WO2020244696A1

WO2020244696A1 - Torsional vibration damper and method for balancing a torsional vibration damper

Info

Publication number: WO2020244696A1
Application number: PCT/DE2020/100183
Authority: WO
Inventors: Pascal Strasser; Jean Baptiste Coulibaly
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2019-06-06
Filing date: 2020-03-12
Publication date: 2020-12-10
Also published as: DE102019115350A1

Abstract

A torsional vibration damper, having an input part (102) and an output part (104) with a common rotational axis (106), around which the input part (102) and the output part (104) can be rotated together and can be rotationally offset relative to one another to a limited extent, a spring/damper device which acts between the input part (102) and the output part (104), and at least one rivet (142) which acts as a balancing mass, wherein the at least one rivet (142) is fastened by means of a swage head (146) and a closing head (150) to a first component (144) of the output part (104), characterized in that the closing head (150) of the at least one rivet (142) is arranged at least partially in a depression (156) of a second component (154) of the output part (104), and a method for balancing a torsional vibration damper according to the invention, characterized in that, in one method step, a rivet shank (148) of the at least one rivet (142) is plugged through an opening (158) of the first component (144) of the output part (104), and, in a following method step, a force is applied to the swage head (146) of the at least one rivet (142), with the result that an end of the rivet shank (148), which end faces away from the swage head (146), is pressed against a bottom (170) of the depression (156) of the second component (154) of the output part (104) in such a way that the closing head (150) is configured at that end of the rivet shank (148) which faces away from the swage head (146).

Description

Rotary vibration damper and method for balancing a

Torsional vibration damper

The invention relates to a torsional vibration damper, in particular a dual-mass flywheel, the torsional vibration damper having an input part and an output part with a common axis of rotation about which the input part and the output part are rotatable together and can be rotated to a limited extent relative to one another, one between the input part and the Spring-damper device with at least one mechanical energy store, in particular one of a bow spring, and at least one rivet that acts as a balancing mass, the at least one rivet being fastened to a first component of the output part by means of a setting head and a closing head.

From DE 10 2010 018 942 A1 a split flywheel is known, with an input part with a primary flywheel, which is received on a crankshaft by means of an axially elastic drive connection, and an output part that is limitedly rotatable against the effect of an energy store and an opposite an angular positioning of the crankshaft calibrated position marking, in which the position marking is arranged on the elastic drive connection. An imbalance produced by the position marking is compensated for by means of at least one opening arranged in the drive connection.

From DE 10 2014 218 268 A1 a centrifugal pendulum device for arrangement in the drive train of a motor vehicle is known, with at least two pendulum masses which are arranged on a carrier disk and can execute a relative movement to the carrier disk along a predetermined pendulum path in order to achieve a take a variable distance to the axis of rotation of the carrier disk, the carrier disk having an imbalance which is compensated for in a basic position of the pendulum masses by a corresponding imbalance of the pendulum masses.

A centrifugal pendulum device for arrangement in the drive train of a motor vehicle is known from WO 2015/176721 A1, with at least one pendulum mass which is arranged on a carrier disk and along a predetermined pendulum path can perform a movement relative to the carrier disk in order to take up a variable distance from the axis of rotation of the carrier disk, the carrier disk comprising at least one bore for receiving at least one balancing mass.

A method for balancing a centrifugal pendulum system for a torque transmission device, in particular for a torque transmission device of a vehicle, with the following steps is known from DE 10 2015 206 856 A1:

- Determination of a component center of gravity of the centrifugal pendulum system,

- Marking of the determined component center of gravity,

- Determination of the positions of the main rivet holes, the positions of the main rivet holes forming a geometric shape which has an axis of rotation, and the axis of rotation is placed on the determined component center of gravity, and

- Creation of the main rivet holes at the specified positions.

An arrangement is known from DE 10 2015 225 049 A1, comprising a centrifugal pendulum device and a plate spring sealing membrane, a centrifugal pendulum flange of the centrifugal pendulum device being riveted to the plate spring sealing membrane by means of rivets of a pre-riveting, so that an imbalance of the arrangement and / or the the centrifugal pendulum device is at least partially compensated.

