CN107002816B - Rotary vibration damper and drive train for a motor vehicle with the same - Google Patents

Abstract

The present invention relates to a kind of torsional vibration damper (2), including can be around the substrate (18) that rotation axis (16) rotate and can be relative to substrate (18) and the inertia mass part (20) rotated against the reset force of resetting apparatus (36), wherein resetting apparatus (36) has for generating the spring unit (38) that power is arranged.The pivotable lever element (40) that there is resetting apparatus (36) at least one can pivot around pivotal point (46), the reset force of inertia mass part (20) is influenced via the reset force junction (44) of lever element (40) by generating, via the lever element (40), power, which is arranged, from the setting power junction (42) of lever element (40) can be transferred to inertia mass part (20).The invention further relates to a kind of transmission systems (110) for the motor vehicles with such torsional vibration damper (2).

Description

Rotary vibration damper and motor vehicle with the same drive system

The invention relates to a rotary vibration damper comprising a base part rotatable around a rotation axis and an inertial mass part rotatable relative to the base part against a reset force of a resetting device, wherein the resetting device has a device for generating a setting force the spring unit. The invention further relates to a drive train for a motor vehicle with such a rotational vibration damper.

DE 199 07 216 C1 discloses a rotational vibration damper having a base part in the form of a support plate rotatable about an axis of rotation. The inertia body is arranged on the support plate, and it can rotate against the reset force of the reset device relative to the base part. The return device has a flexible spring, which extends radially and is arranged on the one hand on the base part and on the other hand on the inertia part. If the mass of inertia is rotated relative to the base part, the flexible spring serves to generate a setting force that directly affects the mass of inertia, whereby the setting force likewise represents a return force that affects the mass of inertia. The radial support of the inertial body on the support plate takes place on the radially outward side of the support plate, wherein the bearing shell is arranged on the support plate for this purpose, the inertial body is supported radially on the bearing shell, and along the circumference direction guide. Existing torsional vibration dampers have the disadvantage that the resetting device requires a relatively large and space-intensive flexible spring, especially if the resetting device has to be arranged on the inertia body on the one hand and on the support plate on the other hand. As already mentioned, the necessity of supporting the flexible springs arranged on the one hand on the support plate and on the other hand on the mass of inertia also leads to a largely predefined arrangement of the flexible springs on the rotational vibration sensor. A flexible arrangement of the flexible spring is therefore not possible in said type of torsional vibration damper. Furthermore, supporting the inertial body radially outward on the support plate by means of mounting shells on the support plate requires a more complex construction of the torsional vibration damper, wherein also increased wear in the region of the support plate supporting the inertial body.

Starting from the prior art, the main problem underlying the present invention is to create a torsional vibration damper with a simplified and installation-space-saving structure, in which a particularly flexible arrangement of the spring units is possible. Furthermore, the main problem underlying the invention is to create a drive train for a motor vehicle with such an advantageous torsional vibration damper.

This problem is solved by the features listed in claim 1 or claim 12 . Advantageous embodiments of the invention are the subject of the dependent claims.

The torsional vibration damper according to the invention has a base part which is rotatable about an axis of rotation. For example, the base element can be formed by a base plate or a support plate extending substantially in the radial direction, if necessary a double base plate or a double support plate. Furthermore, the torsional vibration damper has an inertial mass that is rotatable about the axis of rotation relative to the base part and counter to the restoring force of the restoring device. The restoring device has a spring unit for generating the setting force, wherein the spring unit can have, for example, one or more spring elements. Furthermore, the reset device has a lever element which is pivotable about a pivot point. Thus, the pivotable lever element may, for example, be pivoted indirectly via a pivot point or directly on the base. It is thus preferred that the lever element [runs] on a plane determined by the radial direction of the torsional vibration damper and is thus pivotable about an axis extending from a pivot point in the direction of the torsional vibration damper axis. Furthermore, the pivotable lever element is preferably a bending-resistant or rigid lever element. The lever element is arranged between the spring unit on one side and the inertial mass on the other side, so that the setting force generated by the spring unit is transferred from the setting force joint on the lever element to the inertial mass and generates a return force , which influences the inertial mass via the restoring force joint of the lever element. This has the advantage that the spring unit of the return device generating the setting force does not have to directly affect the inertial mass, but can in fact be arranged at another point on the base part of the rotational vibration damper, in this way, during the rotational vibration damping A space-saving and flexible spring unit arrangement on the machine is possible. On the other hand, thanks to the lever element, a lever ratio can be set or specified, based on which the reset force acting on the inertial mass is greater or smaller than the setting force generated by the spring unit of the reset device. Thus, by specifying the lever ratio without requiring a particularly stiff spring unit for generating the setting force, the stiffness of the reset device can be increased in a targeted manner. It should therefore be noted initially that the spring unit has only a low spring stiffness and can therefore be formed in a particularly space-saving installation, wherein the flexible arrangement of the spring unit on the base part of the torsional vibration damper is also feasible.

In a preferred embodiment of the torsional vibration damper according to the invention, the lever element is supported or can be supported on the base on one side via a support rail on the base or on the lever element and on the other side via a The base member is supported or supportable on a rotatable roller unit that rolls on a support track on the member. Preferably, a support in substantially radial direction is achieved here. Due to the roller unit, imperceptible and small wear is achieved in this embodiment when the lever element pivots about the pivot point, wherein an equally stable support of the lever element on the base part is still ensured. In this embodiment, support rails may be provided which are connected to the roller unit, eg in the area of the pivot point. Alternatively or additionally, support rails connected to the roller units can be provided in the region where the force joints are provided, as will be explained in more detail below.

Therefore, in a particularly preferred embodiment of the torsional vibration damper according to the invention, it is provided that the force joint is movable along the support rail by rotating the inertial mass relative to the base part. Thus, in this embodiment, the support rail or the roller unit interacts with the roller unit or the support rail at the setting force joint. In this way, a particularly simple construction can be achieved, which also ensures low wear between the lever element and the base part when the above-mentioned lever element pivots.

Basically, the above-mentioned roller unit can be formed by a simple wheel or a simple roller, one side of which is rotatably arranged but fixed on the lever element or the base, and the other side can roll on the support rail of the base or lever exchange. In another preferred embodiment of the torsional vibration damper according to the invention, the roller unit is substantially formed by a roller bearing, so that the above-mentioned advantages are achieved and an equally compact construction is achieved. Therefore, the roller bearing may preferably have an inner race, an outer race and rolling elements arranged between the inner race and the outer race. Therefore, the inner race is preferably fixed and arranged on the lever element or the base, and if necessary arranged not to rotate, while the outer race can rest on the support track of the base or lever element due to the rolling elements between the inner and outer races. Scroll up. The roller bearings are preferably needle bearings, so that a loadable and equally compact construction of the roller unit is achieved.

