. Therefore, the friction control plate increases the damping of the single flange in one direction, which can improve the NVH performance of the entire torque vibration reduction device. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present disclosure and, together with the description, serve to explain the principles of the present disclosure.

[0018] Figure 1 is a cross-sectional view of a torque damping device according to an exemplary embodiment;

[0019] Figure 2 yes Figure 1 The enlarged structural diagram at A in the middle;

[0020] Figure 3 It is a schematic diagram of the cooperation between the stop plate and the stop groove of the single flange;

[0021] Figure 4 yes Figure 1 A schematic diagram of the enlarged structure at B in the middle;

[0022] Figure 5 yes Figure 4 Schematic diagram of the three-dimensional structure;

[0023] Figure 6 It is a three-dimensional schematic diagram of the combination of a coil spring and a spring cover;

[0024] Figure 7 is a schematic diagram of the cooperation between the first window for accommodating the coil spring and the axial plate of the friction control plate;

[0025] Figure 8 It is a schematic diagram of the cooperation between the receiving groove of the first window and the axial plate of the friction control plate when the single flange plate transmits torque in the forward direction;

[0026] Fig. 9 It is a schematic diagram of the cooperation between the reset protrusion of the friction control plate and the coil spring. DETAILED DESCRIPTION

[0027] Exemplary embodiments will be described in detail herein, examples of which are shown in the accompanying drawings. When the following description refers to the drawings, the same numbers in different drawings represent the same or similar elements unless otherwise indicated. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the present disclosure. Instead, they are merely examples of devices and methods consistent with some aspects of the present disclosure as detailed in the appended claims.

[0028] In the present invention, unless otherwise specified, the axial direction A, radial direction R and circumferential direction W refer to the axial direction A, radial direction R and circumferential direction W of the dual mass flywheel respectively; the axial side refers to Figure 1 The left side of the axis refers to Figure 1 The right side of the radial direction (or radial outer end) refers to the radial direction R away from Figure 1 The side of the central axis O in ( Figure 1 The radial inner side (or radial inner end) refers to the side close to the central axis O in the radial direction R ( Figure 1 ).

[0029] In addition, "torsion transmission connection" refers to the ability to transmit driving force / torque between two components, and the two components can be directly connected or through various transmission mechanisms or connection structures to achieve the above functions. The term "torsion-resistant connection" refers to the connection between two elements in a manner that does not rotate relative to each other, which can be achieved through a press fit (i.e., interference fit) or by forming the two mentioned components into one piece. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to the specific circumstances.

[0030] The present invention provides a torque damping device 100, which is a device arranged between an engine and a transmission, and is used to transmit torque between the engine (not shown) and the transmission (not shown) and reduce torsional vibration or torsional impact when transmitting torque.

[0031] The torque damping device 100 may include a torque limiter 10 and a torsional vibration damper 20. The torque limiter 10 may be used to transmit a torque not exceeding a predetermined torque between the engine and the transmission to avoid excessive torque being transmitted between the engine and the transmission, thereby preventing damage to the engine or the transmission. The torsional vibration damper 20 may reduce torsional vibration or torsional shock when the torque is transmitted between the engine and the transmission. Therefore, the torque limiter 10 and the torsional vibration damper 20 enable the torque damping device 100 to have both a torque limiting function and a torque damping function.

[0032] In this embodiment, the torque limiter 10 is located radially outside the torsional vibration damper 20. Figure 1As shown, the torque limiter 10 includes a retaining plate 11, two friction plates 12, a pressure plate 13, a first diaphragm spring 14, a first cover plate 15 and a second cover plate 16. The radial inner side of the retaining plate 11 is clamped between the two friction plates 12, the two friction plates 12 are clamped between the first cover plate 15 and the pressure plate 13, and the first diaphragm spring 14 abuts between the pressure plate 13 and the second cover plate 16 in the axial direction A.

[0033] The engine rotates and transmits torque to the retaining plate 11, and the retaining plate 11 generates relative rotation or rotation tendency in the circumferential direction W. Due to the axial compression of the first diaphragm spring 14, friction force is generated on the contact surface between the radial inner side of the retaining plate 11 and the two friction plates 12, and friction force is also generated on the contact surface between the two friction plates 12 and the first cover plate 15 and the pressure plate 13 respectively.

