WO2014202072A1

WO2014202072A1 - Torque transmission device

Info

Publication number: WO2014202072A1
Application number: PCT/DE2014/200245
Authority: WO
Inventors: Jan Hoffmann; Peter Wahl; Michael KÜHNLE
Original assignee: Schaeffler Technologies Gmbh & Co. Kg
Priority date: 2013-06-21
Filing date: 2014-06-05
Publication date: 2014-12-24
Also published as: DE112014002903A5; DE102014210685A1; CN105324589B; CN105324589A

Abstract

The invention relates to a torque transmission device (10) which can rotate about an axis of rotation (15) and has an input part (20), a first clutch element (50) and an output part (25), said first clutch element coupling said input part to said output part and limiting a rotation of the input part relative to the output part. The first clutch element is designed to provide a first restoring force (FR1) between the input part and the output part, the first restoring force being brought about by a radial offset of the first clutch element relative to the axis of rotation.

Description

Torque transfer device

The invention relates to a torque transmission device with the features according to claim 1.

There are known torque transmission devices that are designed as Torsionsschwingungsdämp- fer. The torsional vibration damper usually has a plurality of bow springs, which are fixed by an input part and an output part. A torque is introduced into the input part coming from an internal combustion engine. The input part transmits the torque to the bow spring, which dampens torque peaks and forwards the introduced torque to the output part.

It is an object of the invention to provide an improved torque device, which in particular has improved vibration damping properties. Furthermore, the torque transmission device should be cheaper to produce.

This object is achieved by means of the features of patent claim 1. advantageous

Embodiments are given in the dependent claims. According to the invention, it has been recognized that an improved torque transmission device can be provided in that the torque transmission device comprises an input part, a first coupling element and an output part. The torque transmitting device is further rotatable about an axis of rotation. The first coupling element couples the input part to the output part and limits a rotation of the input part relative to the output part. Furthermore, the first coupling element is designed to provide a first restoring force between the input part and the output part. The first restoring force is effected by a radial offset of the first coupling element.

This embodiment has the advantage that a torque transmission device can be provided which is particularly cost-effective and simple. Furthermore, the torque transmission device has, by means of the abovementioned embodiment, a stiffness which increases with increasing speed and which is particularly well suited to an operating mode. th of the internal combustion engine is adaptable due to an additional, provided by the torque transmission device degree of freedom.

In a further embodiment, the first coupling element has a neutral position and at least one actuation position. The first coupling element is arranged radially offset in the actuating position, in particular radially inwardly, relative to the neutral position. During operation of the torque transmission device, that is, when it rotates about the axis of rotation, a kinematics can be provided by the radial offset and the centrifugal force acting on the first coupling element, on the one hand a simple torque transmission between the input part and the output part is made possible while torque fluctuations in the Transmission of the torque between the input part and the output part can be attenuated. In this way, it is further ensured that after introducing a torque peak, the input part and / or the output part are guided back into the neutral position to intercept more torque peaks can. In this way, it is ensured that torque peaks can be effectively damped by the torque transmission device.

In a further embodiment, the input part and / or the output part has a second neutral position corresponding to the first neutral position of the first coupling element. The input part and / or the output part furthermore have at least one second actuation position corresponding to the first actuation position of the first coupling element. The first coupling element is designed to move the input part and / or the output part from the second actuation position into the second neutral position by means of the first restoring force.

In a further embodiment, the first restoring force is variable depending on the speed. Preferably, as the rotational speed of the torque transmitting device increases, the first restoring force increases in order to move the first coupling element from the first actuation position to the first neutral position. In this way, at higher speeds, the torque transmitting device is stiffer with respect to torque peaks and thus simultaneously adapts to the torque fluctuations of an internal combustion engine connected to the torque transmission device. Thereby, the torque transmission device can be easily adapted to a performance of the internal combustion engine. In a further embodiment, the first coupling element is formed, the first

To cause restoring force by a movement along a guideway, in particular along a pendulum track of the first coupling element. Advantageously, the first coupling element is formed to be provided for providing the first restoring force by acting on the first coupling element centrifugal radially outward along the guideway. This embodiment has the advantage that based on the guideway both the first restoring force in direction and strength can be set in a simple manner.

In a further embodiment, the first coupling element has at least one first recess arranged in the input part, at least one first coupling part, at least one second and third recess arranged in the first coupling part, at least one fourth recess arranged in the output part, and at least two rolling elements. A first rolling element extends through the first recess and the second recess. The first rolling element rolls off at the first recess and at the second recess and couples the input part to the first coupling part. A second rolling element extends through the third recess and the fourth recess. The second rolling element rolls off at the third recess and at the fourth recess and couples the first coupling part to the output part. The recesses define by the rolling of the associated rolling element, the guideways of the coupling element. This embodiment has the advantage that a particularly low-friction coupling between the input part and the output part can be provided.

In a further embodiment, the first restoring force is adjustable by an embodiment of the guideway. This refinement has the advantage that the first restoring force can be adapted to the operating behavior of the internal combustion engine connected to the torque transmission device in a simple manner.

In a further embodiment, the coupling element is limitedly displaceable relative to the input part. In particular, this is achieved via an effect of the first and / or the second rolling element of the coupling element.