In an advantageous embodiment of the torsional vibration damper according to the invention, the spring unit has at least one helical spring for generating a setting force. The helical spring may, for example, be a helical compression spring and/or a helical extension spring, arranged in the recess of the base.

In a further advantageous embodiment of the torsional vibration damper according to the invention, at least one displaceable support base plate is arranged on the helical springs in the recess on which at least one helical spring is arranged, wherein the helical spring, via the facing helical The support base on the support side of the recess of the spring is supported or can be supported outwards in the radial direction. Thus, the support base plate has the advantage that the coil springs are not directly supported or can be supported on the support side of the recess, thereby minimizing potential frictional wear of the coil springs or the support side of the recess. Wear can also be reduced by a suitable choice of material for the support base, wherein the support base is preferably made of plastic, while the helical spring and/or the support side of the recess is particularly preferably formed from metal or steel. The roller unit can also act in an advantageous manner between the support base plate and the support side of the recess, thereby significantly reducing the wear between the support base plate and the support side of the recess, further advantageous embodiments of the rotational vibration damper according to the invention are exactly This situation. Accordingly, corresponding rotatable rollers that can roll on the support floor may be provided, for example, on the support floor itself.

Basically, the support base can only extend in the inner space of the helical spring surrounded by the coiled part of the helical spring, thereby influencing the support on the support side of the recess in this way. In a particularly advantageous embodiment of the torsional vibration damper according to the invention, the support base extends optionally or additionally between the periphery of the coil spring and the support side of the recess, thereby effecting a particularly stable support. The coil spring can also be supported or can be supported on the support side of the recess by placing the support base or at least one support base part in an intermediate position between the coil spring periphery and the support side of the recess.

In a further preferred embodiment of the torsional vibration damper according to the invention, the support base is arranged between the helical spring periphery and the support side of the recess, the other side of the helical spring on the support base on one side and the base on the other side. A gap is created in the area of the helical spring between the support bases or support points between the outer periphery of the helical spring and the support side of the recess. The support point is therefore preferably designated as an end-side support point for the helical spring on the base part, wherein (if necessary) this can also be realized by the support base. The advantage of this embodiment is that the helical spring can be bent laterally towards its direction of extension by the centrifugal force at higher rotational speeds of the torsional vibration damper without the helical spring coming into contact with the support side of the recess, in particular the helical spring Can be bent or extended into the aforementioned gap. The gap or its dimensions are therefore preferably selected such that no contact occurs between the coil spring and the support side of the recess if the rotational vibration damper is driven at maximum rotational speed within the drive train.

The above-mentioned support base can be arranged at substantially all positions in the recess, so that the coil spring is supported by the support base on the support side of the recess. However, in other preferred embodiments of the torsional vibration damper according to the invention, the support base is arranged or formed in such a way that the setting force of the spring unit can be transferred via the support base to the setting force joint of the lever. Thus, the supporting base can be formed, for example, as an end base for the helical spring, which interacts with the end side of the helical spring to transmit the setting force of the spring unit to the setting force joint. However, as mentioned above, other support bases are also conceivable which do not transmit the setting force of the spring unit to the setting force engagement point, but only serve to support the coil spring on the support side of the recess or the above-mentioned support point.

In a further particularly preferred embodiment of the torsional vibration damper according to the invention, the support base plate and the lever element are supported or can be supported on the base part via roller units and support rails. As mentioned above, the support base plate and the lever element are supported or can be supported on the base part via roller units and support rails, preferably in the region where the force joint is provided. On the one hand, this embodiment has the advantage that wear is reduced by the support of the roller unit and the support rail, resulting in less frictional wear on the support base and ensuring simple displaceability of the support base. On the other hand, the above-mentioned second function, the additional support of the support base plate on the base, is assigned to the current roller units and support rails, so that no additional roller units or support rails are required at least in this area, which is extremely important. The structure of the rotary vibration damper is greatly simplified.

In a further advantageous embodiment of the torsional vibration damper according to the invention, the spring unit has two helical springs located on the lever element and interacting with each other. Thus, for example, two helical compression springs or two helical tension springs may be provided. However, it is equally possible to form both helical springs as helical tension and compression springs.

If the spring unit has two helical springs for the setting force, in a further preferred embodiment of the torsional vibration damper according to the invention, the above-mentioned support base forms the support base for one helical spring and the support base for the other helical spring. Spring support base plate. In this way, not only is the number of parts reduced, but the correct interaction of the two helical springs generating the setting force is ensured, especially when the supporting base is a supporting base which transmits the setting force to the setting force joint of the lever element. In this embodiment it is further preferred if the supporting base is formed in one piece, wherein the supporting base is preferably made of plastic as mentioned above.

In a further advantageous embodiment of the torsional vibration damper according to the invention, the center of mass of the lever element is arranged at the level of the arranging force joint or further outwards in the radial direction than the arranging force joint.

In a further preferred embodiment of the torsional vibration damper according to the invention, the center of mass of the lever element is located further outwards in the radial direction than the pivot point, this example exploits the advantages in particular (but not exclusively) and will be discussed below Describe in detail where the return force joint retains its setting relative to the lever element. This has the advantage that the lever element, based only on centrifugal force, tends to return to its original pivoted position. Therefore, it is more advantageous that the center of mass of the lever element is arranged at least at the level of the restoring force engagement point in the radial direction, and preferably further outwards in the radial direction than the restoring force engagement point , so as to further amplify the above-mentioned advantages.

In a further advantageous embodiment of the torsional vibration damper according to the invention, the center of mass of the lever element arranged further outwards (at least in the axial direction) than the pivot point, when viewed in the axial direction, is arranged in a On a common straight line or on a common radial line with the pivot point and/or the restoring force joint and/or the setting force joint. Thus, the listed center of mass of the lever element is preferably arranged at the starting position of the lever element or the inertial mass on a common radial line with the pivot point and/or the restoring force joint and/or the setting force joint. In this way, the centrifugal force has no or little effect on the lever element if it is in its starting position.