[0034] After receiving the torque transmitted by the engine, the radial outer side of the retaining plate 11 transmits the torque to the two friction plates 12 through friction force. The two friction plates 12 transmit the torque to the first cover plate 15 through friction force. The first cover plate 15 and the second cover plate 16 are connected to transmit torque through a plurality of fixing bolts arranged along the circumferential direction W in a torsion-resistant connection.

[0035] If the torque received by the radial outer side of the retaining plate 11 exceeds the maximum torque between the two friction plates 12 and the retaining plate 11, slippage will occur at the contact surface between the two friction plates 12 and the retaining plate 11, and the torque cannot be transmitted to the torsional vibration damper 20 (i.e., the damper). The above-mentioned maximum torque is the maximum torque provided by the maximum friction force of the first diaphragm spring 14 axially pressing between the two friction plates 12 and the retaining plate 11. The maximum torque can be adjusted by adjusting the pressing force of the first diaphragm spring 14 and / or the friction coefficient of the two friction plates 12 and / or the retaining plate 11.

[0036] Therefore, the torque limiter 10 transmits a preset range of torque to the retaining plate 11, and excessive torque cannot be transmitted to the damper due to slippage between the two friction plates 12 and the retaining plate 11, so as to protect the engine or the transmission from damage.

[0037] Furthermore, the torsional vibration damper 20 includes a single flange 21, a coil spring 22 and a hub 23, the single flange 21 has a first window 211 for accommodating the coil spring 22, and the first cover plate 15 and the second cover plate 16 are provided with a second window 151 for accommodating the coil spring 22 at the corresponding position of the coil spring 22.

[0038] When the engine transmits torque to the transmission in the positive direction, the first cover plate 15 and the second cover plate 16 rotate after receiving the torque, and compress the coil spring 22 through the inner wall of the second window 151. The coil spring 22 is compressed and drives the single flange 21 to rotate through the first window 211 of the single flange 21. The single flange 21 is torsionally connected to the wheel hub 23. The single flange 21 then transmits the torque to the wheel hub 23 and the input shaft of the transmission, thereby finally realizing the torque transmission from the engine to the transmission.

[0039] When the transmission transmits torque to the engine in reverse, the input shaft of the transmission drives the wheel hub 23 to rotate, and the wheel hub 23 drives the single flange 21 to rotate. The single flange 21 compresses the coil spring 22 through the inner wall of the first window 211. The coil spring 22 is compressed and drives the first cover plate 15 and the second cover plate 16 to rotate through the second window 151. The first cover plate 15 and the second cover plate 16 transmit the torque to the retaining plate 11 through friction force, thereby finally realizing the torque transmission from the transmission to the engine.

[0040] In this embodiment, the single flange 21 is located between the first cover plate 15 and the second cover plate 16 in the axial direction A, and the single flange 21 is not only located on the radial inner side of the retaining plate 11, but also Figure 1 It can be seen that the single flange 21 is also located radially inside the fixing bolts 17 that fix the first cover plate 15 and the second cover plate 16. Therefore, the first cover plate 15 and the second cover plate 16 can be recessed inward along the axial direction A at the installation position of the fixing bolts 17, thereby reducing the occupied size of the axial direction A and having a wider range of applications.

[0041] Furthermore, it can be seen from the above content that when transmitting torque in the forward direction or the reverse direction, the torque is transmitted between the single flange 21 and the first cover plate 15 and the second cover plate 16 by compressing the coil spring 22. Therefore, the single flange 21 and the first cover plate 15 and the second cover plate 16 do not rotate synchronously. In order to avoid excessive compression of the coil spring 22, it is necessary to limit the relative rotation angle between the single flange 21 and the first cover plate 15 and the second cover plate 16.

[0042] like Figure 2 and Figure 3 As shown, a plurality of stop grooves 212 are provided on the radial outer side of the single flange 21 along the circumferential direction W. Correspondingly, a plurality of stop plates 131 are provided on the radial inner side of the pressure plate 13 along the circumferential direction W. The stop plates 131 are located in the stop grooves 212. The circumferential width W of the stop grooves 212 is greater than the circumferential width of the stop plates 131. The stop plates 131 overlap with the stop grooves 212 radially and at least partially overlap with the axial direction, so that the stop plates 131 can abut against the stop grooves 212 along the circumferential direction, so as to limit the circumferential rotation angle of the single flange 21.

