DE102017005244A1 - Torque transmission device and drive train with such a torque transmission device - Google Patents

Abstract

The present invention relates to a torque transmission device (8) for the drive train of a motor vehicle with a torsional vibration damper (30) comprising a primary element (32) and a secondary element (54) which are rotationally elastically coupled to one another, a tertiary element (62) and a coupling device ( 64) for selectively transmitting torque between the secondary element (54) and the tertiary element (62) having a Zugmittelgetrieberad (90) of a Zugmittelgetriebes (80)), via which the tertiary element (62) with an electric machine (82) is in rotary driving connection, wherein at least one silencing means (156; 162; 174; 176; 178) is attached to the traction means gear (90) and / or formed as part of the traction means gear (90). Moreover, the present invention relates to a drive train (2) with such a torque transmission device (8).

Description

The present invention relates to a torque transmission device for the drive train of a motor vehicle.

From practice, drive trains for motor vehicles are known in which a torque transmission device described in more detail below between the drive unit and a transmission is arranged. The torque transmitting device has a torsional vibration damper. The torsional vibration damper consists essentially of a primary element and a secondary element, which are torsionally coupled to each other. In addition, the torque transmission device has a tertiary element and a coupling device for selectively transmitting torque between the secondary element and the tertiary element. The tertiary element further comprises a Zugmittelgetrieberad a traction mechanism, via which the tertiary element is in rotary driving connection with an electric machine to provide by means of the torque transmission device, a drive train for a hybrid vehicle.

In the described torque-transmitting device, particularly in the coupling region between the primary and secondary elements of the torsional vibration damper and in the region of the coupling device, a strong vibration excitation, and thus noise, may occur. Thus, there is the disadvantage in the known torque transmitting devices that they tend to increased noise.

It is therefore an object of the present invention to develop a torque transmission device of the generic type such that, on the one hand, it has a particularly simple and compact, and thus space-saving, construction, and on the other hand, it can operate with particularly low noise. In addition, the present invention has the object to provide a drive train for a motor vehicle, in particular for a hybrid vehicle, having such an advantageous torque transmission device.

This object is achieved by the features specified in the patent claims 1 and 10, respectively. Advantageous embodiments of the invention are the subject of the dependent claims.

The torque transmission device according to the invention is designed for the drive train of a motor vehicle, in particular for the drive train of a hybrid vehicle. Thus, the torque-transmitting device has a torsional vibration damper with a primary element and a secondary element, which are rotationally coupled to one another. The primary element may also be referred to as the input side of the torsional vibration damper, while the secondary element may also be referred to as the output side of the torsional vibration damper. In this case, within the drive train, the primary element or the input side would be acted upon by the torque of the drive unit of the motor vehicle, for example the internal combustion engine, optionally by means of a flywheel or another intermediate component. In addition, the torque transmission device has a tertiary element arranged in the torque transmission path behind the secondary element, wherein furthermore a coupling device is provided for selectively transmitting torque between the secondary element and the tertiary element. For example, the coupling device can be designed as a separating clutch, wherein the coupling device is preferably a multi-plate clutch, particularly preferably a normally closed multi-plate clutch. In addition, the tertiary element has a traction mechanism gear of a traction mechanism, wherein the traction mechanism can be attached to the tertiary element or formed integrally with the tertiary element. The Zugmittelgetrieberad is preferably a Kettengetrieberad, while the traction mechanism is designed as a sprocket. About the Zugmittelgetrieberad the traction mechanism is the tertiary element with an electric machine in rotary driving connection, wherein the electric machine can be operated preferably under the realization of a drive train for a hybrid vehicle as a generator and motor. In order not only to achieve a particularly compact design of the torque transmission device, but also to effectively prevent the noise during operation, at least one silencer is attached to the Zugmittelgetrieberad and / or the at least one silencing means is formed as part of the Zugmittelgetrieberades. It has been found that the vibration excitations occurring in the region of the coupling between the primary element and the secondary element and in the region of the coupling device can be effectively counteracted in a space-saving manner by attaching the sound damping means to the traction gear or / and its construction as part of the traction gear, without necessarily further Noise or vibration damping measures are required, so that a simple design and low-noise torque transmission device is created.

In a preferred embodiment of the torque transmission device according to the invention, the sound damping means is made of a softer and / or more elastic material than the Zugmittelgetrieberad. It has been found to be advantageous if the soundproofing means made of plastic, optionally made of rubber. Alternatively or additionally, the Zugmittelgetrieberad is made of metal or metal sheet.

In order to suppress the noise particularly effectively, the sound damping means is arranged in a further preferred embodiment of the torque transmission device according to the invention on at least one radial portion of the Zugmittelgetrieberades, fastened or supported.

According to a particularly preferred embodiment of the torque transmission device according to the invention two opposing radial sections of the Zugmittelgetrieberades with the interposition of the silencer or two mutually opposite silencer means interposition of a radial section of the Zugmittelgetrieberades to achieve, especially in planar support, a particularly strong sound-damping effect. In this embodiment, as well as in the embodiment described above, it is also possible to speak of a sandwich-type construction of the traction mechanism gear at least in the region of the or the sound damping means and of the radial section or sections.

In principle, the sound damping means can be arranged, fastened or supported on the traction mechanism in various ways. In an advantageous embodiment of the torque transmission device according to the invention, the at least one sound damping means is clamped, vulcanized or glued to the respective radial section of the Zugmittelgetrieberades.

In a further preferred embodiment of the torque transmission device according to the invention, the traction mechanism gear has an outer radial section and an inner radial section which is separate from the outer radial section and which are rotationally engaged with one another via the at least one silencing means. As a result, an impedance jump is achieved, which allows a particularly safe sound attenuation, especially when it is the softer and / or more elastic material of the silencer to plastic, optionally rubber.