In a further preferred embodiment of the torsional vibration damper according to the invention, the lever element has a preferably elongated lever part and a lever mass. The lever mass is fixed on the lever part such that the center of mass of the lever element is further outwards in the radial direction than the center of mass of the lever part. Accordingly, the lever mass is preferably formed inherently with the lever part or separately from the lever part. The inherent formation of the lever mass and the lever part has the advantage that production is simplified, in particular that the lever mass can be produced together during the production of the lever part. In contrast, separating the lever mass from the lever part has the advantage that it can be applied to already produced lever parts, so that the center of mass of the entire lever element can be positioned in a targeted manner by applying the lever mass to the lever part. With regard to the lever mass formed separately from the lever part, it is more preferred that it is detachably or non-detachably fixed to the lever part via fastening points. In this case, it is also preferred that the lever mass is fastenable at at least two different fastening points and/or can be fixedly positioned along the lever part, so that the center of mass of the lever element can subsequently be influenced.

In a further particularly preferred embodiment of the torsional vibration damper according to the invention, in order to be able to support or mount the inertial mass on the base part in the radial direction, particularly firmly and without excessive frictional losses, the inertial mass The piece is supported or can be supported on the base piece in radial direction by at least three rollers.

In a further preferred embodiment of the torsional vibration damper according to the invention, the roller is rotationally fixed on one side on the inertial mass or the base part and on the other side can roll on the base part or the inertial mass. For example, the fixation of the rollers on the inertial mass or base can be achieved via the inertial mass or base, where the rollers are carried by the roller brackets when the inertial mass or base rotates relative to the base or inertial mass, but which can Roll on base or inertial mass. Therefore, it is preferred that the rollers are arranged fixed with respect to the circumferential direction on the inertial mass or base.

In other preferred embodiments of the torsional vibration damper according to the invention, the aforementioned rollers can roll on roller rails on the base or inertial mass, wherein the roller rails are arranged outside the circumference in the radial direction with a radius of 80% (90% if necessary) of the maximum radius of the base part. In this way, it is ensured that the roller can be arranged further outward in the radial direction, and it is not required to be supported on a longer roller support in the radial direction, so that the structure of the rotary vibration damper can be simplified and its weight can be reduced. reduce. It is therefore particularly advantageous if the roller track is arranged on the largest radius of the base part, while the rollers are preferably arranged on the inertial mass. Conversely, if the rollers are arranged on the base part, it is preferred that the roller rails arranged on the inertial mass are arranged radially outside the base part and thus at a radius greater than the maximum radius of the base part.

As mentioned above, via the rollers and thus the mounting of the inertial mass on the base, a stable and wear-free support of the inertial mass on the base in the radial direction can be achieved. In a further advantageous embodiment of the rotational vibration damper according to the invention, the inertial mass is further supported or further supportable in at least one axial direction, preferably in two axial directions, via at least one roller. Thus, in this embodiment, a dual function is assigned to the rollers, which on the one hand generate support in the radial direction and on the other hand in the axial direction between the inertial mass and the base, so that the structure can Further simplification, in particular no further or additional means for supporting the inertial mass in the axial direction on the base part are required.

In a further advantageous embodiment of the torsional vibration damper according to the invention, the outer side of at least one roller fixed to the inertial mass or the base is provided with a peripheral groove into which the base or inertial mass extends. This embodiment has the advantage that the peripheral grooves in the roll can be easily produced in the environment in which the roll is produced, so that the production of the torsional vibration damper as a whole is simplified.

In other preferred embodiments of the torsional vibration damper according to the invention, grooves are provided on the base or the inertial mass, and rollers extend into the grooves to produce vibrations in at least one axial direction, preferably in two axial directions. The support for the inertial mass in the direction.

In a further advantageous embodiment of the torsional vibration damper according to the invention, the lever element has a first lever part between the setting force joint and the pivot point and a second lever part between the pivot point and the restoring force joint. A lever portion the length of which can be varied by rotating the inertial mass relative to the base while substantially maintaining the leverage ratio.

In a further advantageous embodiment of the torsional vibration damper according to the invention, by changing the length of the lever part, the pivot point and the return force joint can be moved relative to the lever element, while the return force joint maintains its position relative to the lever element. set up. It has been shown that in this embodiment variant the influence of centrifugal forces on the position of the lever element is reduced at higher rotational speeds of the torsional vibration damper, and that the lever element can be returned to its starting position with relative ease. Furthermore, it is preferred in this embodiment than in the case of the pivot point that the setting force is arranged closer to the axis of rotation in the radial direction. It should also be noted that in this embodiment it is preferred to provide a radial distance between the force joint and the axis of rotation that is smaller than the radial distance between the pivot points and the axis of rotation.

In a further advantageous embodiment of the torsional vibration damper according to the invention, an alternative to the above-described embodiment is shown, by changing the length of the lever part, the pivot point and the return force engagement point can be moved relative to the lever element, while the return force engages The point retains its setting relative to the lever element. This embodiment is advantageous, especially in combination with the above-described embodiment, according to which the center of mass of the lever element is arranged further outwards in the radial direction than the pivot point, preferably at least in the radial direction the restoring force At the level of the joint, it is particularly preferred to be further outward in the radial direction than the restoring force joint, so that the above-mentioned advantages are achieved.

In a further preferred embodiment of the torsional vibration damper according to the invention, the restoring force engagement point can be adjusted by changing the restoring force characteristic curve of the restoring force. Thus, for example, by adjusting the restoring force means, the gradient of the restoring force characteristic curve influencing the restoring force of the inertial mass can be increased or decreased, so that the stiffness of the restoring force means is correspondingly increased or decreased. Thus, a restoring force device that reacts flexibly to operating states in the drive train is created.

In a further preferred embodiment of the torsional vibration damper according to the invention, the lever ratio of the lever element can be varied by varying the restoring force characteristic curve of the restoring force. In this embodiment, it is preferred that the pivot point is adjustable by changing the leverage ratio of the lever element, the position of the pivot point relative to the base being changeable. Thus, for example, the pivot can be arranged to be movable on the base part, wherein a movement of the pivot point relative to the base part in a radial direction or a movement in a radial line is preferred. Furthermore, it is preferred in this embodiment that the pivot point is formed by a protruding protrusion which is adjustable or displaceable on the base part.

In a further particularly advantageous embodiment of the torsional vibration damper according to the invention, the center of mass of the lever element is arranged in at least one setting position of the adjustable pivot point in the radial direction (or irrespective of the setting position of the pivot point) The pivot point is positioned further outwards, thereby achieving the above-mentioned advantage that the center of mass of the lever element is arranged further outwards in the radial direction than the pivot point.