In a further embodiment, the recesses have a corresponding recess contour, wherein a first recess contour of the first recess to a second recess contour of the second recess and a third recess contour contour of the third recess to a fourth recess contour of the fourth recess are shaped such that upon rotation of the input part relative to the output part, the coupling element is guided by the rolling on the respectively associated recesses contour rolling elements radially inward. In a simultaneous rotation of the torque transmitting device, the first restoring force acts as a counter force against the torque introduced into the input part and causes the torque from the input part can be passed through the coupling part in the output part, without the rolling elements abut in an end position. As a result, a particularly quiet torque transmission device can be provided.

In a further embodiment, the coupling element comprises a second coupling part, wherein a first coupling means is provided. The first coupling means connects the first coupling part with the second coupling part, wherein the first coupling means is designed to provide a second restoring force for amplifying the first restoring force. As a result, reliable damping of torque peaks can be provided, especially at low speeds.

In a further embodiment, the first coupling means comprises at least one elastic element, preferably a spring element. In this way, a particularly inexpensive coupling agent can be provided.

In a further embodiment, the first coupling means is arranged in the circumferential direction between the coupling parts. In this way, a particularly space-saving design of the torque transmission device can be provided.

In a further embodiment, a second coupling means is provided, wherein the second coupling means is arranged between the input part and the output part and couples the input part to the output part for torque transmission between the input part and the output part. In this way, particularly high torques between the input part and the output part can be transmitted while torque peaks are damped even at high torques.

In a further embodiment, a guide means is provided, wherein the guide means is connected to the input part or to the output part. The guiding means is designed to guide the first coupling element in the radial direction and to provide a torque transmission between the input part or output part and the coupling element.

In this case, it is particularly advantageous if the guide means comprises at least one guide element, at least one guide roller and at least one guide sleeve. The guide roller is arranged between the guide sleeve and the guide element. The guide sleeve is connected to the coupling part. The guide element is connected to the input part or to the output part. Advantageously, the guide element and the guide sleeve extend in the radial direction. In this way, a particularly low-friction guidance and simultaneous torque transmission between input part or output part and coupling part can be provided.

The invention will be explained in more detail with reference to figures. Showing:

Figure 1 is a plan view of a torque transmitting device according to a first embodiment in a first operating position;

2 shows the torque transmission device shown in Figure 1 in a second

Operating position;

Figure 3 is a perspective view of a variant of the torque transmission device shown in Figures 1 and 2;

Figure 4 is a plan view of a torque transmitting device according to a second embodiment;

FIG. 5 shows a diagram with a stiffness plotted against a rotational speed n of the torque transmission device;

FIG. 6 shows a perspective sectional view through a torque transmission device according to a third embodiment; FIG. 7 shows a perspective sectional view through the embodiment of the torque transmission device shown in FIG. 4 in an enlarged view;

Figure 8 is a perspective view of the torque transmitting device shown in Figures 4 and 5;

Figure 9 is a plan view of the torque transmitting device shown in Figures 6 to 8;

FIG. 10 shows a schematic sectional view through a torque transmission device according to a fourth embodiment;

Figure 1 1 is a plan view of the torque transmission device shown in Figure 9;

FIG. 12 shows a schematic sectional view through a torque transmission device according to a fifth embodiment;

FIG. 13 shows a sectional view along a sectional plane A-A shown in FIG. 10 through the torque transmission device;

Figure 14 is a perspective view of a development of the embodiment of the torque transmission device shown in Figure 3;

FIG. 15 shows a schematic structure of a drive train according to a first embodiment with the torque transmission device shown in FIGS. 1 to 14; and

16 shows a schematic structure of a drive train according to a second

Embodiment.

1 shows a plan view of a torque transmission device 10 according to a first embodiment in a first actuation position, and FIG. 2 shows a plan view of the torque transmission device 10 shown in FIG. 1 in a second actuation position. supply position. FIG. 3 shows a perspective view of a variant of the torque transmission device 10 shown in FIGS. 1 and 2.

The torque transmission device 10 is rotatable about a rotation axis 15. Die

Torque transmission device 10 comprises an input part 20 and an output part 25. The input part 20 has radially inwardly a first receptacle 30 in order to provide a torque-locking connection between the input part 20 and an output shaft (not shown) of an internal combustion engine. The output part 25 has a second receptacle 35 in order to provide a torque-locking connection with a transmission input shaft 36. Of course, it is also conceivable that torque-resistant connections to other components of a drive train (see FIGS. 14 and 15) are provided via the receptacles 30, 35. It is also conceivable that the receptacles 30, 35 are dispensed with and the input part 20 or the output part 25 is connected to other components of the drive train in a different manner, for example by means of a riveted connection.

The input part 20 has radially outwardly of the first receptacle 30 two oppositely arranged first actuating arms 40. The output part 25 is formed analogously to the input part 20 and has radially on the outside to the second receptacle 35 in each case also two oppositely disposed second actuating arms 45. Furthermore, the torque transmission device 10 comprises two coupling elements 50. The coupling elements 50 are designed to couple the input part 20 with the output part 25 in order to provide a torque transmission between the input part 20 and the output part 25.