In a further advantageous embodiment of the torque transmission device according to the invention, which is based on the embodiment described above, the sound damping means is preferably an axially flexible plate which rotatably connects the outer and inner radial portion with each other. It has been found that the flexible plate, which can also be designed as a so-called flexplate, on the one hand enables safe torque transmission between the outer and inner radial sections and on the other hand contributes to soundproofing. In this embodiment, two or more flexible plates can be used, which connect the outer and inner radial portion of Zugmittelgetrieberades rotation with each other. In this embodiment, it is also preferable if the flexible plate is thinner or / and more flexible than the outer and / or inner radial section. Also, it is preferred in this embodiment, when the flexible plate is formed separately from the outer and / or inner radial portion and, for example, positively and / or non-positively connected to the outer and / or inner radial portion to connect them rotationally fixed to each other. In the case of two or more flexible plates, it is preferable that the total thickness of both or all the flexible plates is made smaller than the thickness of the outer and / or inner radial sections. Also, it has been found in the use of two flexible plates advantageous if they are spaced from each other and / or not adjacent to each other with the outer and / or inner radial section, preferably creating a, optionally in the axial direction, intermediate space.

In a particularly advantageous embodiment of the torque transmission device according to the invention the outer and inner radial portion of the Zugmittelgetrieberades within a rotational angle range are rotatable relative to each other, in which the outer and inner radial portion exclusively indirectly via the at least one silencing means in rotary driving connection, while the outer and inner radial portion outside the rotation angle range or directly alone with each other in rotary driving connection. As a result, smaller torques can be transmitted only via the silencer between the outer and inner radial section, while larger torques can be transmitted directly between the outer and inner radial section to ensure safe torque transmission and nevertheless to achieve a relatively good sound attenuation by at least one silencer.

Based on the embodiment described above, the outer and Inner radial section in a further advantageous embodiment of the torque transmission device according to the invention playful interlocking teeth, which are supported or supported directly against each other outside the rotation angle range. Within the above-mentioned rotation angle range, the mutual support or torque transmission can take place exclusively indirectly via the at least one sound damping means, wherein the at least one sound damping means can act or be arranged, for example, between the teeth of the outer and inner radial sections.

In principle, the Zugmittelgetrieberad have any form, but the Zugmittelgetrieberad is formed in a further advantageous embodiment of the torque transmission device according to the invention as a sprocket, so that the traction mechanism can also be referred to as a chain transmission. Thanks to the sprocket or the chain transmission, the torque can be transmitted particularly securely between the electric machine and the tertiary element of the torque transmission device. Any vibration excitation in the region of the contact between the chain and the sprocket is already counteracted by the sound damping means on the Zugmittelgetrieberad, so that in principle no further measures for soundproofing are required to provide a low-noise torque transmitting device.

In a further advantageous embodiment of the torque transmission device according to the invention, a clutch actuating device is provided for actuating the clutch device. The clutch actuation device is preferably a hydraulically operable clutch actuation device. Thus, the clutch actuator may for example be formed by a piston-cylinder arrangement whose output member is formed by the piston of the piston-cylinder assembly.

According to a further advantageous embodiment of the torque transmission device according to the invention, the clutch actuating device is arranged on the side facing away from the coupling device of the primary element. As a result, although the force of the clutch actuator on the primary element must be transmitted past the coupling device, said arrangement allows a particularly compact construction of the torque transmitting device and a good accessibility of the clutch actuator for the purpose of operating or controlling the same. Thus, for example, a hydraulic clutch actuating device, optionally in the form of the piston-cylinder arrangement, can be supplied particularly quickly and easily with the corresponding hydraulic fluid, optionally via the adjacent housing of an internal combustion engine.

In order to further simplify the structure of the torque transmission device and to avoid the formation of a fluid pressure in particular in a hydraulic clutch actuator within the corresponding pressure chamber of the cylinder, the clutch actuator is fixed. Thus, the clutch actuator may for example be arranged on a fixed housing, it may be advantageous in this case, when the clutch actuator is detachably mounted on said housing, such as a housing of an internal combustion engine. Alternatively, however, the clutch actuator may also be partially integral with said stationary housing. For example, the cylinders of a clutch actuator in the form of a piston-cylinder arrangement could be formed integrally with the stationary housing.

In a further particularly preferred embodiment of the torque transmission device according to the invention, the clutch actuating device interacts with the clutch device via a force transmission device in order to be able to actuate the clutch device, in particular in the case of an arrangement of the clutch actuating device on the side of the primary element facing away from the clutch device. For this purpose, the power transmission device extends through at least one recess in the primary element. In this case, it is preferable if the force transmission device extends through at least two or more recesses in the primary element, wherein the recesses are preferably formed like a window. Depending on the variant of the secondary element, it may also be advantageous if the force transmission device also extends through at least one recess in the secondary element in order to avoid both primary and secondary elements in the most direct way possible. Here, too, it is advantageous if at least two or more recesses are provided in the secondary element, through which the power transmission device can extend in order to be able to actuate the clutch device via the power transmission device. Moreover, it is preferred if the force transmission device extends in the axial direction through correspondingly axially formed recesses in the primary element, optionally also the secondary element, to ensure a secure To ensure power transmission through the power transmission device.

In a particularly advantageous embodiment of the torque transmission device according to the invention, the power transmission device comprises a first power transmission element extending through the at least one recess in the primary element and a second power transmission element formed separately from the first power transmission element and supportable or supported on the first power transmission element. This has the advantage that only relatively small recesses in the primary element must be provided for passing the first power transmission element, especially since the relative rotation of the secondary element or tertiary element relative to the primary element need not be taken into account in the design of the recesses. Consequently, this also creates a particularly strong or stable primary element of the torsional vibration damper, while also a relatively direct power transmission from the clutch actuating device via the power transmission device to the coupling device is possible. In this embodiment, it is also preferred if said second power transmission element extends through the aforementioned at least one recess in the secondary element, wherein due to the separation of the first power transmission element and the second power transmission element, the recesses in the secondary element can be made relatively small, especially Relative rotation between primary element and secondary element can be disregarded. This not only simplifies the production of the torsional vibration damper, but also a particularly stable secondary element of the torsional vibration damper is created here.

In a further advantageous embodiment of the torque transmission device according to the invention, the coupling device is a multi-plate clutch. The multi-plate clutch is preferably a normally closed or / and wet-running multi-disc clutch.

In a further preferred embodiment of the torque transmission device according to the invention, an output side of the multi-plate clutch forming the clutch device, optionally a plate carrier or outer plate carrier, and the tertiary element, optionally the Zugmittelgetrieberad, a common support portion for radially supporting the output side of the multi-plate clutch and the tertiary element. In this case, it is preferable if the common support section extends substantially in the radial direction and is particularly preferably fastened radially on the inside to a support hub.