A drive train according to the invention for a motor vehicle has a rotational vibration damper of this type according to the invention, the base part of which is fixed in rotation on a component of the drive train. Thus, the base element can be substantially fixed to any part of the rotationally oscillating transmission system.

In a preferred embodiment of the transmission system according to the invention, the base part of the torsional vibration damper is rotationally fixedly mounted to a component which is the input side of the torsional vibration damper or the dual mass flywheel, the torsional vibration damper or the dual mass flywheel The output side of the clutch, the input side of the clutch, if necessary the input disc carrier or the radial support part of the input disc carrier, the output side of the clutch, the input side of the transmission and/or the output side of the transmission. Therefore, two or more torsional vibration dampers each affecting one of the above-mentioned two points can be provided without any problem in the drive train.

In a particularly preferred embodiment of the transmission system according to the invention, the output side of the clutch device is the output side disc carrier or a radial support part of the output side disc carrier, the base part is rotationally fixedly mounted to the output side of the clutch device, which The engine speed strength of the output side disc carrier or the radial support portion of the output side disc carrier is increased. Therefore, the base member is rotatably fixedly mounted on the output side disc carrier or the radial support portion of the output side disc carrier, and reinforces the output side disc carrier or the radial support portion of the output side disc carrier.

Afterwards, the present invention will be described in more detail by way of exemplary embodiments with reference to the accompanying drawings. As follows:

1 is a front view of an embodiment of a rotational vibration damper with a lever member in a starting position according to the present invention;

Figure 2 is a view of the rotational vibration damper with the lever member pivoted out of the starting position in Figure 1;

Fig. 3 is a partial view of the rotational vibration damper in Figs. 1 and 2 along the line A-A in the modification of the first embodiment;

Fig. 4 is a partial view of the rotational vibration damper in Figs. 1 and 2 along the line A-A in the modification of the second embodiment;

FIG. 5 is a schematic representation of an embodiment of a drive train with at least one torsional vibration damper according to FIGS. 1 to 4 .

1 and 2 show an embodiment of a rotational vibration damper 2 according to the invention. In these figures, the opposite axial directions 4, 6, the opposite radial directions 8, 10 and the opposite circumferential directions 12, 14 of the torsional vibration damper 2 are shown by corresponding arrows, which may also be designated as opposite direction of rotation. The torsional vibration damper 2 has an axis of rotation 16 extending in the axial direction 4 , 6 .

The torsional vibration damper 2 has a base part 18 which is rotatable about an axis of rotation 16 in the circumferential direction 12 , 14 . The base part 18 can be formed, for example, in the shape of a plate or double plate, wherein the base part 18 preferably extends in the plane of the radial directions 8 , 10 , the plane of drawing here. The base part 18 can be rotationally fixedly connected to components within the drive train, for example in the region of the axis of rotation 16 , so as to dampen rotational shocks of the elements. The base 18 is rotatably fixedly mounted to components of the transmission system, which will be described in more detail below with reference to FIG. 5 .

The rotational vibration damper 2 further has an inertial mass 20 , wherein the inertial mass 20 is formed in a ring shape. The inertial mass 20 is supported or can be supported on the base part 18 in the radial direction 8 via at least three rollers 22 . The rollers 22 are thus spaced apart from each other by a uniform distance in the circumferential direction 12 , 14 . In the illustrated embodiment, the roller 22 is fixed to the inertial mass 20 in such a way that it is rotatable with the inertial mass 20 relative to the base 18 in the circumferential direction 12 , 14 . It can thus be stated that the rollers 22 are arranged fixed to the inertial mass 20 in the circumferential direction 12 , 14 . However, the roller 22 is rotatably fixed on the inertial mass 20 . Thus, the rollers 22 are each rotatable about a roller axis 24 extending in the axial direction 4 , 6 . Instead, roller rails 26 are provided on the base part 18 on which the rollers 22 can roll, preferably on their outer sides 28 . The base part 18 has a maximum radius r ₁ , which can be designated as the maximum radius of the base part 18 , where the roller track 26 is arranged outside the circumference 30 in the radial direction 8 , whose radius _r2 is the maximum radius r of the base part 18 80% of ₁ , 90% if necessary. In the illustrated embodiment, the roller track 26 is arranged at the level of the largest radius r ₁ of the base part 18 . In addition, reference is made at this point to the fact that a reverse arrangement is also possible. The rollers 22 are therefore also or additionally rotatably fixed on the base part 18 , while roller rails 26 are arranged on the inertial mass 20 on which the rollers 22 can roll. In this embodiment variant, therefore, the roller track 26 can also be arranged outside the base part 18 at the radial position 8 or outside the circumference of the maximum radius r ₁ .

The inertial mass 20 is further supported or further supportable on the base part 18 via at least one roller 22 in at least one axial direction 4 , 6 , preferably in both axial directions 4 and 6 . Thus, in the first embodiment variant shown in FIG. 3 , the peripheral groove 32 is arranged on the outer side 28 of at least one roller 22 fixed on the inertial mass 20 or the base part 18 in the radial direction 8 Extending into this peripheral groove 32 , a positive locking fixation of the inertial mass 20 on the base part 18 in the axial direction 4 , 6 is achieved. FIG. 3 therefore shows a variant in which the roller 22 is fixed in rotation on the inertial mass 20 , while the roller rail 26 is arranged on the base part 18 . Alternatively or additionally, a groove 34 can be provided on the base part 18 or on the inertial mass 20 , wherein FIG. 4 shows this second embodiment variant. In this second embodiment variant, the rollers 22 extend in the radial direction 10 as in recesses 34 on the base part 18 or the inertial mass 20, wherein FIG. 4 also shows an embodiment in which the rollers 22 are rotatably fixed in the inertia On the mass part 20 , and the roller shaft 26 is arranged on the base part 18 . Reference is made again at this point: the two embodiment variants according to FIGS. 3 and 4 can be used in a similar manner for an arrangement in which the roller 22 is rotationally fixed on the base member 18 and the roller track 26 is arranged on the inertial mass 20 on.

As can be seen from FIG. 1 , the torsional vibration damper 2 furthermore has reset devices 36 which are arranged exactly opposite one another and/or are spaced apart from one another by a uniform distance in the circumferential direction 12 , 14 on the torsional vibration damper 2 . The reset devices 36 are therefore designed to be structurally substantially identical, so that the reset devices 36 can be described below with reference to one of the reset devices 36 , wherein the description applies equally to the other reset devices 36 . Reference is also made to the fact that the torsional vibration damper 2 can of course have three or more reset devices 36 of the type described below, wherein these reset devices 36 are also to be spaced apart from each other by a uniform distance in the circumferential direction 12 , 14 .