The coupling element 50 has a coupling part 55 and a coupling means 75. The coupling part 55 is formed part-ring-shaped. The coupling part 55 has a spring receptacle 65 on a front face 60 arranged in the circumferential direction. In the spring receptacle 65, a fixing pin 70 is further provided. In the spring receptacle 65, the coupling means 75 is arranged which is designed as a spring element in the figures 1 and 2 by way of example as a helical spring. Of course, other spring elements such as coil springs, rubber elements or double springs are conceivable as coupling means 75. In this case, the coupling means 75 surrounds the fastening pin 70 on the circumferential side, so that a clamping connection 80 between the coupling means 75 and the coupling part 55 can thereby be provided. The spring retainer 65 secures the coupling means 75 radially outward in the rotating state and reduces one Bending of the coupling means 75 radially outwardly by a radially outside concerns the coupling means 75 on the spring retainer 75. The spring retainer 65 and the mounting pin 70 are respectively provided on the two opposite end faces 60 of the coupling parts 55. The coupling means 75 connect in the circumferential direction, the two coupling parts 55. The coupling means 75 are formed as helical compression springs.

The coupling element 50 has a guide means 81 which is designed to guide the coupling part 55. The guide means 81 has on the first actuating arm 40 radially on the outside a first recess 85 with a first recess contour 90. The first recess 85 is designed to be continuous in the axial direction. In the coupling part 55, the guide means 81 has a second recess 95 and a third recess 100. The second and the third recess 95, 100 are arranged approximately at the same radial height and spaced from each other in the circumferential direction. The second recess 95 has a second recess contour 105 and the third recess 100 has a third recess contour 1 10. In the second actuating arm 45, the guide means 81 has a fourth recess. The fourth recess 15 includes a fourth recess contour 120.

A first rolling element 125 extends through the first recess 85 and the second recess 95. The second rolling element 130 extends through the third recess 100 and the fourth recess 15. The first Rolling element 125 rolls off upon actuation of the input part 20 on the first recess contour 90 and the second recess contour 105 and defines a first guide track 140. The second rolling element 130 rolls on the third recess contour 1 10 and on the fourth recess contour 120 and defines a second guide track 145. The first guide track 140 is designed identically to the second guide track 145 in the embodiment. Of course, it is also conceivable that the first guide track 140 deviating from the second guide track 145 is configured.

Due to the rotation of the torque transmission device 10 acts on the components 20, 30, 55, 125, 130 of the torque transmission device 10 each have a centrifugal force F _F. The centrifugal force F _F acting on the coupling part 55 pulls the coupling part 55 radially outward. In a purely rotating operating state of the torque transmission device 10, that is to say when no torque M is input and / or discharged into the torque transmission device 10, the coupling parts 55 are in a neutral position, which in FIG. gur 1 is shown by dashed lines. The neutral position is determined by the guideways 140, 145 and is in an equilibrium state. The coupling part 55 in this state does not oscillate in the circumferential direction along the guideways 140, 145.

If in the rotating state of the torque transmission device 10 via the first receptacle 30 of the input part 20 a (possibly fluctuating) torque M in the input part 20 and / or discharged, so the coupling member 55 moves out of the neutral position with respect to the input part 20 along the first Guideway 140. In this case, the first rolling element 125 rolls on the first recess contour 90 and the second recess contour 105. Due to the radially inwardly guided configuration of the first guide track 140, the coupling part 55 is pressed radially inwards by the input part 20 and transferred from the neutral position into a first actuation position (shown in FIG. 1 by solid lines).

Due to the radially inwardly extending first guide track 140 and a radial offset of the coupling part 55 in the first actuation position to the neutral position causes the centrifugal force F _F corresponding to the first guide track 140 designed first restoring force F _R1 . The first restoring force F _R1 acts as a counterforce to a transmission force FQ resulting from the torque M. By the first restoring force F _R1 , the coupling part 50 is clamped relative to the input part 20. Due to the tension, the torque M can be transmitted from the input part 20 to the coupling part 55. Due to the radial offset due to the introduced torque M, the coupling means 75 are further braced. The coupling means 75 provide a second restoring force F _R2 due to the tension, which reinforces the first restoring force F _R1 and thus the tension of the coupling part 55 relative to the input part 20.

The coupling member 55 also provides at the second guide track 145, the first return force F _R1 ready to bring the coupling member 55 also relative to the output member 25 back to the neutral position. The first restoring force F _R1 is dependent on the second guide track 145 of this. If the second guide track 145 differs from the first guide track 140, then correspondingly differently formed restoring forces F _R1 act on the two guide tracks 140, 145. By the first restoring force F _R1 acts on the second guide track 145 as a counter force to be discharged from the coupling part 55 Transmission power FQ. As a result, the coupling part 55 is braced against the output part 25 via the second rolling element 130. As a result of the tensioning, the torque M or the transmission force FÜ can be guided out of the coupling part 55 into the output part 25. Again, the first restoring force F _R1 is reinforced by the second restoring force F _R2 , so that even at low speeds at which a low centrifugal force F _f acts on the coupling member 55, a reliable torque transmission is ensured by the coupling member 55 to the output member 25, without the input part 20 relative to the coupling part 55 is rotated so much that a torque transmission by abutment of the first rolling element 125 at the first and second recesses 85, 95 takes place. Furthermore, by the described embodiment, a higher torque can be transmitted by means of the torque transmission device 10 between the input part 20 and the output part 25.

To a restriction of the coupling element 50 with respect to the input part 10 and the output part 25 can be arranged additionally in Figures 1 and 2 above the plane another coupling part 50 to transmit the torque M between the input part 20 and the output part 25.