In a further advantageous embodiment of the torque transmission device according to the invention, the output side of the multi-plate clutch and the tertiary element are formed integrally with each other. Alternatively, however, the initially separate output side of the multi-plate clutch may also have been fastened to the tertiary element, possibly by material bonding by welding, but also non-positively and / or positively.

In a further advantageous embodiment of the torque transmission device according to the invention, an input side of the multi-plate clutch, optionally a disk carrier or inner disk carrier, arranged on the secondary element or fixed or formed integrally with the secondary element.

In a further preferred embodiment of the torque transmission device according to the invention, a torsional vibration damper is arranged on the primary element, the secondary element or the tertiary element, optionally the Zugmittelgetrieberad, in order to avoid any torsional vibrations even more effectively than by the torsional vibration damper alone. The torsional vibration damper has in this case preferably at least one relative to the primary element, secondary element or tertiary element, optionally Zugmittelgetrieberad, movable or rotatable inertial mass portion, which itself is not arranged in the torque transmission path of the drive train or the torque transmission device. The at least one inertial mass portion may also be associated with a return device, such as a spring device.

The drive train according to the invention for a motor vehicle has a drive unit, preferably an internal combustion engine, and a torque transmission device of the type according to the invention arranged in the torque transmission path between the drive unit and a transmission.

• 1 eine schematische Darstellung einer Ausführungsform eines Antriebsstrangs mit einer Drehmomentübertragungsvorrichtung,
• 2 eine teilweise Seitenansicht der Drehmomentübertragungsvorrichtung aus 1 in detaillierter und geschnittener Darstellung,
• 3 den Ausschnitt A von 2 in einer Ausführungsvariante der Drehmomentübertragungsvorrichtung,
• 4 den Ausschnitt B von 2 in einer ersten Ausführungsvariante,
• 5 den Ausschnitt B von 2 in einer zweiten Ausführungsvariante,
• 6 den Ausschnitt B von 2 in einer dritten Ausführungsvariante,
• 7 den Ausschnitt C von 2 in einer Ausführungsvariante und
• 8 den Ausschnitt C von 7 in einer Vorderansicht.

The invention is explained in more detail below with reference to exemplary embodiments with reference to the accompanying drawings. Show it:

• 1 1 is a schematic representation of an embodiment of a drive train with a torque transmission device;
• 2 a partial side view of the torque transmitting device 1 in detailed and cut representation,
• 3 the section A of 2 in a variant of the torque transmission device,
• 4 the section B of 2 in a first embodiment,
• 5 the section B of 2 in a second embodiment,
• 6 the section B of 2 in a third embodiment,
• 7 the section C of 2 in a variant embodiment and
• 8th the section C of 7 in a front view.

1 shows a schematic representation of a drive train 2 for a motor vehicle, more specifically for a hybrid vehicle. The powertrain 2 has a drive unit 4 in the form of an internal combustion engine. The exit side 6 the drive unit 4 is with a torque transmitting device 8th coupled, on their construction later in more detail with reference to 2 to be received. An exit side 10 the torque transmission device 8th is on the other hand a Flexplate 12 with a component following in the torque transmission path 14 , For example, a further coupling device, a torque converter and / or a transmission, connected, so that there is a rotary driving connection.

2 shows the aforementioned torque transmission device 8th in detail. In the figure, the opposite axial directions 16 . 18 , the opposite radial directions 20 . 22 and the opposite circumferential directions 24 . 26 indicated by corresponding arrows, the circumferential directions 24 . 26 can also be referred to as directions of rotation and the axis of rotation 28 the torque transmission device 8th in 2 is indicated.

The torque transmission device 8th has a torsional vibration damper 30 on. The torsional vibration damper 30 has an input-side primary element 32 on. The primary element 32 is in the radial direction 22 inside over a first radial section 34 with the exit side 6 the drive unit 4 , For example, the crankshaft end, rotatably connected. For this purpose, in the first radial section 34 several in the circumferential direction 24 . 26 spaced mounting holes 36 provided, extending in the axial direction 16 . 18 through the first radial section 34 extend and into the fasteners 38 , here in the form of screws, are inserted to the primary element 32 at the exit side 6 the drive unit 4 to fix.

The first radial section 34 extends in the radial direction 20 outwards to an axial section 40 wherein in the first radial section 34 several in the circumferential direction 24 . 26 spaced-apart recesses 42 are provided, will be discussed in more detail later. The recesses mentioned 42 extend in the axial direction 16 . 18 through the first radial section 34 of the primary element 32 , The axial section 40 extends from the radial direction 20 outwardly facing end of the first radial section 34 in the axial direction 16 to a second radial section 44 that continues in the radial direction 20 extends to the outside. The axial section 40 forms one in the radial direction 20 outwardly facing primary element side sliding surface 46 from that of a secondary element-side sliding surface 48 at the later described in more detail secondary element of the torsional vibration damper 30 assigned.

That in the radial direction 20 outer end of the second radial section 44 surrounds a recording room 50 of the torsional vibration damper 30 in the axial directions 16 . 18 as well as in the radial direction 20 to the outside, the receiving space 50 a substantially in the circumferential direction 24 . 26 is circumferential recording space. The recording room 50 serves to receive a spring device 52 , which may be, for example, multiple coil springs. The spring device 52 serves the torsionally elastic coupling of the primary element 32 with a secondary element 54 of the torsional vibration damper 30 ,

The secondary element 54 has a first radial section 56 on, moving in the radial direction 20 out into the recording room 50 and in the radial direction 22 inwardly to an axial section 58 of the secondary element 54 extends. The axial section 58 extends from the first radial section 56 in the axial direction 18 , wherein the axial section 58 at least partially in the radial direction 22 inwardly via the secondary element side sliding surface 48 on the primary element-side sliding surface 46 is supported. Here is therefore a radial bearing between the secondary element 54 and primary element 32 provided, which will be discussed in more detail later. To the in the axial direction 18 pointing end of the axial section 58 closes a second radial section 60 on, starting from the axial section 58 further in the radial direction 22 extends inwards.