The reset device 36 has a spring unit 38 and a pivotable lever element 40 for generating a setting force, whereby the setting of the spring unit 38 affects the inertial mass 20 by generating a restoring force via the restoring force joint 44 of the lever element 40 . Force can be transmitted from the provided force joint 42 of the lever element 40 to the inertial mass 20 . In other words, the inertial mass 20 is rotatable about the axis of rotation 16 in the circumferential direction 12 , 14 relative to the base part 18 against the restoring force of the restoring device 36 .

The lever member 40 is pivotable relative to the base member 18 about a fixed pivot point 46 . Thus, the lever element 40 is pivotable relative to the base part 18 about a pivot axis extending in the axial direction 4 , 6 . Thus, the pivot point 46 may be formed by a protruding protrusion on the base member 18 . The pivot point 46 is displaceable relative to the base part 18 along a displacement path 48 extending straight in the axial direction 8, 10, wherein to form the displacement path 48, for example, for forming the pivot point Corresponding guides to the protruding protrusions at 46 may be provided on the base part 18 . If the pivot point 46 is also formed by such a protruding protrusion on the base part 18, the protrusion preferably extends on a guide body 50 on the lever element 40 in the direction of extension of the lever element 40 in the axial direction 4, 6, And it is formed as an elongated concave part.

The lever element 40 has a first lever portion 52 between the setting force joint point 42 at which the setting force is transmitted from the spring unit 38 to the lever element 40 and the pivot point 46 . Furthermore, the lever element 40 has a second lever part 54 which extends between the pivot point 46 and the restoring force joint 44 , wherein the restoring force caused by the setting force of the spring unit 38 affects the inertial mass via the restoring force joint 44 20. The first lever portion 52 has a length l ₁ and the second lever portion 54 has a length l2. The lever element 40 therefore has a leverage ratio l ₁ /l ₂ , ie l ₁ to l ₂ .

As shown in Figure 2, by rotating the inertial mass 20 about the axis of rotation 16 relative to the base 18, the two lengths _l1 and _l2 can be changed, thus increased or decreased, substantially maintaining the leverage ratio _l1 / _l2 . For this purpose, as shown in the embodiment, on the one hand the pivot point 46 is displaceable relative to the lever element 40 as described above with reference to the protruding protrusions forming the pivot point 46 and the guide body 50 . On the other hand, the restoring force engagement point 44 is displaceable relative to the lever element 40 in the direction of extension of the lever element 40 . The latter is achieved due to the protruding protrusions on the inertial mass 20 forming the restoring force joint 44 being arranged on the guide body 56 in the lever element 40 , wherein the guide body 56 extends like the guide body 50 in the direction of extension of the lever element 40 , and is formed, for example, as an elongated recess on the lever element 40 . Conversely, the setting force joint 42 maintains its setting relative to the lever member 40 when the lever member 40 is pivoted about the pivot point 46 . However, at least the joint 42 may be provided fixed on the lever element 40 with respect to the direction of extension of the lever element 40 . Even though the illustrated embodiment is preferred, alternatively, the pivot point 46 and setting force joint 42 can be formed to be movable relative to the lever member 40 by changing the length l ₁ , l ₂ of the lever portions 52 , 54 for resetting. The force joint 44 maintains its setting relative to the lever element 40 . In this example, the guide body 56 may be assigned to the setting force joint 42 . The support rails and roller units described in detail below can then also be omitted.

The reset device 36 can be adjusted by changing the restoring force characteristic curve which influences the restoring force of the inertial mass 20 . In the illustrated embodiment, the leverage ratio l ₁ /l ₂ of the lever element 40 can be varied for this purpose, since the pivot point 46 can be moved along the aforementioned displacement path 48 relative to the base member 18 stylus diameter. The adjustment or displacement is outward in direction 8 or inward in radial direction 10 and the lever ratio l ₁ /l ₂ of the lever element 40 is changed. For this purpose, corresponding reset means can be provided, which can adjust or displace the pivot point 46 mechanically or hydraulically along the displacement path 48, wherein for the sake of clarity, the representation of the reset means in the figures Can be omitted. In any case, the adjustability of the reset device 36 enables the rotational vibration damper 2 to be flexibly adjusted to the transmission system or The different states of the torsional vibration damper 2 react.

The lever element 40 has an elongated lever part 58 and a lever mass 60 arranged on the lever part 58 . The lever part 58 has a center of mass 62 and the lever mass 60 has a center of mass 64 . The lever mass 60 is therefore arranged on the lever part 58 in such a way that the center of mass 66 of the lever element 40 (composed of the lever part 58 and the lever mass 60 ) is arranged further in the radial direction 8 than the center of mass 62 of the lever part 58 outward position. The lever mass 60 may be integrally formed with the lever member 58 . Alternatively, the lever mass 60 may be formed separately from the lever member 58 so as to be removably or non-removably secured to the lever member 58 via fasteners or fastening points. With respect to the initially separately formed lever mass 60, it is further preferred that the positioning of the lever mass 60 on the lever part 58 is changeable at least in the radial direction 8, 10 or in the direction of extension of the lever part 58, so that the lever element Proper setting of the center of mass 66 of 40 (consisting of lever mass 60 and lever 58).