If a fluctuating torque M, that is to say a torque which increases and decreases in relation to a constant torque over time, is introduced into the input part 20, then the transmission force FÜ increases or decreases accordingly. With increasing transfer force Fu, the first restoring force F _R1 and the second restoring force F _{R2 are} less than the transfer force FÜ. As a result, the input part 20 can continue to rotate relative to the coupling part 55. In this case, the input part 20 presses radially along the first guide track 140 inwards into a second actuation position. In the second actuation position, the coupling part 55 is thus arranged radially inward than in the first actuation position. At the same time, the coupling means 75 are further braced and provide an amplified second restoring force F _R2 . Since the radial offset of the coupling part 55 is only small, the radial offset in the second actuation position has only a slight effect on the centrifugal force F _F acting on the coupling part. The centrifugal force F _F decreasing with the radial offset is compensated for by the design of the guide tracks 140, 145 for the first restoring force F _R1 such that with increasing radial displacement of the coupling part 55 from the neutral position radially inwards, the guide track 140, 145 has an increasing curvature having. By the rotation of the input part 20 to the coupling part 55 is in the second operating position, a more curved portion of the guideway 140 is set. Due to the curvature of the guideway 140, 145, the centrifugal force F _{F is converted} into an amplified first restoring force F _R1 , which in turn acts as a counterforce to the transmission force F _Ü and causes an increased tension of the coupling part 55 relative to the input part 20. The gain of the tension of the coupling part 55 hurried by 90 ° out of phase with the introduced fluctuating torque M afterwards. Characterized the coupling parts 55 are excited to vibrate along the guideways 140, 145 and take on the task of a pendulum mass of a centrifugal pendulum. As a result, the fluctuating torque is canceled and only as described above discharged in a highly damped state from the coupling part 55 in the output part 25. Thus, in the embodiment, a combination of a torsional vibration damper can be provided with a centrifugal pendulum, can be compensated by the effect and easily the fluctuating torque and thus the ride comfort of a vehicle equipped with such a torque transmission device 10 can be increased.

Furthermore, the torque transmission device 10 depending on the embodiment of

Guideways 140, 145 a linear (see Figure 3) or nonlinear behavior (Figures 1 and 2) of the first and / or second restoring force F _R1 , F _R2 with respect to a twist angle between the input part 20 and the output part 25 on. In this case, a linear behavior is achieved by a rectilinear alignment of the recesses 85, 95, 100, 15. Thereby, the torque transmission device 10 in a simple manner, namely by adapting the guideways 140, 145 are adapted to a performance of the internal combustion engine of the motor vehicle.

The first restoring force F _R1 is speed-dependent as a result of the centrifugal force acting on the coupling part 55, so that the first restoring force F _R1 increases with an increasing rotational speed of the torque transmission device 10. As a result, the torque transmission device 10 becomes stiffer with increasing rotational speed, so that the torque transmission device 10 thus automatically adapts itself to the torque peaks which decrease as the rotational speed increases. By means of the configuration of the guide tracks 140, 145 and / or a variation of a mass of the coupling part 55, the rigidity of the torque transmission device 10 can be varied particularly easily. In the embodiment, two coupling parts 55 and two coupling means 75 are provided.

Of course, it is also conceivable to provide a different number and a different embodiment of the coupling means 75 and the coupling parts 55. It is also conceivable that a different number of recesses 85, 95, 100, 1 15 is provided to couple the input part 20 with the output part 25 via the coupling element 50.

In Figure 2, the torque transmitting device 10 is shown in a maximum position of rotation. The rolling elements 125, 130 strike the recesses 85, 95, 100, 15 in the circumferential direction and thus limit a maximum angle of rotation between the input part 20 and the output part 25 the coupling parts 55 beat each other. In this way, a noise of the torque transmission device 10 is kept low. Furthermore, it is ensured in this way that a particularly high torque can be transmitted via the torque transmission device 10.

FIG. 4 shows a plan view of a torque transmission device 200 according to a second embodiment. FIG. 5 shows a diagram with a stiffness plotted against a rotational speed n of the torque transmission device 200.

The torque transmission device 200 is shown in a first actuation position analogous to the actuation position shown in FIG. The torque transmission device 200 is designed substantially identical to the torque transmission device 10 shown in FIGS. 1 and 2. Deviating from this, a further coupling means 201 is additionally provided which connects the input part 20 to the output part 25. The further coupling means 201 comprises a retainer 205 arranged in the input part 20 and / or output part 25. A spring-loaded memory 210 of the further coupling means 201 is arranged in the retainer 205. The spring accumulator 210 is formed in the embodiment as a bow spring. Of course, it is also conceivable that other spring stores, in particular rectilinear coil springs, are arranged in the retainer 205. Also, the configuration of the retainer 205 may be different. In the embodiment, the retainer 205 extends in the circumferential direction. Of course, it is also conceivable that the container 205 is rectilinear. In the embodiment shown in FIG. 3, the coupling means 75 is shorter in the circumferential direction than in FIGS. 1 and 2. Of course, it is also conceivable that the coupling means are formed identical to Figure 1 and 2.