From DE 10 2016 220 911 A1 a centrifugal pendulum device is known, in particular for a torque transmission device, the centrifugal pendulum device having an axis of rotation, a pendulum mass carrier rotatable about the axis of rotation, and at least one pendulum mass displaceably arranged on the pendulum mass carrier along a pendulum track, the Pendulum mass carrier has at least one hole for fastening a balancing mass in order to balance the centrifugal pendulum device. A method for mounting and balancing this centrifugal pendulum device is characterized in that at least one hole for attaching a balancing mass is made in the pendulum mass carrier in one process step, and in a subsequent process step the at least one pendulum mass is attached to the pendulum mass Delmasseträger is displaceably attached, and in a further process step to reduce an imbalance at least one balancing mass is attached using the at least one hole on the pendulum mass carrier.

The invention is based on the object of structurally and / or functionally improving a torsional vibration damper mentioned at the beginning. In addition, the invention is based on the object of providing an improved method for balancing such a torsional vibration damper.

The object is achieved with a torsional vibration damper with the features of claim 1. Advantageous designs and developments are the subject of the dependent claims.

The terms “input part” and “output part” relate in particular to a line flow direction starting from a traction drive machine. Unless otherwise stated or the context does not indicate otherwise, the information “axial”, “radial” and “in the circumferential direction” refer to a direction of extension of the axis of rotation. “Axial” corresponds to the direction of extension of the axis of rotation. "Radial" is a direction perpendicular to the direction of extension of the axis of rotation and intersecting with the axis of rotation. "In the circumferential direction" corresponds to a circular arc direction around the axis of rotation.

The closing head of the at least one rivet is at least partially arranged in a recess of a second component of the output part. The closing head of the at least one rivet can also be partially arranged in a recess in the first component of the output part. The first component and the second component can lie against one another. The recess of the second component and the recess of the first component can be arranged opposite one another.

The closing head of the at least one rivet can essentially completely fill the recess in the first component and the recess in the second component. Substantially filling here means that at least 80 percent, preferably at least 90 percent, most preferably at least 95 percent of a common volume formed by the depressions is filled by the closing head are. The recess of the second component and the recess of the first component can completely accommodate the closing head of the at least one rivet.

The output part can have an output flange part. The outlet flange part can have radially outwardly projecting extensions. The extensions can protrude into a receiving space for the at least one mechanical energy store. The extensions can serve as support sections on the output part side for the at least one mechanical energy store. The output part can have a hub part. The hub part can have a flange section and a hub section. The hub part can be connectable to a shaft. The shaft can be a gear input shaft. The hub section can have internal teeth for connection to external teeth of a shaft. The flange part and the hub part can be firmly connected to one another. The flange part and the hub part can be made in one piece. The flange part and the hub part can be non-positively and / or positively connected to one another, in particular riveted.

The at least one mechanical energy store can be supported on the one hand on the input part and on the other hand on the output part. The at least one mechanical energy store can be a helical spring. The at least one mechanical energy store can be a compression spring. The at least one mechanical energy store can be an arc spring.

The output flange part can be the first component of the output part to which the at least one rivet is attached, and the hub part, in particular a flange section of the hub part, the second component of the output part with the recess in which the closing head of the at least one rivet is at least partially arranged it's his. Alternatively, the hub part, in particular a flange section of the hub part, the first component of the output part to which the at least one rivet is attached, and the output flange part, the second component of the output part with the recess in which the closing head of the at least one rivet is at least partially is arranged to be. The output part can have a centrifugal pendulum device. The centrifugal pendulum device can have a pendulum mass carrier rotatable about the axis of rotation and at least one pendulum mass arranged on the pendulum mass carrier so as to be displaceable along a pendulum track. The centrifugal pendulum device serves to dampen vibrations. The centrifugal pendulum device can have exactly two pendulum masses. The centrifugal pendulum device can have more than two pendulum masses. Two pendulum masses can be arranged diametrically opposite one another on the pendulum mass carrier. The centrifugal pendulum device can have at least one pendulum mass, which has two pendulum mass parts connected to one another.