In addition, the torque transmission device 8th a tertiary element 62 on, wherein a coupling device 64 for selectively transmitting torque between the secondary element 54 and the tertiary element 62 is provided. The coupling device 64 is as Multi-disc clutch with a disc pack 66 formed from outer and inner plates. This is in the illustrated embodiment is a normally closed and wet-running multi-plate clutch. The coupling device 64 has a substantially tubular inlet side 68 in the form of an inner disk carrier, wherein the input side 68 essentially from the axial section 58 of the secondary element 54 is formed and the axial section 58 For this purpose, a corresponding rotational drive contour for the inner disk of the disk pack 66 having. It can be the input side 68 forming axial section 58 integral with the first radial section 56 and / or integral with the second radial section 60 of the secondary element 54 be formed, but it is also a two- or multi-part design possible. In addition, the coupling device 64 a substantially tubular exit side 70 on, extending in the axial direction 16 . 18 extends and as an outer disk carrier of the coupling device 64 is trained. For this purpose, the output side 70 the coupling device 64 a corresponding rotational drive contour for achieving a rotational drive between the output side 70 and the outer disks of the disk pack 66 on. The exit side 70 extends in the axial direction 18 up to the tertiary element 62 with which the output side 70 rotatably connected, the output side 70 either integral with the tertiary element 62 can be trained, as in 2 is indicated, or subsequently to the tertiary element 62 can be fixed, like this in 3 is hinted that the section A of 2 in an embodiment variant shows. In this embodiment, the output side 70 non-positively and / or positively on the tertiary element 62 fastened, for example by means of rivets or screws. Alternatively, however, the attachment can also be made materially, for example by welding.

The tertiary element 62 extends substantially in the radial directions 20 . 22 starting from the point of attachment to the exit side 70 the coupling device 64 , This is how the tertiary element extends 62 starting from the in the axial direction 18 pointing end of the output side 70 the coupling device 64 in the radial direction 22 in a support section 72 inside up to a support hub 74 , The support section 72 thus forms a common support section 72 for radial support of both the output side 70 the coupling device 64 as well as the tertiary element 62 , due to the common support section 72 a particularly compact design with regard to the axial length of the torque transmission device 8th can be achieved. In addition, the tertiary element extends 62 starting from the in the axial direction 18 pointing end of the output side 70 the coupling device 64 in another radial section 76 in the radial direction 20 to the outside, the radial section 76 at its in the radial direction 20 outward pointing end a gearing 78 which will be discussed in more detail below.

The tertiary element 62 is about that in 1 shown traction mechanism 80 such with an electric machine 82 connected to that the tertiary element 62 with the electric machine 82 is in rotary driving connection. How out 1 Obviously, is the electric machine 82 paraxial to the drive train 2 arranged. The traction mechanism 80 is formed in the illustrated embodiment as a chain transmission, so that this is a traction means 84 in the form of a chain 86 having. The chain 86 encloses on the one hand a Zugmittelgetrieberad 88 the electric machine 82 and on the other hand a Zugmittelgetrieberad 90 that is the tertiary element 62 forms or with the tertiary element 62 is in rotary driving connection. In the latter case, the Zugmittelgetrieberad 90 for example, at the tertiary element 62 be attached. In the illustrated embodiment according to 2 is the tertiary element 62 however, from the gear wheel 90 formed or formed integrally with this. Due to the fact that the traction mechanism 80 formed in the illustrated embodiment as a chain transmission, are also the Zugmittelgetrieberäder 88 . 90 designed as sprockets, the aforementioned toothing 78 at the tertiary element 62 or the Zugmittelgetrieberad 90 in the chain 86 intervenes. The electric machine 82 is arranged such that these change the tension of the traction means 84 in the form of the chain 86 is adjustable. More specifically, the distance between the axis of rotation 28 and the axis of the electric machine 82 be changed, the electric machine 82 can then be locked while maintaining the set distance. On further clamping means is preferably omitted.

In addition, is off 1 It can be seen that at least one further vehicle component 92 over the traction means 84 in the form of the chain 86 is driven or driven. For this purpose, the other vehicle component 92 a corresponding input wheel 94 on, which is also designed as a sprocket and in the traction means 84 in the form of the chain 86 intervenes. For the other vehicle component 92 it is preferably a water pump, an air conditioning pump and / or a pump for a power steering of the motor vehicle.

The tertiary element 62 or the Zugmittelgetrieberad 90 is over its support hub 74 with the help of appropriate radial bearings 96 in the radial direction 20 . 22 at the exit side 6 the drive unit 4 and the primary element 32 of the torsional vibration damper 30 supported, with the support hub 74 further with an exit side 10 the torque transmission device 8th is in rotary driving connection, wherein the output side 10 , which is designed here as an output hub, releasably on the support hub 74 is attached, here by means of a spline 98 , The exit side 10 is rotationally fixed with the substantially in the radial direction 20 . 22 extending flexplate 12 connected, so that - as well as from both 1 and 2 apparent - the output side 10 the torque transmission device 8th over the flexplate 12 with the component following in the torque transmission path 14 is in rotary driving connection or can be brought. How out 2 As can be seen, the further component is 14 via a circlip 100 in the axial directions 16 . 18 at the flexplate 12 set, allowing for a costly screwing of the flexplate 12 with the following component 14 can be waived. How out 2 As can be seen, the flexplate points 12 for this purpose at its in the radial direction 20 outwardly projecting end protruding approaches 102 on, extending in the axial direction 18 extend and in the circumferential direction 24 . 26 spaced apart from each other. The connector 104 the following component 14 points, however, in the radial direction 20 protruding approaches 106 on that between the protruding lugs 104 can be pushed to achieve a positive rotational drive connection. The axial securing of the connector 104 at the flexplate 12 on the other hand takes place via the already mentioned circlip 100 ,

How out 1 and 2 can be seen, are the torsional vibration damper 30 , the coupling device 64 , the tertiary element 62 or the Zugmittelgetrieberad 90 and also the traction means 84 in the form of the chain 86 in a common wet room 106 arranged. This wet room 106 is in the axial direction 16 in particular of a housing 108 the drive unit 4 and in the axial direction 18 from a housing cover 110 limited, where - as in 1 shown - also the Zugmittelgetrieberad 88 the electric machine 82 and the input wheel 94 the other vehicle component 92 inside this wet room 106 are arranged.