The spring accumulator 210 couples the input part 20 to the output part 25. If the torque M is introduced into the torque transmission device 10 via the input part 20, then the input part 20 is rotated relative to the output part 25. In addition to the torque transmission as described in FIGS. 1 and 2, a part of the torque M is transmitted to the spring accumulator 210 by the spring accumulator 210 is compressed in the circumferential direction. Due to the compression of the spring accumulator 210 presses at a longitudinal end of the spring accumulator 210 opposite the input part 20 to the output part 25 and transmits part of the torque M from the input part 20 to the output part 25. Of course, in the towing mode of a vehicle, a torque from the output part 25 on the input part 20 are transmitted. By the spring accumulator 210, a third restoring force F _R3 is further provided to return the coupling member 55 in the neutral position. By means of the further coupling means 201, a fluctuating torque M can be further damped and thus a particularly well-damping torque transmission device 200 can be provided.

Due to the configuration of the coupling element 50, an operating behavior of the torque transmission device 200 can be provided which follows a first characteristic curve 215. The further coupling means 201 has an independent operating behavior which can be designed independently of the coupling element 50 in accordance with a second characteristic 220. By coupling the coupling element 50 with the further coupling means 201, the two characteristic curves can be combined to form an overall characteristic 225 so that the first characteristic curve 215 of the coupling element 50 can be adapted in a simple manner by the further coupling means 201 and thus further the operating behavior of the torque transmission device 200 can be improved.

FIG. 6 shows a perspective sectional view through a torque transmission device 300 according to a third embodiment. FIG. 7 shows an enlarged view of the perspective sectional view of the torque transmission device 300 shown in FIG. 6. FIG. 8 shows a perspective view of the torque transmission device 300 shown in FIGS. 6 and 7. FIG. 9 shows a plan view of the torque transmission device 300 shown in FIGS , The torque transmission device 300 has a disk carrier 305 arranged on the left side in FIGS. 6 and 7. The plate carrier 305 serves to fix plates of a friction clutch (not shown). The plate carrier 305 is arranged on the left side on the input part 20. The input part 20 is disc-shaped in the embodiment. The input part 20 includes a first input disk 310 and a second input disk 315. The first input disk 310 is axially spaced from the second input disk 315 and coupled to the second input disk 315 via standoffs 320. Between the two input disks 310, 315, the coupling element 50 is arranged. The output part 25 is also arranged between the two input disks 310, 315. The output part 25 is arranged radially inwardly of the coupling element 50. The output part 25 is coupled to a spring damper 321 designed as a further coupling element. The spring damper 321 comprises a disc 325, which is torque-connected to the output part 25. The disk 325 and the output part 25 form a retainer 330 of the spring damper 321, in which a spring accumulator 335 of the spring damper 321 is arranged. The disk 325 has a first stop 340, to which a first longitudinal end 345 of the spring accumulator 335 is assigned. Opposite the first longitudinal end 345, a hub flange 355 of the spring damper 321 is provided at a second longitudinal end 350 of the spring accumulator 335, which is arranged between the disc 325 and the output part 25 in the axial direction. The hub flange 355 has, radially inward of the disc 325, a shaft receptacle 360 into which a transmission input shaft 361 can be inserted. The shaft receiver 360 is designed to form a shaft-hub connection with the transmission input shaft 361.

The coupling element 50 is designed similarly to the coupling element 50 shown in FIGS. 1 to 5. In the embodiment, the coupling element 50 has three coupling parts 55, which are designed in the form of a partial ring and are arranged on the circumference radially outside the output part 25. In the circumferential direction, the coupling parts 55 are each connected to the coupling means 75. The guide means 81 is adapted to the changed number of coupling parts 55. The recesses 85, 95, 100, 15 are formed as shown in FIGS. 1 to 3 and, together with the rolling elements 125, 130, define the guideways 140, 145 by rolling the rolling elements 125, 130 against the recesses 90, 105, 1 10, 120. The mode of operation of the torque damping between the input part 20 and the output part 25 corresponds to the torque transmission device 10 shown in FIGS. 1 and 2. The spring damper 321 adjoining the output part 25 further enables a fluctuating torque M discharged from the output part 25 to continue so that a particularly smoothly running torque can be provided to a transmission connected to the torque transmission device 300.

The torque M is introduced from the output part 25 in the disc 325. The output part 25 is coupled to the disk 325 via further spacer bolts (not shown). The output part 25 and the disc 325 press the front side at the first longitudinal end 345 of the spring accumulator 335 and thus initiate the torque coming from the output part 25 into the spring accumulator 335. The spring accumulator 335 is thereby compressed. The spring accumulator 335 is pressed radially outward against the retainer 330 by a centrifugal force acting on the spring accumulator 335. The compressed spring accumulator 335 is the torque introduced into it by abutting a second longitudinal end 350 of the spring accumulator 335 to the hub flange 355 from this. By circumferentially rubbing the spring accumulator 335 thereby torque peaks of the torque M in the spring damper 321 are again reduced, so that at the hub flange 355 a particularly uniform torque M can be provided.

The downstream switching of the spring damper 321 of the torque transmission device 10 already shown in FIGS. 1 and 2 has the advantage that a particularly compact torque transmission device 300 can be provided, since the spring damper 321 is arranged radially on the inside of the torque transmission device 10 already known from FIGS. 1 and 2 can. As a result, the installation space is used efficiently and at the same time a particularly small fluctuating torque can be provided on the output side of the torque transmission device 300 on the shaft receptacle 360.

FIG. 10 shows a longitudinal section through a torque transmission device 400 according to a fourth embodiment. FIG. 11 shows a plan view of the torque transmission device 400 shown in FIG.