The pendulum mass carrier can be arranged axially between the pendulum mass parts, so that the pendulum mass parts are arranged on the outside of the pendulum mass carrier. The pendulum mass carrier can have two pendulum mass carrier parts. The at least one pendulum mass can then be arranged axially between the pendulum mass carrier parts, so that the at least one pendulum mass is arranged on the inside. The pendulum mass carrier can have at least one recess for a rolling element. The at least one recess can serve to define an aerial tramway. The at least one recess can have a kidney-like shape.

The pendulum mass carrier can be the first component of the output part to which the at least one rivet is attached, and the hub part, in particular a flange section of the hub part, the second component of the output part with the recess in which the closing head of the at least one rivet is at least partially arranged it's his. Alternatively, the hub part, in particular a flange section of the hub part, the first component of the output part to which the at least one rivet is attached, and the pendulum mass carrier the second component of the output part with the recess in which the closing head of the at least one rivet is at least partially is arranged to be.

A bottom of the recess of the second component can adjoin a receiving space. The at least one mechanical energy store can be arranged in the receiving space. A centrifugal pendulum device can be arranged in the receiving space. The receiving space can be sealed with a sealing arrangement. The receiving space can be sealed with a sealing arrangement having a plate spring membrane. The receiving space can be sealed with a plate spring membrane. The bottom of the recess can be a closed surface.

As a result, no dirt can get through the recess into the receiving space. In addition, no fat can escape from the receiving space via the depression. The at least one rivet can thus be fastened to the output part without opening the receiving space.

The torsional vibration damper can have exactly one rivet that acts as a balancing mass. The torsional vibration damper can have several rivets that act as balancing masses. At least one of the plurality of rivets can be attached to a first component of the output part by means of a setting head and a closing head, the closing head of the at least one of the plurality of rivets being at least partially arranged in a recess of a second component of the output part. All of the multiple rivets can be fastened to a first component of the output part by means of a setting head and a closing head, the closing head of the plurality of rivets being at least partially arranged in a respective recess of a second component of the output part.

Several rivets that act as balancing masses can be distributed evenly over the circumference of the pendulum mass carrier. Several rivets acting as balancing masses can be arranged distributed unevenly over the circumference of the pendulum mass carrier. A plurality of rivets acting as balancing masses can be arranged distributed centrally with respect to an axis of rotation of the torsional vibration damper. Several rivets that act as balancing masses can be arranged eccentrically in relation to an axis of rotation of the torsional vibration damper. Several rivets that act as balancing masses can be arranged distributed over the circumference of the pendulum mass carrier, determined by means of a calculation.

The object is also achieved by a method for balancing a torsional vibration damper with the features of claim 8. In one method step, a rivet shank of the at least one rivet is inserted through an opening in the first component of the output part, and in a subsequent method step a force is applied the setting head of the at least one rivet applied, so that one of the The end of the rivet shank facing away from the setting head is pressed against a bottom of the recess of the second component of the starting part in such a way that the closing head is formed on the end of the rivet shank facing away from the setting head.

The second component of the starting part can serve as a tool for forming the closing head during the process. The second component of the starting part can serve as the only tool for forming the closing head during the process. This can reduce tool costs.

A setting head diameter and / or a setting head length and / or a rivet shank diameter can be selected as a function of the size of an unbalance to be balanced. For this purpose, the at least one rivet can be selected from a construction kit with different rivets. The kit can have several rivets with different set head diameters and / or set head lengths and / or rivet shank diameters.

The torsional vibration damper can be used for arrangement in a drive train of a vehicle. The drive train can have a drive machine. The prime mover can be an internal combustion engine. The internal combustion engine can have a crankshaft. The drive train can have a friction clutch device. The drive train can have a hydrodynamic torque converter. The drive train can have a transmission. The drive train can have at least one drivable vehicle wheel. The drive train can have an auxiliary unit drive. The torsional vibration damper can be designed as a dual mass flywheel. The torsional vibration damper can be arranged between the drive machine and the hydrodynamic torque converter or the transmission.