The center of mass 66 of the lever element 40 is arranged in the radial direction 8, possibly at the level of the setting force joint 42, and possibly further outwards in the radial direction 8 than the setting force joint 42 as shown in FIGS. 1 and 2 position. More precisely, the center of mass 66 is arranged further outwards in the radial direction 8 than the pivot point 46 . Since in the illustrated embodiment the pivot point 46 can be displaced or moved in the radial direction 8, 10 along the displacement path 48 by changing the restoring force characteristic curve, it should be considered that the center of mass 66 of the lever element 40 is arranged as At least at the disposition of the pivot point 46 , further outwards in the radial direction 8 than the pivot point 46 at this disposition. However, it is also preferred that the center of mass 66 of the lever element 40 is arranged further outwards in the radial direction 8 than the pivot point 46 , regardless of the corresponding arrangement of the pivot point 46 . However, it is also possible to define the center of mass 66 of the lever element 40 in such a way that the pivot point 46 in its outermost arrangement position in the radial direction 8 is arranged at the center of mass 66 of the lever element 40 in the radial direction 8 , 10 level. In the illustrated embodiment, not only is the center of mass 66 arranged further outwards in the radial direction 8 than the pivot point 46 , regardless of where the pivot point 46 is located, but the center of mass 66 of the lever element 40 is arranged in the radial direction 8 further outward than the restoring force engagement point 44 , wherein it is also possible to arrange the center of mass 66 of the lever element 40 at the level of the restoring force engagement point 44 in the radial direction 8 , 10 . By using the arrangement of the center of mass 66 of the lever element 40 instead of the above, the influence of the centrifugal force affecting the lever element 40 at higher rotational speeds of the rotary vibration damper 2 can be optimized or changed to achieve that the lever element 40 already tends to Returning to the starting position shown in FIG. 1 , wherein, through the arrangement of the center of mass 66 shown in FIGS. 1 and 2 in the radial direction 8 further outward than the restoring force engagement point 44 , this behavior occurs in a special degree is supported. It can also be seen from FIGS. 1 and 2 that the center of mass 66 of the lever element 40 is arranged on a common line 68 with the pivot point 46 , the restoring force joint 44 and the setting force joint 42 when viewed from the axial directions 4 , 6 , wherein the straight line 68 preferably corresponds to the radial line in the starting position of the lever element 40 according to FIG. 1 . In any instance, the center of mass 66 of the lever member 40 should be disposed on a common line 68 with at least the pivot point 46 and the force setting joint 42 .

The lever element 40 is in the radial direction 8 and in the radial direction 10 on the one hand via at least one of the support rails 70 , 72 on the base part 18 and on the other side via a The rotatable roller unit 74 is supported or can be supported on the base member 18 . More precisely, by rotating the inertial mass 20 , the setting force joint 42 is movable along the support rails 70 , 72 relative to the base 18 . In the example shown, at the setting force joint 42 , the roller unit 74 is rotationally fixed on the lever element 40 . Thus, the roller 74 shown in the embodiment is formed as a roller bearing, preferably a needle bearing, the inner race 76 of which is fixed to the protruding protrusion of the lever element 40 forming the force joint 42, wherein the roller element 78 is arranged Between the inner race 76 and the outer race 80 of the roller bearing, and the outer race 80 can be supported and rolled on the aforementioned support rails 70 , 72 .

A roller unit 74 formed in the form of a roller bearing is arranged on a guide body 82 (here formed as an elongated recess), shown only in dashes as a part 84, wherein the part 84 may be formed inherently with the base part 18 or as a The individual parts are fastened to the base element 18 . The support rail 70 delimits the guide rail 82 outwardly in the radial direction 8 , while the support rail 72 delimits the guide rail 82 inwardly in the radial direction 10 . Due to the roller unit 74, the wear of the area between the lever element 40 on one side and the base part 18 on the other side where the force joint point 42 is provided (which may occur when the lever element 40 pivots or the inertial mass 20 relative to the base Occurs when member 18 rotates) is significantly reduced. It should be noted at this point that the roller unit 74 can also be designed more simply and thus, for example, be formed as a rotatable wheel or a rotatable roller which is or can be supported on corresponding support rails 70 , 72 . It should also be noted that the arrangement shown can also be realized in reverse, so that the guide body 82 comprising the support rails 70 , 72 is arranged on the lever element 40 and the roller unit 74 can be arranged on the base member 18 .

The spring unit 38 of the restoring device 36 has two helical springs 86 , 88 , which are here formed as helical compression springs. The two springs 86 , 88 act against one another on the lever element 40 or on the setting force joint 42 of the lever element 40 . The two helical springs 86 , 88 are thus supported on the one side on support points 90 , 92 on the base part 18 and on the other side at the setting force joint 42 , for example via a support base formed as an end base. . Accordingly, the two coil springs 86 , 88 are respectively arranged in a recess 94 of the base part 18 , wherein the recess 94 for the coil springs 86 , 88 is preferably formed as a continuous recess 94 . The recesses 94 each have a support side 96 facing inwards substantially in the radial direction 10 towards the associated coil spring 86 , 88 . The helical springs 86 , 88 are thus each supported or respectively supportable via a support base 98 (arranged on the support side 96 on the helical springs 86 , 88 facing outward in the radial direction 8 ). It can be drawn from FIGS. 1 and 2 that the support base 98 is formed as an end base for each of the coil springs 86, 88, wherein the support base 98 forms the support base for one coil spring 86 and the other coil spring 86. The supporting base of the spring 88. In the illustrated embodiment, the support base 98 is formed in one piece and is preferably made of plastic.

The support base plate 98 has a central portion 100 arranged between the coil springs 86 , 88 in the direction of extension of the two coil springs 86 , 88 . Furthermore, the support base plate 98 has a first portion 102 connected to the central portion 100 and a second portion 104 connected to the central portion 100, the first portion extending between the periphery of the coil spring 86 and the support side 96, and the second portion extending from the central portion 100. Beginning to extend between the periphery of the coil spring 88 and the support side 96 . In other words, the first portion 102 is disposed between the periphery of the coil spring 86 and the support side 96 , while the second portion 104 is disposed between the periphery of the coil spring 88 and the support side 96 . In the process, the corresponding helical springs 86, 88 in the region of the helical springs 86, 88 between the corresponding supporting side 96 and the supporting points 90, 92 of the supporting base plate 98 on the one side and the helical springs 86, 88 on the other side A gap 106 is created between the outer peripheries of the . Basically, further support bases can be provided in the recesses 94 on the corresponding coil springs 86, 88, wherein in this example a gap 106 can also be formed between the support base 98 on one side and an additional support base on the other side . The gap 106 enables the helical springs 86, 88 to bend outwards in the radial direction 8 into the gap 106 at higher rotational speeds without contact between the corresponding helical springs 86, 88 and the supporting side 96 of the associated recess 94, such that As a result, the helical springs 86, 88 can perform their function unhindered, and wear on the recess 94 and on the corresponding helical springs 86, 88 is avoided.