The torque transmission device 400 is configured similarly to the torque transmission device 10 shown in FIGS. 1 to 3. The torque transmitting device 400 has the input part 20 extending radially from inside to outside. On both sides of the input part 20, the coupling element 50 has a first coupling part 405 and a second coupling part 410. The coupling parts 405, 410 are moved by means of the guide means 81 along the guideways 140, 145 out. The first coupling part 405 is connected by means of spacer bolt 415 with the second coupling part 410. The coupling parts 405, 410 each have the second and third recesses 95, 100. In the embodiment, by way of example, the second and third recesses 95, 100 are kidney-shaped. The second and third recesses 95, 100 are open radially outward, whereas the first and the fourth recesses are opened radially inwards.

The coupling element 50 also has a further guide means 430. The further

Guide means 430 comprises a guide sleeve 435, a guide element 440 and a plurality of guide rollers 445. The guide element 440 is web-shaped and is connected to the output part 25. The guide sleeve 435 is arranged in the coupling part 405, 410. Between the guide member 440 and the guide sleeve 435 while the guide rollers 445 are provided. The guide rollers 445 ensure a bearing of the coupling part 405, 410 in order to perform a low-friction movement radially from the inside to the outside along the guide member 440 can. The guide sleeve 435 is arranged between the second recess 95 and the third recess 100. The further guide means 430 also serves to transfer an introduced into the coupling part 405, 410 torque M from the coupling part 405, 410 in the output part 25. Thus, the further guide element 430 has an additional torque-transmitting function task.

If a torque M is introduced into the torque transmission device 400 via the input part 20, a further torque transmission from the input part 20 to the coupling parts 405, 410 takes place analogously to the torque transmission described in FIG. 1 from the input part 20 to the coupling parts 55 shown there these coupling parts 405, 410, the first restoring force F _R1 ready. If the torque M or the corresponding corresponding transfer force F _{Ü introduced} from the input part 20 in the coupling parts 405, 410, the coupling parts 405, 410 are moved from the neutral position radially inwardly into an actuating position. Due to the radial offset, the centrifugal force F _F in conjunction with the defined by the recesses 95, 100, 85, 1 15 guideways 140, 145 to the effect that the centrifugal force F _F by the guideways 140, 145 partially converted into the first reset force F _R1 is that would like to move the coupling parts 405, 410 back to the neutral position. The first restoring force F _R1 acts as a counterforce to the transmission force F _Ü , so that the coupling part 405, 410 braced relative to the input part 20 and the torque M is introduced into the coupling parts 405, 410. From the coupling parts 405, 410, the torque is derived by the further guide means 430 in the output part 25. Due to the torque transmission by means of the coupling elements 50, a lagging of the coupling parts 405, 410 is achieved with a phase shift of 90 °, so that torque fluctuations in the torque M to be transmitted can be compensated for particularly well by the mass of the coupling parts 405, 410 and the coupling means 75. The design of the coupling element 50 and its guidance along the guideway 140, 145 causes the torque transfer device 400 as a combination of a centrifugal pendulum and a torsional vibration damper. The guideways 140, 145 form pendulum tracks.

FIG. 12 shows a longitudinal section through a torque transmission device 500 according to a fourth embodiment. FIG. 13 shows a sectional view through the torque transmission device 500 shown in FIG. 12 along a sectional plane A-A shown in FIG.

The torque transmission device 500 is designed substantially identical to the torque transmission device 400 shown in FIGS. 10 and 11. Deviating from this, the torque transmission device 500 has a two-part input part 20 which limits a coupling part 505 in the axial direction on both sides in the axial direction. The two input parts 20 are connected to each other via spacer bolts 510, for example. This ensures that the torque M is transmitted to both input parts 20. Both the mode of operation and the further construction of the torque transmission device 500 are identical to the torque transmission device 400 shown in FIGS. 10 and 11.

The torque transmission device 500 has the advantage that as a result of the design of the coupling elements 50, the number of components can be reduced overall compared with the embodiment of the torque transmission device 400 shown in FIGS. 10 and 11. As a result, both the weight of the torque transmission device 500 can be reduced overall and also a cost-effective torque transmission device 500 can be provided.

In FIGS. 10 to 13, the coupling part 405, 410, 505 has a substantially T-shaped configuration, in the middle of which the further guide means 430 is arranged. This Design has the advantage that a particularly large mass for the coupling parts 405, 410, 505 can be provided. Of course, it is also conceivable to form the coupling parts 405, 410, 505 differently. It is also conceivable that the further guide means 430 is formed differently.

In the embodiments, the torque transmitting device is formed mainly of a combination of centrifugal pendulum and torsional vibration damper.

Of course, it is also conceivable that the embodiments shown in the figures of the torque transmission device 10, 200, 300, 400, 500 as a dual mass flywheel, as a torque converter or torsional vibration or in the application of a clutch device, preferably in a wet clutch, for example, a starting clutch or dual clutch executed are.

It is also conceivable that a stop is provided between the input part 20 and the output part 25, in particular to avoid the second restoring force causing coupling element 50, in particular to a striking of the coupling parts 55, 405, 410 with each other. Additionally or alternatively, a stop on the coupling means 75 may be provided, for example by an elastic element or by going to block of the coupling means 75 shown in the embodiments. It is also conceivable that designed as a helical spring coupling means 75 additionally have an inner spring. It is also conceivable that a free path is provided, which, when exceeded, causes one or both coupling means 75 to be acted upon.