In summary and in other words, the invention thus results, inter alia, in a torsional vibration damper and a method for balancing a torsional vibration damper by means of a balancing rivet. The secondary sides of torsional vibration dampers and dual mass flywheels must be balanced so that there are no disruptions in the ferry operation of the vehicle in which they are installed. With the invention it can be avoided that in one of the Components of the torsional vibration damper must be drilled for the purpose of balancing, in particular to achieve a balancing target. In the case of torsional vibration dampers with centrifugal pendulums, swarfs are avoided during balancing compared to balancing methods known from the prior art. The chips could enter the centrifugal pendulum and cause disturbances to the centrifugal pendulum. In preferred exemplary embodiments of a torsional vibration damper according to the invention, the (balancing) rivet is inserted through the components from right to left (from the output part in the direction of the input part). In other exemplary embodiments, the process can also be applied from left to right. The rivet shaft is deformed so that a closing head is created. The pressing force acts on the setting head so that the closing head adapts to cavities (depressions) in components A (first component) and B (second component). The cavities can be impressions in part A and / or part B. A sufficient embedment ensures that the balancing rivet is firmly seated. The set head length, the set head diameter, the shaft length, the shaft diameter and the dimensions of the cavities vary depending on the project and / or product. Another advantage is that part B, on which the rivet shank rests during the deformation, is closed (in particular in the circumferential direction) and thus a grease space, in particular a receiving space, is sealed.

A torsional vibration damper is optimized with the invention. An alternative method of balancing a torsional vibration damper is provided. In particular, chip-forming manufacturing processes, for example balancing bores, can be dispensed with.

In the following, exemplary embodiments of the invention are described in more detail with reference to figures. Further features and advantages emerge from this description. Specific features of these exemplary embodiments can represent general features of the invention. Features of these exemplary embodiments that are connected to other features can also represent individual features of the invention.

They show schematically and by way of example: 1 shows a section through a rotary vibration damper according to the invention according to a first exemplary embodiment,

FIG. 2 shows a rivet prior to assembly as a balancing mass in the torsional vibration damper from FIG. 1,

3 shows a detailed view of the torsional vibration damper from FIG. 1 in the area of the rivet that acts as a balancing mass,

4 shows a section through a rotary vibration damper according to the invention according to a second exemplary embodiment,

FIG. 5 shows an output flange part of the torsional vibration damper from FIG. 4,

6 shows a section through a rotary vibration damper according to the invention according to a third exemplary embodiment,

7 shows a detail of a section through a rotary vibration damper according to the invention according to a fourth exemplary embodiment, and FIG

8 shows a detail of a section through a rotary vibration damper according to the invention according to a fifth exemplary embodiment.

1 shows a section of a torsional vibration damper designed as a dual mass flywheel 100 according to a first exemplary embodiment. The dual-mass flywheel 100 is used for arrangement in a drive train of a motor vehicle, for example between an internal combustion engine and a friction clutch, in order to reduce torsional vibrations.

The dual mass flywheel 100 has an input part 102 and an output part 104. The input part 102 and the output part 104 can be rotated together about a common axis of rotation 106 and rotated to a limited extent relative to one another. The directional information used, such as “axial”, “radial” and “circumferential direction”, are related to the axis of rotation 106 of the dual-mass flywheel 100, unless otherwise described. A spring damper device is effective between the input part 102 and the output part 104. The spring damper device has a mechanical energy store, in the present case an arc spring arrangement with two arc springs 108, and a sliding shell 110.

The input part 102 has an input flange part 112 and a cover part 114.

The inlet flange part 112 is largely cup-shaped with a central opening.

The input flange part 112 can be screwed on the input side with screws, which are not shown in FIG. 1, to a further component of the drive train of the motor vehicle, for example a crankshaft of an internal combustion engine, also not shown. The cover part 114 is largely like a ring disk. The inlet flange part 112 and the cover part 114 are firmly connected to one another, in the present case welded. The inlet flange part 112 and the cover part 114 delimit a receiving space 116. The arc springs 108 and a centrifugal pendulum device 118 are arranged in the receiving space 116.