The torque transmission device 8th also has a clutch actuator 114 for actuating the coupling device 64 on. The clutch actuator 114 is on the clutch device 64 opposite side of the primary element 32 of the torsional vibration damper 30 arranged. In other words, the clutch actuator 114 on the in the axial direction 16 pointing side of the primary element 32 and the coupling device 64 on the in the axial direction 18 pointing side of the primary element 32 arranged. In the clutch actuator 114 it is a hydraulically driven clutch actuator in the form of a piston-cylinder assembly, wherein the - here annular formed - actuating piston in the axial direction 16 . 18 slidably disposed in the cylinder and the actuating piston below also as an output member 116 the clutch actuator 114 referred to as. The clutch actuator 114 is fixedly formed, in the present example on the fixed housing 108 arranged or fixed, it may be advantageous if the clutch actuator 114 detachable on the fixed housing 110 is arranged. Alternatively, however, at least the cylinder of the clutch actuator 114 integral or partially integral with the housing 108 be educated.

The clutch actuator 114 does not work directly over its output link 116 with the coupling device 64 together, it is rather a power transmission device 118 provided, via which the clutch actuator 114 with the coupling device 64 interacts. This, in this case two-part, power transmission device 118 extends in the axial direction 16 . 18 through the recesses 42 in the primary element 32 and also by recesses 120 in the second radial section 60 of the secondary element 54 , The recesses 120 are in the circumferential direction 24 . 26 spaced apart in the second radial section 60 of the secondary element 54 arranged and extend in the axial direction 16 . 18 through it.

As already indicated above, the power transmission device 118 formed at least in two parts. Thus, the power transmission device 118 a first power transmission element 122 on that through the recesses 42 in the primary element 32 extends. The first power transmission element 122 is separate or separate from a second power transmission element 124 formed in the axial direction 16 on the first power transmission element 122 is supported or supported by the recesses 120 in the second radial section 60 of the secondary element 54 extends.

The first power transmission element 122 has a circumferential direction 24 . 26 extending annular section 126 on, in the axial direction 18 pointing side of the primary element 32 is arranged, wherein at the annular portion 126 in the axial direction 16 protruding support fingers 128 are arranged, each with the achievement of a rotational driving connection with the primary element 32 through one of the recesses 42 on the in the axial direction 16 facing side of the primary element 32 extend. The support fingers are aligned 128 in the axial direction 16 With the output member 116 the clutch actuator 114 , So is the first power transmission element 122 floating in the axial direction 16 . 18 on the primary element 32 stored. Also the second power transmission element 124 has a circumferential direction 24 . 26 extending annular section 130 and at the annular portion 130 arranged, in the axial direction 16 extending support fingers 132 on, resulting in the provision of a rotary driving connection with the secondary element 54 through the recesses 120 in the second radial section 60 of the secondary element 54 in the axial direction 16 extend so that the annular section 130 on the in the axial direction 18 facing side of the secondary element 54 is arranged while the support fingers 132 each through the individual recesses 120 on the in the axial direction 16 facing side of the secondary element 54 extend to there at the annular portion 126 of the first power transmission element 122 be supported or supported. How out 2 As can be seen, the annular portion extends 130 of the second power transmission element 124 further in the radial direction 20 over the the entrance side 68 the coupling device 64 forming axial section 58 of the secondary element 54 out there as a pressure plate for the disk pack 66 the coupling device 64 to act.

Out 2 is also apparent that in the axial direction 16 . 18 between the first power transmission element 122 or in the axial direction 16 pointing ends of the support fingers 128 on the one hand and on the first power transmission element 122 supportable or supported output member 116 the clutch actuator 114 on the other hand a wear-inhibiting and / or friction-reducing device 134 is arranged, the relative rotation between the first power transmission element 122 opposite the output member 116 the clutch actuator 114 , preferably also in the circumferential direction 24 . 26 is fixed and thus not rotatable, takes into account. In this case, the wear-inhibiting and / or friction-reducing device 134 either on the first power transmission element 122 or at the output member 116 be fixed, the first-mentioned variant is realized by way of example in the illustrated embodiment. Also, the anti-wear and / or friction reducing device 134 formed in the illustrated embodiment of a sliding lining whose material is selected such that the wear and the friction in the region between the first power transmission element 122 and the output member 116 the clutch actuator 114 is reduced. Correspondingly, a wear-inhibiting and / or friction-reducing device is also suitable 136 in the axial direction 16 . 18 between the first power transmission element 122 and the second power transmission element 124 arranged, which should also be a sliding coating in this case, either on the support fingers 132 of the second power transmission element 124 or the annular portion 126 of the first power transmission element 122 can be attached. At the device 136 However, it could alternatively also be a wear-reducing or / and friction-increasing device 136 , For example, a friction lining act.

As already indicated above, it is the coupling device 64 around a normally closed multi-disc clutch. For this purpose, a spring device 138 - Here in the form of a plate spring - to close the clutch device 64 provided if not by the clutch actuator 114 is pressed or opened. The named spring device 138 acts between the second radial section 60 of the secondary element 54 on the one hand and the disk pack 66 the coupling device 64 on the other hand. In other words, the spring device 138 in the axial direction 18 at the second radial section 60 and in the axial direction 16 on the disk pack 66 the coupling device 64 supportable or supported. However, the support is not done directly. Rather, one is releasable on the second radial section 60 attached support ring 140 provided on which the spring device 138 in the axial direction 18 is supportable or supported, while the support of the spring means 138 on the disk pack 66 the coupling device 64 via the aforementioned second power transmission element 124 takes place, which thus - as already indicated above - also against the disk set 66 forms compressible printing plate. In addition, the disc pack 66 in the axial direction 16 at the first radial section 56 of the secondary element 54 supportable, with a purpose in the axial direction for this purpose 18 projecting support projection 142 at the first radial section 56 of the secondary element 54 is provided.

At the primary element 32 , the secondary element 54 or / and the tertiary element 62 or the Zugmittelgetrieberad 90 Furthermore, a torsional vibration damper is arranged, as in the illustrated embodiment by way of example with reference to a torsional vibration damper 144 at the tertiary element 62 or the Zugmittelgetrieberad 90 is indicated. In any case, such a torsional vibration damper would 144 at least one relative to the primary element 32 , the secondary element 54 or - as shown here - the tertiary element 62 or the Zugmittelgetrieberad 90 movable or in the circumferential direction 24 . 26 around the axis of rotation 28 rotatable inertial mass part 146 having such an inertial mass portion 146 also one, possibly resilient, return device may be associated with, as known in the art, but not in 2 is shown.