[0043] In the related art, the circumferential rotation W of the single flange 21 is often limited by the fixing bolts 17 between the first cover plate 15 and the second cover plate 16. Since the first cover plate 15 and the second cover plate 16 need to clamp the friction plate 12 and the retaining plate 11, the fixing bolts 17 are often arranged at a position closer to the radial outside of the first cover plate 15 and the second cover plate 16. If the rotation angle of the single flange 21 is limited by the fixing bolts 17, not only the radial dimension of the single flange 21 is increased, but also the axial dimension of the entire torque damping device 100 is increased.

[0044] In other related technologies, a stop pin may be separately provided to limit the circumferential rotation W of the single flange 21. However, the stop pin extending in the axial direction A also increases the axial dimension A of the entire torque damping device 100 and the number of parts.

[0045] The stop plate 131 of the present disclosure is fixedly connected to the radial inner side of the pressure plate 13, for example, it can be fixedly connected together by fasteners such as bolts and pins. The stop plate 131 can extend radially inward and abut against the stop groove 212 on the radial outer side of the single flange 21 with a smaller radial dimension, without the need for the single flange 21 to extend radially outward, so that the material cost of the overall torque vibration damping device 100 is low, while reducing the radial dimension of the single flange 21, and without the need to set additional stop pins, thereby reducing the axial dimension of the overall torque vibration damping device 100.

[0046] In addition, the single flange 21 and the retaining plate 11 also at least partially overlap in the axial direction A, so that the axial dimension of the torque damping device 100 can be further reduced. The reduction of the axial dimension can increase the application range of the torque damping device 100.

[0047] In some embodiments, the retaining plate 11 and the friction control plate 24 can be stamped on a plate material using a stamping process using one mold, thereby saving material costs and reducing process costs.

[0048] In some embodiments, the stop plate 131 is radially located radially inside the retaining plate 11 and at least overlaps with the retaining plate 11 in the axial direction, so as to limit the radial R movement of the retaining plate 11 toward the single flange 21 .

[0049] It can be seen from the above content that when the torque received by the radial outer side of the retaining plate 11 exceeds the maximum torque between the two friction plates 12 and the radial inner side of the retaining plate 11, slippage will occur at the contact surface of the two friction plates 12 and the retaining plate 11, and the torque cannot be transmitted to the torsional vibration damper 20 (i.e., the damper). The slipping retaining plate 11 is easy to move in the radial direction R, and the stop plate 131 is located on the radial inner side of the retaining plate 11 and overlaps with the radial inner side in the axial direction A, so that the retaining plate 11 can be limited to move radially R in the direction of the single flange 21 when slipping with the friction plate 12, thereby limiting the radial R position of the retaining plate 11 and avoiding mutual damage between the retaining plate 11 and the single flange 21 due to radial R collision.

[0050] In some embodiments, Figure 4 and Figure 5 As shown, the torsional vibration damper 20 further includes a friction control plate 24 , which is axially located between the first cover plate 15 and the single flange 21 , and one axial side of the friction control plate 24 is in friction contact with the first cover plate 15 .

[0051] In some embodiments, the torsional vibration damper 20 also includes a second friction gasket 25 and a second diaphragm spring 26, both of which are located on the other axial side of the single flange 21, wherein the second friction gasket 25 is frictionally abutted against the other axial side of the single flange 21, and the second friction gasket 25 protrudes toward the second cover plate 16 to form a hollow protrusion 251, and the second diaphragm spring 26 is axially A and elastically abutted between the protrusion 251 and the second cover plate 16, and due to the axial A compression effect of the second diaphragm spring 26, damping is generated on the contact surface between the axial side of the radial outer end of the friction control plate 24 and the first cover plate 15.

[0052] Furthermore, an axial plate 241 is provided on the other axial side of the friction control plate 24 , and the single flange 21 is provided with a receiving groove 213 extending in the circumferential direction W, and the axial plate 241 can be inserted into the receiving groove 213 of the single flange 21 .