FIG. 14 shows a perspective illustration of a development of the embodiment of the torque transmission device shown in FIG. The development corresponds essentially to the torque transmission device 10 shown in FIG. 3. In addition, in order to be able to provide guideways 140, 145, which are formed particularly steeply relative to the circumferential direction, in addition to the rolling elements 125, 130 or to the recess contours 90, 105 , 1 10, 120 a first teeth 550, 555 provided, wherein a second toothing 560 of the rolling elements 125, 130 in each case the corresponding toothing 550, 555 of the recess contour 90, 105, 1 10, 120 engages. As a result, rolling of the rolling element 125, 130 on the recess contour 90, 105, 110, 120 can be ensured if rolling sliding conditions would no longer be met. This allows the Guide track 140, 145 are particularly steep relative to the circumferential direction radially inwardly out.

FIG. 15 shows a schematic representation of a drive system 600 according to a first embodiment. The drive system 600 includes a drive machine 605, which may be designed, for example, as an internal combustion engine. The prime mover 605 is connected to a clutch 610. The coupling 610 is designed as a converter clutch, which has a hydrodynamic converter 615 and a lock-up clutch 620. The clutch 610 is connected to the torque transmission device 300 shown in FIGS. 6 to 7. The torque transmission device 300 is connected on the right side to an output flange 625.

As already explained in FIGS. 6 to 9, the torque transmission device 300 has the input part 20, which is connected to the coupling 610. For this purpose, the input part 20 has a connection both to the lockup clutch 620 and to an output side of the hydrodynamic converter 615. The input part 20 is connected via the guide means 81 with the coupling parts 55. The guide means 81 acts as a lever system, by means of which the torque M is transmitted to the coupling part 55.

The coupling means 75 is a spring element in FIG. 15 and is between the two

Coupling 55 arranged. The spring damper 321 connected to the output part in FIGS. 6 to 9 is shown in FIG. 15 as a spring element, which is arranged between the input part 20 and the hub flange 355.

The prime mover 605 provides a torque M, which is provided in the closed state via the clutch 610 of the torque transmitting device 300. The torque transmitting device 300 passes this to the output flange 625 to drive a vehicle in which the powertrain 600 is mounted.

FIG. 16 shows a further schematic representation of a drive system 700 in a second embodiment. The drive system 700 is similar to the drive system 600 shown in FIG. Deviating from this, however, instead of the torque transmission device 300 shown in FIG. 15, the torque transmission device 10 already shown in FIGS. 1 to 3 is available for transmitting the torque M from the coupling device. ment 610 provided on the output flange 625. The mode of operation of the torque transmission device has already been explained in FIGS. 1 to 3. In this case, the torque transmission device 10 transmits the torque coming from the clutch 610 to the output flange 625.

It should be understood that other components in the powertrain 600, 700 may of course be provided to transmit the torque M between the prime mover 605 and the output flange 625. For example, it is conceivable that the coupling 610 is designed as a wet clutch. It is also conceivable, for example, to provide a double clutch for the clutch 610. To the output flange 625, for example, a manual, but also a semi or fully automatic automatic switch can be connected.

It should be noted that the guide means 81 shown in FIGS. 1 to 16 are exemplary. In particular, it is conceivable that the guide means 81 are designed differently and in particular have different cutout contours. It is also conceivable that, for example, the third and fourth recesses 100, 15 are dispensed with. It is also conceivable to combine the features shown in FIGS. 1 to 16 or different configurations of the torque transmission devices 10, 200, 300, 400, 500, 600 with one another.

LIST OF REFERENCE NUMBERS

Torque transmission device rotation axis

introductory

output portion

First recording

Second shot

Transmission input shaft

First operating arm

Second actuating arm

coupling element

coupling part

face

spring mount

fastening pin

coupling means

clamp connection

guide means

First recess

First recess contour

Second recess

Third recess

Second recess contour

Third recess contour

Fourth recess

Fourth recess contour

First rolling element

Second rolling element First guideway

Second guideway

Torque transmission device Further coupling agent 205 Retainer

210 spring accumulator

215 First characteristic

220 Second characteristic

225 overall characteristic

300 torque transmitting device

305 plate carrier

310 First input disk

315 Second input disk

320 spacers

321 spring damper

325 slice

330 retainer

335 spring accumulator

340 stop

345 First longitudinal end

350 Second longitudinal end

355 hub flange

360 wave recording

361 transmission input shaft

400 torque transmitting device

405 First coupling part

410 second coupling part

415 spacer bolts

420 spacers

guide means

guide sleeve

guide element

leadership

500 torque transmission device 505 coupling part

510 spacers 550 First toothing

555 First gearing

560 Second toothing

600 torque transmission device

605 prime mover

610 clutch

615 transducers

620 lockup clutch

625 output flange

Claims

Patent claims

Torque transmission device (10; 200; 300; 400; 500; 600), which is rotatable about an axis of rotation (15),

- having an input part (20), a first coupling element (50) and an output part (25),

- wherein the first coupling element (50) couples the input part (20) to the output part (25) and limits rotation of the input part (20) relative to the output part (25),

- wherein the first coupling element (50) is designed to provide a first restoring force (F _R1 ) between the input part (20) and the output part (25), characterized in that

- The first restoring force (F _R1 ) is caused by a radial offset of the first coupling element (50) with respect to the axis of rotation (15).