As already indicated above, the primary element is 32 over the mounting holes 36 and by means of the fastening means 38 at the exit side 6 the drive unit 4 attachable or attached. In order to simplify assembly and disassembly, are in the tertiary element 62 or the Zugmittelgetrieberad 90 more precisely in the common support section 72 the same, several mounting holes provided, extending in the axial direction 16 . 18 through the said support section 72 extend and at least with some of the mounting holes 36 in the primary element 32 are arranged in alignment. The said mounting holes can not only pass the fastening means 38 but rather also the associated tool for actuating the fastening means 38 serve. However, around the support section 72 not to weaken too much through the mounting holes, the number of mounting holes is less than the number of mounting holes 36 , Nevertheless, the accessibility of all mounting holes 36 or fasteners 38 in the axial direction 16 to ensure through the mounting holes is at least one of the mounting holes by turning the tertiary element 62 or the Zugmittelgetrieberades 90 relative to the primary element 32 successively with at least two mounting holes 36 can be brought into alignment. So is a first mounting hole 36 or a first fastening means 38 accessible or reachable in a first relative rotational position via the mounting opening, while in the second relative rotational position, a different or second mounting opening 36 and a second attachment means 38 accessible or accessible via the same mounting opening.

Another feature of the torque transmitting device 8th is that the coupling device 64 or their disc pack 66 in the radial direction 20 . 22 with the spring device 52 of the torsional vibration damper 30 is arranged nested. This has the advantage of a smaller axial length.

Hereinafter, further features of the torque transmitting device 8th and their operation with reference to the 1 and 2 described in more detail.

Is the coupling device 64 closed or this is not on the clutch actuator 114 actuated, then one of the drive unit 4 generated torque on the output side 6 , the primary element 32 , the spring device 52 , the secondary element 54 , the coupling device 64 and the tertiary element 62 or the Zugmittelgetrieberad 90 on the output side 10 the torque transmission device 8th transfer. This causes the torsional vibration damper 30 a damping of the drive unit 4 originating torsional vibrations, including the torsional vibration damper 144 contributes to the eradication of torsional vibrations. About the traction mechanism 80 , so the Zugmittelgetrieberad 90 and the traction means 84 in the form of the chain 86 will also be the at least one other vehicle component 92 and the Zugmittelgetrieberad 88 the electric machine 82 driven in generator mode, the electric machine 82 however, can also be operated as a motor to the drive unit 4 to support in the sense of a boost function. The output member 116 or the actuating piston of the clutch actuator 114 is in the in 2 shown starting position, ie in the axial direction 16 , reset so that preferably no contact between the output member 116 and the first power transmission element 122 consists. Also the first power transmission element 122 is designed accordingly that such a contact between the first power transmission element 122 and the output member 116 omitted. To reset the output member 116 this is a spring device 148 assigned, which is exemplified here by an annular wave spring, extending in the axial direction 18 on a detachable on the housing of the clutch actuator 114 attached support ring 150 and in the opposite axial direction 16 at the output member 116 supported. When the clutch device is closed 64 becomes a closed power flow over the spring device 138 , the second power transmission element 124 , the disc pack 66 , the first radial section 56 , the axial section 58 , the second radial section 60 and the support ring 140 achieved, in turn, the spring device 138 is supported.

Should the powertrain 2 only via the electric machine operated as a motor 82 be driven, so must the coupling device 64 be opened. For this purpose, the hydraulically operated clutch actuator 114 or the output member 116 in the form of the actuating piston associated pressure chamber subjected to hydraulic pressure, so that the output member 116 against the restoring force of the spring device 148 in the axial direction 18 is moved. In the course of this contacted the output member 116 the wear-resistant and / or friction-reducing device 134 - Here, the sliding coating - on the first power transmission element 122 , which consequently also in the axial direction 18 is moved. The first power transmission element 122 also pushes over the wear-inhibiting and / or friction-reducing device 136 against the second power transmission element 124 as a result, contrary to the Restoring force of the spring device 138 in the axial direction 18 is moved. This has the consequence that the second power transmission element 124 , equally as a pressure plate for the disk pack 66 serves, no longer against the disk pack 66 is pressed, so that the coupling device 64 is opened.

Because in the axial direction 18 acting actuating force of the clutch actuator 114 over the first power transmission element 122 , the second power transmission element 124 , the spring device 138 and the support ring 140 also on the second radial section 60 of the secondary element 54 acts, becomes the second radial section 60 of the secondary element 54 also in the axial direction 18 urged, wherein the second radial section 60 of the secondary element 54 in the axial direction 18 over a circlip 150 on the primary element 32 is supported or supported, thereby further reducing the friction between the secondary element 54 and the primary element 32 elevated.

By the electric machine 82 in engine operation can by means of the traction mechanism 80 the exit side 10 the torque transmission device 8th are driven, wherein the at least one further vehicle component 92 over the traction mechanism 80 through the electric machine 82 can be driven during engine operation.

As mentioned earlier, the primary element is 32 and the secondary element 54 by a spring device 52 torsionally coupled with each other in the recording room 50 of the primary element 32 is arranged. The recording room 50 is in the radial direction 20 outward and in the axial directions 16 . 18 through the primary element 32 limited. This is the primary element 32 in a tertiary element 62 or gear wheel 90 in the axial direction 18 facing, in the radial direction 20 . 22 extending boundary section 152 on, in which several in the circumferential direction 24 . 26 spaced-apart, window-like openings 154 are provided. Thus, the limiting section 152 on the one hand its function for holding the spring device 52 be fair while on the at least one opening 154 the coolant and / or lubricant, preferably oil, from the receiving space 50 specifically the tertiary element 62 or traction gear 90 , thus the traction mechanism and the traction means 84 , can be supplied. This not only causes improved lubrication, but also a quick removal of coolant or / and lubricant.

In the above-described operation of the torque transmission device 8th It can come at different points of the same to increased vibrational excitations, which ultimately lead to a greater noise. This occurs in particular in the area of interaction between the spring device 52 on the one hand and the primary element 32 and the secondary element 54 on the other hand to a vibration excitation by the operation of the torsional vibration damper 30 , In addition, it also comes in the field of coupling device 64 to a vibration excitation, in particular in the areas of interaction between the input side 68 and the inner disks of the disk pack 66 as well as the output side 70 and the outer disks of the disk pack 66 , Also the traction mechanism 80 in the form of a chain gear leads to a vibration excitation, which could be accompanied by a greater noise, the vibration excitation here in particular in the interaction between the traction means 84 in the form of the chain 86 and the Zugmittelgetrieberad 90 or its toothing 78 is to be feared.