[0053] Furthermore, the friction control plate 24 further includes a reset protrusion 242, such as Fig. 9 As shown, the reset protrusion 242 protrudes from the friction control plate 24 in the radial direction R, and the reset protrusion 242 abuts against one end of the coil spring 22 in the circumferential direction W. The reset protrusion 242 abuts against the end of the coil spring 22 in the circumferential direction W. The coil spring 22 circumferentially supports the reset protrusion 242, so that when the torque damping device 100 does not need to transmit torque, the axial plate 214 always abuts against the inner wall of one circumferential end of the accommodating groove 213, and the inner wall can be defined as an abutting wall 2131. The end of the reset protrusion 242 abutting against the coil spring 22 in the circumferential direction is the end of the abutting wall 2131 close to the accommodating groove 213.

[0054] When the transmission transmits torque to the engine, that is, when the torque damper transmits torque in the reverse direction, based on Figure 7 As shown, as the single flange 21 rotates counterclockwise, due to the friction between the axial plate 241 of the friction control plate 24 and the abutting wall of the receiving groove 213 (such as Figure 7 The single flange 21 is in contact with the inner wall of the wheel hub 23 (shown on the right side), so that the single flange 21 can drive the friction control plate 24 to rotate, thereby increasing the friction between the friction control plate 24 and the first cover plate 15, and further increasing the damping of the single flange 21 when transmitting torque in the reverse direction. Therefore, when transmitting torque in the reverse direction, the outer gear of the wheel hub 23 and the inner gear of the single flange 21 generate torsional impact, and the increase in damping of the single flange 21 can reduce the torque vibration caused by the torque impact, making the meshing of the inner gear of the single flange 21 and the outer gear of the wheel hub 23 smoother and reducing noise, so that the NVH (Noise, Vibration, Harshness) performance of the entire torque damping device 100 can be improved.

[0055] When the engine transmits torque to the transmission in the positive direction, Figure 8 As shown, the single flange 21 rotates clockwise. Since the circumferential width of the accommodating groove 213 is greater than the circumferential width of the axial plate 241, the axial plate 241 and the abutting wall 2131 of the accommodating groove 213 can be separated. The single flange 21 cannot drive the friction control plate 24 to rotate together through the axial plate 241, but rotates relative to the friction control plate 24. Since there is a gap between the other axial side of the friction control plate 24 and the single flange 21, there is no friction surface. Therefore, when the torque is transmitted in the positive direction, the damping of the single flange 21 is not increased.

[0056] It can be seen from this that the provision of the friction control plate 24 increases the damping of the torque vibration reduction device 100 in one direction.

[0057] It should be noted that when the transmission transmits torque to the engine in the reverse direction, that is, the single flange 21 is based on Figure 7 When the friction control plate 24 rotates counterclockwise, the axial plate 241 of the friction control plate 24 circumferentially abuts against the abutting wall 2131 of the receiving groove 213, so that the single flange 21 can drive the friction control plate 24 to rotate counterclockwise at the same time. Figure 7 The right inner wall shown in FIG. 1 ) and the reset protrusion 242 of the friction control plate 24 simultaneously compress the coil spring 22 in the counterclockwise direction (the coil spring 22 is in the Figure 7 When the reverse torque transmission ends, the coil spring 22 releases the compression force and pushes the single flange 21 in the reverse direction (i.e., clockwise) as shown in FIG. Figure 7The right inner wall and the reset protrusion 242 of the friction control plate 24 are shown, so that the single flange 21 and the friction control plate 24 are reset at the same time, and the axial plate 241 of the friction control plate 24 is always in contact with the abutment wall 2131 of the accommodating groove 213.