The setting force of the spring unit 38 formed by the coil springs 86 , 88 is transmitted to the setting force joint 42 via the support base plate 98 . For this purpose, a protrusion on the lever element 40 forming the force joint 42 may, for example, extend through a corresponding recess or opening in the support base plate 98 . Irrespective of the corresponding connection of the support base plate 98 at the setting force joint 42 , the support base plate 98 with the lever element 40 is supported or can be supported on the part 84 of the base part 18 via the roller unit 74 and the support rails 70 , 72 . Furthermore, in the region of the central part 100 , the support base plate 98 is at a distance from the support side 96 or the side of the recess 94 inward in the radial direction 10 , which is passed through a depression on the side of the central section 100 facing the support side 96 108 is shown. Thus, the support base plate 98 is supported on the corresponding support side 96 substantially via the first part 102 , optionally also via parts of the central part 100 , and the second part 104 , optionally also via parts of the central part 100 , while the central part 100 is The support of the support base plate 98 takes place substantially via the roller unit 74 and the support rails 70 , 72 . In this way, support is achieved in each case at three support points spaced apart from one another, which has proven to be advantageous.

FIG. 5 schematically shows a drive train 110 for a motor vehicle, wherein different possibilities for arranging the torsional vibration damper 2 are shown according to FIGS. 1 to 4 . The transmission system 110 has a transmission unit 112, a torsional vibration damper 114 (which may be designated as a dual mass flywheel and follows the transmission unit 112 in the torque flow), a clutch device 116 that follows the torsional vibration damper 114 in the torque flow, and The transmission 118 of the clutch device 116 follows in the torque flow. Thus, the torsional vibration damper 2 (shown in each case by a dashed line in FIG. 5 ) can be fixed in rotation with its base part 18 on the input side of the torsional vibration damper 114 120 , output side 122 of torsional vibration damper 114 , input side 124 of clutch device 116 , output side 126 of clutch device 116 , input side 128 of transmission 118 and/or output side 130 of transmission 118 . A plurality of rotational vibration dampers 2 of the type described above may also be used in the transmission system 110 at the above-listed points in the transmission system 110 . The clutch device 116 is preferably a multi-disc clutch device, wherein the base member 18 of the rotary vibration damper 2 is rotatably mounted and fixed on the input side of the disc carrier on the output side, or the radial support of the disc carrier on the input side or the output side Partially, in this way, in particular, a joint reinforcement between the torsional vibration damper 2 and the disc carrier or a supporting part of the disc carrier can be achieved.

Reference Symbol Table

2 Rotary vibration damper

4 axial direction

6 Axial direction

8 radial direction

10 radial direction

12 Circumferential direction

14 Circumferential direction

16 axis of rotation

18 base parts

20 inertial masses

22 rolls

24 roller axis

26 roller track

28 outside

30 circles

32 peripheral groove

34 grooves

36 Reset device

38 spring unit

40 lever element

42 Setting Force Joints

44 Return force joint

46 pivot points

48 Shift path

50 guides

52 First lever part

54 Second lever part

56 guide

58 lever

60 lever mass

62 centroid

64 Centroid

66 Centroid

68 straight/radial

70 Support rail

72 Support rail

74 roller device

76 inner race

78 Rolling elements

80 outer race

82 guide

84 parts

86 coil spring

88 coil spring

90 support points

92 support points

94 concave

96 Support side

98 Support base plate

100 center section

102 part one

104 part two

106 Gap

108 sunken

110 Driveline

112 drive unit

114 Torsional vibration damper

116 Clutch

118 transmission

120 input side

122 output side

124 input side

126 output side

128 input side

130 output side

l ₁ length

l ₂ Length

r ₁ maximum radius

r ₂ circle radius

Claims (41)