In order to counteract a noise due to the vibration excitation in said areas, without having to take targeted action in said areas of vibration excitation measures, at least one silencing means on the traction means 90 attached or / and the silencer is as part of the Zugmittelgetrieberades 90 formed as described below with reference to the 4 to 8th will be described, the fragmentary different embodiments of the torque transmission device 8th to 2 demonstrate. Due to the fact that already a silencer on the Zugmittelgetrieberad 90 Moreover, a noise development due to the vibration excitations in the said areas relatively effectively prevents, is also a torque transmission device 8th created, which has a simple and compact structure.

4 shows the section B of 2 in a first embodiment. More specifically, the detail B at least partially shows the aforementioned support portion 72 the Zugmittelgetrieberades 90 which is in the radial direction 22 . 20 between the connection point of the output side 70 the coupling device 64 and the support hub 74 extends. The silencer 156 is flat on at least one radial section 158 . 160 the Zugmittelgetrieberades 90 arranged, fastened or supported. More specifically, the Zugmittelgetrieberad 90 in the embodiment according to 4 two each other in the axial direction 16 . 18 opposite radial sections 158 . 160 on, with the silencer 156 in the axial direction 16 . 18 between the two radial sections 158 . 160 is arranged. One can here also of a sandwich-like arrangement of the at least one sound damping means 156 and the at least one radial section 158 . 160 the Zugmittelgetrieberades 90 speak. The silencer 156 can, for example, between the two radial sections 158 . 160 be trapped. Alternatively or additionally, the silencing means 156 with at least one of the two radial sections 158 . 160 , preferably with both radial sections 158 . 160 , glued or vulcanized to this.

One of the embodiment according to 4 similar variant is in 5 shown. In contrast to the embodiment according to 4 However, they are two mutually opposed silencer 156 and 162 provided, between which the radial section 158 the Zugmittelgetrieberades 90 is arranged. Here are the two silencer 156 . 162 in turn flat on the radial section 158 the Zugmittelgetrieberades 90 arranged, fastened or supported. Also in this embodiment, the silencing means 156 . 162 to the radial section 158 clamped, vulcanized and / or glued. In 5 is an example of a clamping of the silencer 156 . 162 to the opposite sides of the radial section 158 shown, with the silencer 156 by means of a holding part or retaining plate 164 against in the axial direction 16 pointing side of the radial section 158 is pressed while the silencer 162 by means of another holding part 166 , which may also be formed as a holding plate, in the axial direction 16 against in the axial direction 18 pointing side of the radial section 158 is pressed. The two holding parts 164 . 166 are via a connection device 168 with the radial section 158 or / and the other holding part 166 respectively. 164 connected, wherein the connecting device 168 is formed here by way of example of a riveted joint.

The silencer 156 . 162 in the embodiments according to the 4 and 5 For example, they may be formed as a covering or as a sheet. That's how the silencers can work 156 . 162 for example in the circumferential direction 24 . 26 continuous and thus ring-shaped around the axis of rotation 28 extend. However, it is also conceivable, several in the circumferential direction 24 . 26 mutually spaced silencer 156 . 162 provided. Moreover, the silencers are 156 . 162 in the embodiments according to the 4 and 5 essentially on or in the common support section 72 provided, which is particularly advantageous in terms of the sound damping properties, in principle, the silencing means 156 . 162 but also in the radial direction 20 outwards to the radial section 76 extend or be provided there. Moreover, the silencers are 156 . 162 made of a softer and / or more elastic material than the Zugmittelgetrieberad 90 or its radial sections 158 . 160 manufactured, which in a corresponding manner also for the later described embodiments according to the 6 to 8th applies. So are the silencers 156 . 162 preferably made of plastic, particularly preferably rubber, while the Zugmittelgetrieberad 90 can be made for example of metal or metal sheet.

In the following with reference to the 6 as well as 7 and 8 described in more detail variants is the Zugmittelgetrieberad 90 in the support section 72 in an outer radial section 170 and one of the outer radial portion 170 separately formed inner radial section 172 educated. Here are the outer radial section 170 and the inner radial section 172 over silencer 174 and 176 respectively. 178 brought together in rotational driving connection.

In the embodiment according to 6 are the silencers 174 . 176 each from one in the axial direction 16 . 18 formed flexible plate, the two soundproofing means 174 . 176 in the form of the flexible plates, the outer and inner radial section 170 . 172 rotatably connect with each other. How out 6 can be seen, the two, here essentially annular or annular disk-shaped, flexible plates in the axial direction 16 . 18 arranged so that there is a free space between them 180 arises. The individual soundproofing agents 174 . 176 are each thinner and / or more flexible than the outer and / or inner radial section 170 . 172 educated. Also, the two soundproofing means 174 . 176 each separated from the outer and inner radial section 170 . 172 formed so that it does not form an integral part of the outer and / or inner radial portion 170 . 172 form. The two silencers 174 . 176 in the form of the flexible plates are rather via a connecting device 182 . 184 non-positively and / or positively with the outer and inner radial section 170 . 172 connected to achieve the aforementioned rotationally fixed connection.

In the embodiment according to the 7 and 8th are several silencers 178 between the outer and inner radial sections 170 . 172 arranged, wherein the outer and inner radial section 170 . 172 within a rotation angle range about the rotation axis 28 are rotatable relative to each other, in which the outer and inner radial section 170 . 172 only indirectly via the silencer 178 in rotary driving connection stand. At the silencers 178 These may again be rubber or plastic parts. In addition, the outer radial section 170 and the inner radial section 172 an internal or external toothing 186 respectively. 188 on, in the radial direction 20 . 22 playfully meshed with each other, with the silencer 178 between the tooth flanks of the teeth of the inner and outer teeth 186 . 188 are arranged. In this way, the outer radial section 170 and the inner radial section 172 be rotated relative to each other within said rotation angle range, without the two radial sections 170 . 172 are directly in rotational drive connection with each other. However, if the relative rotation is so great that it lies outside of the stated rotation angle range, then the radial sections are 170 . 172 about their teeth 186 . 188 can be supported or supported directly against one another in order to be able to transmit particularly high torques.