[0058] When the engine transmits torque to the transmission in the positive direction, that is, the single flange 21 is based on Figure 8 When the axial plate 241 rotates clockwise as shown, the axial plate 241 is circumferentially separated from the abutting wall 2131 of the receiving groove 213. At this time, the coil spring 22 is compressed in the overlapping part of the first window 211 and the second window 151. When the forward transmission torque ends, the coil spring 22 releases the compression force and moves circumferentially based on Figure 8 The single flange 21 is pushed by rotating counterclockwise as shown, and after the single flange 21 is reset, the abutting wall 2131 of the receiving groove 213 abuts against the axial plate 241 of the friction control plate 24. Further, the axial plate 241 may be a plate-shaped structure integrally formed with the friction control plate 24, and the axial plate 241 is integrally formed with the friction control plate 24 through mechanical processes such as bending or casting. Preferably, in some embodiments, the axial plate 241 is formed by bending the radial outer end of the friction control plate 24 in the axial direction A, which not only simplifies the process, but also reduces the radial R dimension of the friction control plate 24.

[0059] In some other embodiments, the axial plate 241 may also be a columnar structure formed separately from the friction control plate 24, such as a pin, etc., which is not specifically limited here.

[0060] At the same time, the axial plate 241 is inserted into the receiving groove 213 of the single flange 21 in the axial direction A, thereby reducing the axial dimension of the torque vibration reduction device 100 and increasing the applicable scope of the torque vibration reduction device 100 .

[0061] Furthermore, the reset protrusion 242, the axial plate 241 and the friction control plate 24 are integrally formed. Fig. 9 As shown, in this embodiment, the single flange 21 has four coil springs 22 in the circumferential direction. Accordingly, the friction control plate 24 is substantially in a square structure, and the reset protrusions 242 are respectively located at the four corners of the friction control plate 24 .

[0062] When the square friction control plate 24 is in frictional contact with the first cover plate 15, the radial dimension can be reduced while increasing the friction area between the friction control plate 24 and the first cover plate 15, thereby increasing the damping between the single flange 21 and the first cover plate 15 when increasing the reverse transmission torque.

[0063] Furthermore, the receiving groove 213 may be a circumferential groove formed separately on the single flange 21. In some embodiments, for example Figure 7As shown, the receiving groove 213 can also be located in the first window 211, that is, the inner wall of the radial inner side of the first window 211 of the single flange 21 is recessed toward the radial inner side to form the receiving groove 213. In this way, the first window 211 can be fully utilized, and the receiving groove 213 and the first window 211 are integrally formed, the process is simple, and there is no need to separately set the receiving groove 213 at other positions of the single flange 21, thereby increasing the strength of the single flange 21.

[0064] In some embodiments, the torsional vibration damper 20 further includes a first friction pad 27, which is axially frictionally abutted between the friction control plate 24 and the single flange 21. When transmitting torque in the forward direction, the first friction pad 27 is used to increase the damping between the single flange 21 and the friction control plate 24.

[0065] Specifically, when the torque is transmitted in the reverse direction, the single flange 21 can drive the friction control plate 24 to rotate together through the receiving groove 213 and the axial plate 241. At this time, the first friction pad 27 between the single flange 21 and the friction control plate 24 and the single flange 21 and the friction control plate 24 are in relative rotation. When the torque is transmitted in the forward direction, the single flange 21 rotates relative to the friction control plate 24, and the first friction pad 27 increases the damping of the single flange 21 when transmitting the torque in the reverse direction.

[0066] Furthermore, the second friction washer 25 and the second diaphragm spring 26 mentioned above can always increase the damping of the single flange 21 when transmitting torque in the forward direction or the reverse direction.

[0067] Depend on Figure 4 and Figure 5 As shown, the second friction pad 25 protrudes toward the second cover plate 16 to form a hollow protrusion 251. This structure of the second friction pad 25 increases the axial thickness A of the second friction pad 25, has higher structural strength, and uses less material.

[0068] Furthermore, the first friction pad 27 and the second friction pad 25 are both made of plastic material, and the first diaphragm spring 14 and the second diaphragm spring 26 are both made of metal material. The damping between the single flange 21 and the second cover plate 16 can be adjusted by changing the friction coefficient between the first friction pad 27 and the single flange 21 or the pressing force of the second diaphragm spring 26.