1. A rotary vibration damper (2) comprising a base part (18) rotatable about an axis of rotation (16) and a resetting force rotatable relative to said base part (18) and against a resetting device (36) while rotating the inertial mass (20), wherein the reset device (36) has a spring unit (38) for generating a setting force, wherein the reset device (36) has a pivot point (46) that can rotate around the pivoting at least one lever element (40), via which a setting force is transferable from a setting force joint (42) of said lever element (40) to said inertial mass (20), At the same time the restoring force is generated, which affects the inertial mass ( 20 ) via the restoring force engagement point ( 44 ) of the lever element ( 40 ), characterized in that one side of the lever element ( 40 ) via the The support rail (70; 72) on the base (18) or the lever element (40), and the support rail (70) on the base (18) or the lever element (40) ; 72) A rolling rotatable roller unit (74) is radially supported on said base member (18). 2. Rotational vibration damper (2) according to claim 1, characterized in that the setting force joint (42) can be rotated by rotating the inertial mass (20) relative to the base (18) Instead, it moves along said support rail (70; 72). 3. Rotational vibration damper (2) according to claim 1, characterized in that the roller unit (74) is formed as a roller bearing. 4. Rotational vibration damper (2) according to claim 1, characterized in that the roller unit (74) is formed as a needle bearing. 5. Rotational vibration damper (2) according to claim 1, characterized in that the spring unit (38) has at least one helical spring (86; 88) for generating a setting force, the helical spring ( 86; 88) are arranged in a recess (94) on said base part (18). 6. Rotational vibration damper (2) according to claim 5, characterized in that at least one displaceable support plate (98) is arranged in said recess (94) of said helical spring (86; 88) , via said support base plate (98), said helical springs (86, 88) are supported in radial direction (8) or can be supported in said recess facing one of said helical springs (86; 88) (94) on the support side (96). 7. Rotational vibration damper (2) according to claim 6, characterized in that the support base plate (98) is between the periphery of the coil spring (86, 88) and the support side (96) extend. 8. Rotational vibration damper (2) according to claim 7, characterized in that the helix on the support base plate (98) on one side and the base member (18) on the other side at the same time Other support bases or support points (90, 92) of the spring (86; 88) are generated in the region of the helical spring (86; 88) between the support side (96) and the helical spring (86; 88) between the perimeters of the gap (106). 9. The rotational vibration damper (2) according to claim 5, characterized in that: the setting force of the spring unit (38) can be transmitted to the setting force joint (42) via the support base plate (98) ), and/or the support base (98) and the lever element (40) are supported or can be supported on the base (18) via the roller unit (74) and support rails (70; 72) superior. 10. Rotational vibration damper (2) according to claim 9, characterized in that the support base plate (98) and the lever element (40) are connected via the roller unit (74) and the support track (70; 72 ) is supported or can be supported in the region of said provision force joint ( 42 ). 11. Rotational vibration damper (2) according to claim 5, characterized in that the spring unit (38) has two helical springs (86, 88) situated on the lever element (40) and interacting with each other ). 12. Rotational vibration damper (2) according to claim 11, characterized in that said support base plate (98) forms said support base plate for one said coil spring (86) and for the other said The coil springs (88) support the base plate. 13. The rotational vibration damper (2) according to claim 12, characterized in that the support base plate (98) is formed in one piece. 14. The rotational vibration damper (2) according to claim 13, characterized in that the support base plate (98) is made of plastic. 15. Rotational vibration damper (2) according to claim 1, characterized in that the center of mass (66) of the lever element (40) is arranged in the radial direction (8) at the setting force joint ( 42) or further outward in the radial direction (8) than the setting force joint (42) or further outward in the radial direction (8) than the pivot point (46) where the center of mass (66) of the lever element (40) is arranged when viewed from the axial direction (4, 6) in relation to the pivot point (46) and/or the return force engagement point ( 44) and/or set the common straight line (68) or common radial line of the force joints (42). 16. Rotational vibration damper (2) according to claim 15, characterized in that the center of mass (66) of the lever element (40) is arranged in radial direction (8, 10) in the engagement of the restoring force Point (44) on the level. 17. Rotational vibration damper (2) according to claim 15, characterized in that the center of mass (66) of the lever element (40) is arranged in the radial direction (8) smaller than the return force engagement point ( 44) A more outward position. 18. The rotational vibration damper (2) according to claim 1, characterized in that the lever element (40) has a lever element (58) and a lever mass ( 60), the center of mass (66) of the lever element (40) is arranged to be more outward than the center of mass (62) of the lever member (58) in the radial direction (8). 19. The rotational vibration damper (2) according to claim 18, characterized in that the lever mass (60) is formed inherently or separately from the lever (58). 20. Rotational vibration damper (2) according to claim 19, characterized in that the lever mass (60) formed separately from the lever (58) is detachable or non-removable via a fastening point Removably secured to said lever member (58). 21. Rotational vibration damper (2) according to claim 1, characterized in that the inertial mass (20) can be supported in radial direction (8; 10) via at least three rollers (22) or can be supported on said base (18), roller rails (26) arranged outside the circumference (30) in radial direction (8) with a radius (r ₂ ) of said base (18) 80% of the maximum radius (r ₁ ). 22. Rotational vibration damper (2) according to claim 1, characterized in that the inertial mass (20) can be supported in radial direction (8; 10) via at least three rollers (22) or can be supported on said base (18), roller rails (26) arranged outside the circumference (30) in radial direction (8) with a radius (r ₂ ) of said base (18) 90% of the maximum radius (r ₁ ). 23. The rotational vibration damper (2) according to claim 21 or 22, characterized in that: one side of the roller (22) is rotationally fixed on the inertial mass (20) or the base (18) ), and the other side can roll on the base (18) or the inertial mass (20). 24. The rotational vibration damper (2) according to claim 21 or 22, characterized in that the roller (22) can be a roller on the base member (18) or the inertial mass member (20) Roll on rail (26). 25. The torsional vibration damper (2) according to claim 21, characterized in that the roller track (26) is arranged on the largest radius ( _r1 ) of the base part (18). 26. Rotational vibration damper (2) according to claim 21, characterized in that the inertial mass (20) is further compressed in at least one axial direction (4; 6) via at least one roller (22) Support or further can be supported. 27. Rotational vibration damper (2) according to claim 26, characterized in that the inertial mass (20) is further compressed in both axial directions (4, 6) via at least one roller (22) Support or further can be supported. 28. Rotational vibration damper (2) according to claim 26, characterized in that the peripheral groove (32) is provided on at least one roller fixed to the inertial mass (20) or base (18) (22), the base (18) or the mass (20) extends into the peripheral groove (32), or the groove is set on the base (18) or the In the inertial mass (20), the roller (22) extends into the groove. 29. Rotational vibration damper (2) according to claim 1, characterized in that said lever element (40) has a The first lever part (52) and the second lever part (54) between said pivot point (46) and said return force engagement point (44), the length (l ₁ , l ₂ ) of which can be obtained by Rotation of the inertial mass (20) relative to the base (18) is varied while substantially maintaining the leverage ratio (l ₁ /l ₂ ). 30. Rotational vibration damper (2) according to claim 29, characterized in that by changing the length (l ₁ , l ₂ ) of the lever portion (52, 54), the pivot point ( 46) and said reset force engagement point (44) are movable relative to said lever element (40), while said setting force engagement point (42) maintains its relative arrangement with respect to lever element (40). 31. Rotational vibration damper (2) according to claim 29, characterized in that by changing said length (l ₁ , l ₂ ) of said lever portion (52, 54), said pivot point ( 46) and said setting force engagement point (42) are movable relative to said lever element (40), while said return force engagement point (44) maintains its relative setting relative to lever element (40). 32. The rotational vibration damper (2) according to claim 1, characterized in that the reset device (36) can be adjusted by changing the reset force characteristic curve of the reset force. 33. The rotational vibration damper (2) according to claim 32, characterized in that the leverage ratio (l ₁ /l ₂ ) of the lever element (40) is changeable. 34. Rotational vibration damper (2) according to claim 33, characterized in that said pivot point (46) can be adjusted by changing said lever ratio (l ₁ /l ₂ ) of said lever element (40) ) to adjust. 35. The rotational vibration damper (2) according to claim 32, characterized in that the center of mass (66) of the lever element (40) is arranged at least at the arrangement position of the pivot point (46), Or further outwards in the radial direction (8) than said pivot point (46) regardless of where said pivot point (46) is located. 36. A transmission system (110) for a motor vehicle with a torsional vibration damper (2) according to one of the preceding claims, the base part (18) of which is rotationally fixedly mounted on the transmission system (110) components. 37. The transmission system (110) according to claim 36, characterized in that the component is a torsional vibration damper (114) or the input side (120) of a dual mass flywheel, a torsional vibration damper (114) or a dual mass flywheel The output side (122) of the quality flywheel, the input side (124) of the clutch device (116). 38. The transmission system (110) according to claim 36, characterized in that the components are the input side disc bracket, the output side (126) of the clutch device (116), the input side (128) of the transmission (118) ) and/or the output side (130) of the transmission (118). 39. The transmission system (110) according to claim 36, characterized in that said component is a radial support part of the input side disc bracket. 40. The transmission system (110) according to claim 38, characterized in that: the output side (126) of the clutch device (116) is an output side disc bracket, and the base member (18) rotates It is fixedly installed here, and at the same time increases the engine speed strength of the output side pan bracket. 41. The transmission system (110) according to claim 38, characterized in that: the output side (126) of the clutch device (116) is a radial support part of the disc bracket on the output side, and the base member (18) Rotationally fixedly installed here, while increasing the engine speed strength of the radial support portion of the output side disc bracket.