LIST OF REFERENCE NUMBERS

2

powertrain

4

drive unit

6

output side

8th

The torque transfer device

10

output side

12

flexplate

14

component

16

axial direction

18

axial direction

20

radial direction

22

radial direction

24

circumferentially

26

circumferentially

28

axis of rotation

30

torsional vibration damper

32

primary element

34

first radial section

36

mounting holes

38

fastener

40

axial

42

recesses

44

second radial section

46

primary element-side sliding surface

48

secondary element-side sliding surface

50

accommodation space

52

spring means

54

secondary element

56

first radial section

58

axial

60

second radial section

62

tertiary element

64

coupling device

66

disk pack

68

input side

70

output side

72

support section

74

support hub

76

radial section

78

gearing

80

traction drives

82

electric machine

84

traction means

86

Chain

88

Zugmittelgetrieberad

90

Zugmittelgetrieberad

92

further vehicle component

94

input gear

96

radial bearings

98

plug-in device

100

circlip

102

protruding approaches

104

joint

106

protruding approaches

108

common wet room

110

casing

112

housing cover

114

Clutch actuator

116

output member

118

Power transmission device

120

recesses

122

first power transmission element

124

second power transmission element

126

annular section

128

support fingers

130

annular section

132

support fingers

134

wear-resistant / friction-reducing device

136

wear-resistant / friction-reducing device

138

spring means

140

support ring

142

supporting projection

144

A torsional vibration damper

146

Inertial mass part

148

spring means

150

support ring

152

limiting portion

154

openings

156

Silencing means

158

radial section

160

radial section

162

Silencing means

164

holding part

166

holding part

168

connecting device

170

outer radial section

172

inner radial section

174

Silencing means

176

Silencing means

178

Silencing means

180

free space

182

connecting device

184

connecting device

186

internal gearing

188

external teeth

Claims (10)

A torque transmitting device (8) for the powertrain of a motor vehicle having a torsional vibration damper (30) comprising a primary element (32) and a secondary element (54) torsionally coupled to each other, a tertiary element (62), and a torque transfer optional coupling device (64) between the secondary element (54) and the tertiary element (62), which has a traction mechanism gear (90) of a traction mechanism (80) via which the tertiary element (62) is rotationally engaged with an electrical machine (82), wherein at least one silencing means ( 156; 162; 174; 176; 178) is attached to the traction mechanism gear (90) and / or is formed as part of the traction mechanism gear (90). Torque transmission device (8) according to Claim 1 characterized in that the sound attenuating means (156; 162; 174; 176; 178) is made of a softer and / or more elastic material than the traction means gear (90), the silencing means (156; 162; 174; 176; 178) preferably made of plastic, particularly preferably rubber, and / or the Zugmittelgetrieberad (90) is made of metal or metal sheet. Torque transmission device (8) according to one of Claims 1 or 2 characterized in that the sound damping means (156; 162; 174; 176; 178) is arranged, fastened or supported flat on at least one radial section (158; 160) of the traction gear (90), preferably two opposing radial sections (158,160 ) of the Zugmittelgetrieberades (90) with the interposition of the silencer (156) or two mutually opposed silencer means (156, 162) with the interposition of a radial section (158) of the Zugmittelgetrieberades (90) are provided and the silencer (156, 162) particularly preferably to the respective Radial section (158, 160) is clamped, vulcanized or glued. Torque transmission device (8) according to one of Claims 1 or 2 characterized in that said traction means gear (90) has an outer radial portion (170) and an inner radial portion (172) separate from said outer radial portion (170) which are rotationally engaged with each other via said at least one silencing means (174; 176; 178) wherein the sound damping means (174; 176) is preferably a flexible plate (16, 18) in the axial direction, which rotatably connects the outer and inner radial sections (170, 172), and the flexible plate is more preferably thinner and / or more flexible than the outer and / or inner radial section (170, 172) or / and separated from the outer and / or inner radial section (170, 172) is formed. Torque transmission device (8) according to Claim 4 characterized in that the outer and inner radial sections (170, 172) are rotatable relative to one another within a range of rotational angles in which the outer and inner radial sections (170, 172) are only indirectly indirectly rotationally engaged via the at least one muffler (178), and The outer and inner radial sections (170, 172) preferably have play-engaging interlocking toothings (186, 188) which can be supported or supported directly against one another outside the rotation angle range. Torque transmission device (8) according to one of the preceding claims, characterized in that the Zugmittelgetrieberad (90) as a sprocket and / or the traction mechanism (80) is designed as a chain transmission. Torque transmission device (8) according to any one of the preceding claims, characterized in that a clutch actuator (114) is provided for actuating the clutch device (64), preferably arranged on the coupling device (64) side facing away from the primary element (32) and / or fixed formed and / or on a fixed housing (110), optionally detachable, arranged and / or hydraulically driven or / and via a power transmission device (118) with the coupling device (64) cooperating through at least one recess in the primary element (32 optionally, also at least one recess in the secondary element (54), wherein the force transmission device (118) particularly preferably a first force transmission element (122) extending through the at least one recess in the primary element (32), and one of the first power transmission element (122) separated au a second power transmission member (124) adapted to be supported on the first power transmission member (122) and optionally extending through the at least one recess in the secondary member (54). Torque transmission device (8) according to one of the preceding claims, characterized in that the coupling device (64) is a multi-plate clutch, preferably a normally closed and / or wet multi-plate clutch, wherein an output side (70) of the multi-plate clutch, optionally a disc carrier or outer disc carrier, and the Tertiary element (62), optionally the Zugmittelgetrieberad (90), more preferably a common support portion (72) for radial support and / or integrally formed with each other and / or an input side (68) of the multi-plate clutch, optionally a plate carrier or inner disc carrier, particularly preferred is arranged on the secondary element (54) or formed integrally therewith. Torque transmission device (8) according to one of the preceding claims, characterized in that on the primary element (32), the secondary element (54) or the tertiary element (62), optionally the Zugmittelgetrieberad (90), a torsional vibration damper (144) is arranged, wherein the Torsional vibration damper (144) preferably at least one relative to the primary element (32), secondary element (54) or tertiary element (62), optionally Zugmittelgetrieberad (90), movable or rotatable inertial mass portion (146). Drive train (2) for a motor vehicle with a drive unit (4), preferably an internal combustion engine, and a torque transmission device (8) according to one of the preceding claims arranged in the torque transmission path between the drive unit (4) and a transmission.

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