[0069] In some embodiments, Figure 6As shown, spring covers 28 are provided at both ends of the coil spring 22 in the circumferential direction. The spring cover 28 includes a plug-in portion 281 and a cap 282. The cap 282 and the plug-in portion 281 can be integrally formed. The plug-in portion 281 is inserted into the inner ring of the coil spring 22; the cap 282 is located outside the coil spring 22, and its diameter is larger than the outer ring diameter of the coil spring 22. The side of the cap 282 away from the plug-in portion 281 abuts against the first window 211 of the single flange 21.

[0070] The spring cover 28 is connected to the coil spring 22 via the plug-in portion 281, and the spring cover 28 abuts against the first window 211 of the single flange 21 via the cap 282, and isolates the coil spring 22 from the first window 211 in the radial direction R and the circumferential direction W. Further, in some embodiments, the spring cover 28 is made of plastic material, and the friction coefficient between the spring cover 28 and the first window 211 is smaller than the friction coefficient between the coil spring 22 and the first window 211.

[0071] It can be seen that when transmitting torque in the forward direction and in the reverse direction, the coil spring 22 has no direct connection with the first window 211 of the single flange 21, thereby avoiding direct wear between the coil spring 22 and the single flange 21, extending the life of the single flange 21, and when the spring cover 28 is damaged, the spring cover 28 can be replaced, and the cost of replacement and maintenance is low. In addition, the spring cover 28 is not fixedly connected to the first window 211 of the single flange 21, which facilitates the replacement of the spring cover 28. In addition, adding the spring cover 28 can also reduce the dynamic hysteresis of the coil spring 22.

[0072] In addition, by Fig. 9 It can be known that the reset protrusion 242 of the friction control plate 24 abuts against the spring cover 28 of the coil spring 22. The direct contact and abutment between the coil spring 22 and the friction control plate 24 is avoided, the friction is reduced, and the service life is extended.

[0073] In some embodiments, the plug-in portion 281 is provided with a compression rib 283, which can not only increase the strength of the plug-in portion 281, but also enable the plug-in portion 281 to have an interference fit with the inner ring of the coil spring 22 through the compression rib 283. The interference fit with the coil spring 22 can be achieved only through the plug-in portion 281, without increasing the diameter of the entire plug-in portion 281, reducing the material and weight of the spring cover 28, and reducing costs.

[0074] It is understood that in the present disclosure, "plurality" refers to two or more than two, and other quantifiers are similar thereto. It is further understood that the terms "first", "second", etc. are used to describe various structures, but these structures should not be limited to these terms. These terms are only used to distinguish structures of the same type from each other and do not indicate a specific order or degree of importance. In fact, expressions such as "first", "second", etc. can be used interchangeably. For example, without departing from the scope of the present disclosure, the first structure may also be referred to as the second structure, and similarly, the second structure may also be referred to as the first structure.

[0075] It will be further understood that the terms “center”, “longitudinal”, “lateral”, “front”, “back”, “up”, “down”, “left”, “right”, “vertical”, “horizontal”, “top”, “bottom”, “inside”, “outside”, etc., indicating orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, are only for the convenience of describing the present embodiment and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation.

[0076] Those skilled in the art will readily appreciate other embodiments of the present disclosure after considering the specification and practicing the invention disclosed herein. This application is intended to cover any modification, use or adaptation of the present disclosure, which follows the general principles of the present disclosure and includes common knowledge or customary techniques in the art that are not disclosed in the present disclosure. The specification and examples are intended to be exemplary only, and the true scope and spirit of the present disclosure are indicated by the following scope of rights.

[0077] It should be understood that the present disclosure is not limited to the precise structures that have been described above and shown in the drawings, and that various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the scope of the appended claims.

Claims

1. A torque damping device (100), characterized in that: include: Torque limiter (10); A torsional vibration damper (20) comprises a single flange (21) and a friction control plate (24), wherein the friction control plate (24) is axially located on one axial side of the single flange (21) and is in frictional contact with the torque limiter (10). The other axial side of the friction control plate (24) is provided with an axial plate (241), the single flange (21) is provided with a circumferentially extending receiving groove (213), and the axial plate (241) is inserted into the receiving groove (213). When the torque is transmitted in the reverse direction, the axial plate (241) abuts against the abutting wall of the accommodating groove (213), and the single flange (21) drives the friction control plate (24) to rotate, so as to increase the damping between the single flange (21) and the first cover plate (15); when the torque is transmitted in the forward direction, the axial plate (241) is separated from the abutting wall of the accommodating groove (213), and the single flange (21) rotates relative to the friction control plate (24).