Torque transmission device (10; 200; 300; 400; 500; 600) according to claim 1, characterized in that the first coupling element (50) has a neutral position and at least one actuation position, wherein the first coupling element (50) in the actuation position radially, in particular radially inwards, offset from the neutral position.

Torque transmission device (10; 200; 300; 400; 500; 600) according to claim 1 or 2, characterized in that

- the first restoring force (F _R1 ) is variable depending on the speed,

- The first restoring force (F _R1 ) preferably increases with an increasing speed of the torque transmission device (10; 200; 300; 400; 500; 600) in order to move the first coupling element (50) from the first actuation position into the neutral position.

Torque transmission device (10; 200; 300; 400; 500; 600) according to one of claims 1 to 3, characterized in that

- the first coupling element (50) is designed to bring about the first restoring force (F _R1 ) by moving along a guide track (140, 145), in particular along a pendulum path of the first coupling element (50), - wherein advantageously the first coupling element (50) is designed to be pulled radially outwards along the _guide track (140, 145) by a centrifugal force (F _F ) acting on the first coupling element (50) in order to provide the first restoring force (F R1). .

5. Torque transmission device (10; 200; 300; 400; 500; 600) according to claim 4, characterized in that

- the first coupling element (50) has at least one first recess (85) arranged in the input part (20), at least one first coupling part (55; 405, 410; 505), at least one arranged in the first coupling part (55; 405, 410; 505). second and third recesses (95, 100), at least one fourth recess (1 15) arranged in the output part (25) and at least two rolling elements (125, 130),

- wherein a first rolling element (125) extends through the first recess (85) and the second recess (95),

- the first rolling element (125) rolling on the first recess (85) and the second recess (95) and coupling the input part (20) with the first coupling part (55; 405, 410; 505),

- wherein a second rolling element (130) extends through the third recess (100) and the fourth recess (1 15),

- the second rolling element (130) rolling on the third recess (100) and the fourth recess (1 15) and coupling the first coupling part (55; 405, 410; 505) with the output part (25),

- The recesses (85, 95, 100, 110) determine the guide track (140, 145) of the coupling element (50) by rolling the associated rolling element.

6. Torque transmission device (10; 200; 300; 400; 500; 600) according to claim 4 or 5, wherein the first restoring force (F _R1 ) is adjustable by a design of the guide track (140, 145).

7. Torque transmission device (10; 200; 300; 400; 500; 600) according to one of claims 1 to 6, wherein the coupling element (50) can be displaced to a limited extent relative to the input part (20) and / or the output part (25), in particular via an action of the first and/or second rolling element (125, 130) of the coupling element (50).

8. Torque transmission device (10; 200; 300; 400; 500; 600) according to one of claims 4 to 7, characterized in that the recesses (85, 95, 100, 1 10) have a corresponding recess contour (90, 105, 1 10 , 120), wherein a first recess contour (90) of the first recess (85) forms a second recess contour (105) of the second recess (95) and a third recess contour (1 10) of the third recess (100) forms a fourth recess contour ( 120) of the fourth recess (1 15) are shaped in such a way that when the input part (20) is rotated relative to the output part (25), the coupling part (55; 405, 410; 505) is rolled by the rolling elements (125) which roll on the respective associated recess contours , 130) is guided radially inwards.

9. Torque transmission device (10; 200; 300; 400; 500; 600) according to one of claims 1 to 8, characterized in that the coupling element (50) comprises a second coupling part (55; 405, 410; 505), wherein a first Coupling means (75) is provided, wherein the first coupling means (75) connects the first coupling part (55; 405, 410; 505) with the second coupling part (55; 405, 410; 505), wherein the first coupling means (75) is formed to provide a second restoring force (F _R2 ) to reinforce the first restoring force (F _R1 ).

10. Torque transmission device (10; 200; 300; 400; 500; 600) according to claim 9, wherein the first coupling means (75) comprises at least one elastic element, preferably a spring element.

1 1 . Torque transmission device (10; 200; 300; 400; 500; 600) according to claim 9 or 10, characterized in that the first coupling means (75) is arranged in the circumferential direction between the coupling parts (55; 405, 410; 505).

12. Torque transmission device (10; 200; 300; 400; 500; 600) according to one of claims 1 to 1 1, characterized in that a second coupling means (201, 321) is provided, wherein the second coupling means (201, 321) between the input part (20) and the output part (25) is arranged and the input part (20) is coupled to the output part (25) for torque transmission between the input part (20) and the output part (25).

13. Torque transmission device (10; 200; 300; 400; 500; 600) according to one of claims 1 to 12, characterized in that a guide means (81) is provided, the guide means (81) being connected to the input part (20) or with Output part (25) is connected, wherein the guide means (81) is designed to guide the first coupling part (55; 405, 410; 505) in the radial direction and to transmit torque between the input part (20) or output part (25) and the coupling element (50) to provide.

14. Torque transmission device (10; 200; 300; 400; 500; 600) according to claim 13, characterized in that the guide means (81) comprises at least one guide element (440), at least one guide roller (445) and at least one guide sleeve (435). , wherein the guide roller (445) is arranged between the guide sleeve (435) and the guide element (445), the guide sleeve (435) being connected to at least the first coupling part (55; 405; 410; 505), the guide element (445 ) is connected to the input part (20) or to the output part (25), the guide element (445) and the guide sleeve (435) advantageously extending in the radial direction.