2. The torque damping device (100) according to claim 1, characterized in that: The torque limiter (10) comprises a retaining plate (11), two friction plates (12), a pressure plate (13), a first diaphragm spring (14), a first cover plate (15) and a second cover plate (16); the radial inner side of the retaining plate (11) is clamped between the two friction plates (12); the two friction plates (12) are clamped between the first cover plate (15) and the pressure plate (13); the first diaphragm spring (14) is axially abutted between the pressure plate (13) and the second cover plate (16); The radial outer side of the single flange (21) is provided with a plurality of stop grooves (212) along the circumferential direction, the radial inner side of the pressure plate (13) is provided with a plurality of stop plates (131) along the circumferential direction, the stop plates (131) are located in the stop grooves (212), and the stop plates (131) abut against the stop grooves (212) along the circumferential direction (W) for limiting the circumferential rotation angle of the single flange (21).

3. The torque damping device (100) according to claim 2, characterized in that: The stop plate (131) is radially located on the radial inner side of the retaining plate (11) and at least partially overlaps with the retaining plate (11) in the axial direction (A), and is used to limit the radial movement of the retaining plate (11) toward the single flange (21).

4. The torque damping device (100) according to claim 2, characterized in that: The stop plate (131) and the pressure plate (13) are fixedly connected via fasteners.

5. The torque damping device (100) according to claim 1, characterized in that: The torsional vibration damper (20) further comprises a coil spring (22), the single flange (21) having a first window (211) for accommodating the coil spring (22), and the inner wall of the radial inner side of the first window (211) being recessed radially inward to form the accommodating groove (213).

6. The torque damping device (100) according to claim 5, characterized in that: The friction control plate (24) further comprises a reset protrusion (242), the reset protrusion (242) protrudes radially from the friction control plate (24), and the reset protrusion (242) is circumferentially abutted against one end of the coil spring (22) close to the abutment wall (2131) of the accommodating groove (213).

7. The torque damping device (100) according to claim 1, characterized in that: The torsional vibration damper (20) further comprises a first friction pad (27), wherein the first friction pad (27) is frictionally abutted between the friction control plate (24) and the single flange (21) along the axial direction, and when transmitting torque in the forward direction, the first friction pad (27) is used to increase the damping between the single flange (21) and the friction control plate (24).

8. The torque damping device (100) according to claim 1, characterized in that: The axial plate (241) is formed by axially bending the radial outer end of the friction control plate (24).

9. The torque damping device (100) according to claim 5, characterized in that: The torsional vibration damper (20) further comprises: The second friction gasket (25) is in friction contact with the other axial side of the single flange (21), and the second friction gasket (25) protrudes toward the second cover plate (16) to form a hollow protrusion (251). A second diaphragm spring (26), wherein the second diaphragm spring (26) elastically abuts between the protruding portion (251) and the second cover plate (16).

10. The torque vibration reduction device (100) according to claim 5, characterized in that: Spring covers (28) are provided at both ends of the coil spring (22) in the circumferential direction, and the spring cover (28) comprises: An inserting portion (281), the inserting portion (281) being inserted into the inner ring of the coil spring (22); A cover cap (282) is located outside the coil spring (22) and has a diameter greater than the outer diameter of the coil spring (22). The side of the cover cap (282) away from the plug-in portion (281) is non-fixedly in contact with the first window (211) of the flange. The spring cover (28) is in contact with the first window (211) of the single flange (21) and isolates the coil spring (22) from the first window (211) in the radial direction and the circumferential direction.

11. The torque damping device (100) according to claim 10, characterized in that: The plug-in portion (281) is provided with a crushing rib (283), and the plug-in portion (281) is interference-fitted with the inner ring of the coil spring (22) via the crushing rib (283).

12. The torque vibration reduction device (100) according to claim 10, characterized in that: The spring cover (28) is made of plastic material, and the friction coefficient between the spring cover (28) and the first window (211) is smaller than the friction coefficient between the coil spring (22) and the first window (211).

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