A starter ring gear 120 is arranged radially on the outside on the input flange part 112 and is fastened to the input flange part 112. In the installation position of the dual-mass flywheel 100, the starter ring gear 120 can be brought into engagement with an electric starter of the motor vehicle, not shown here.

The output part 104 has an output flange part 122 and an output part, in this case a hub part 124. The hub part 124 is largely cup-shaped with a central opening. The hub part 124 has a flange section 126 and a hub section 128. The hub section 128 has an internal toothing 130 for connection to an external toothing of a shaft not shown in FIG. 1. The outlet flange part 122 is connected to the hub part 124 by means of a plurality of rivet connections that are distributed over the circumference and are not shown in FIG.

The inlet flange part 112 and the cover part 114 have passages, not shown in FIG. 1, which protrude into the receiving space 116 and which form the inlet-side support sections for the arc springs 108. The output flange part 122 has radially outward extensions 132 which protrude into the receiving space 116 and form the output-side support sections for the arc springs 108.

A sealing arrangement seals off the receiving space 116. The sealing arrangement has a disc spring membrane 134 and a friction ring 136. A radially inner area of the disc spring membrane 134 rests on the output flange part 122 and is preferably connected to the output flange part 122 by means of the rivet connections (not shown in FIG. 1) between the output flange part 122 and the hub part 124. A radially outer area of the disc spring membrane 134 rests against the friction ring 136. The friction ring 136 is connected to the cover part 114. The disk spring diaphragm 134 closes an annular gap between the output flange part 122 and the cover part 114 and is axially pretensioned between the output flange part 122 and the cover part 114.

The centrifugal pendulum device 1 18 eliminates rotational irregularities and thereby increases the effectiveness of the dual-mass flywheel 100. The centrifugal pendulum device 1 18 is assigned to the output part 104. The centrifugal pendulum device 1 18 is arranged in the receiving space 1 16.

The centrifugal pendulum device 118 has a pendulum mass carrier 138. The pendulum mass carrier 138 is largely in the form of an annular disk. Pendulum masses such as 140 are arranged on pendulum mass carrier 138 so that they can be displaced along one or more pendulum tracks. The pendulum tracks are formed in the pendulum mass carrier 138. The pendulum mass carrier 138 is connected to the hub part 124 and the output flange part 122 by means of the rivet connections (not shown in FIG. 1). The flange section 126 of the hub part 124 is arranged axially between the pendulum mass carrier 138 and the output flange part 122.

A rivet 142, which acts as a balancing mass, is attached to a first component 144 of the output part 104, in this case the output flange part 122. The rivet 142 has a setting head 146, a rivet shank 148 and a closing head 150. The closing head 150 of the rivet 142 is partially arranged in a recess 156 of a second component 154, in this case the hub part 124. In addition, the closing head 150 is partially in a recess 152 of the first component 144 (of the output flange part 122) arranged. The rivet shank 148 extends through an opening 158 of the first component 144 (the output flange portion 122). The setting head 146 is arranged on the side of the first component 144 facing away from the input part 102.

2 shows the rivet 142 in an original state, that is, before riveting to the starting part 104. A setting head diameter 162, a setting head length 164, a shank diameter 166, and a shank length 168 are selected with regard to an optimal balancing result. The rivet 142 is preferably selected from a construction kit with rivets of different dimensions. Different shaft lengths 168 are indicated in FIG. 2 by partially hatched lines.

3 shows a detailed view of the dual mass flywheel 100 in the area of the rivet 142, which acts as a balancing mass. FIG. 3 shows the rivet 142 in a deformed state, that is to say with the closing head 150 formed. The opening 158 in the first component 144 (in the outlet flange part 122) is stepped in the axial direction. A first cylindrical section of the opening 158 has a first hole diameter 172. A second cylindrical section of the opening 158 adjoining the first cylindrical section of the opening 158 has a second hole diameter 174. The first hole diameter 172 corresponds to the shaft diameter 166 of the Rivet 142. In the present case, the second hole diameter 174 is slightly larger than a closing head diameter 176 of the closing head 150. The second hole diameter 174 is smaller than the first hole diameter 172. The second hole diameter 174 and the first hole diameter 172 are each smaller than the setting head diameter 162.

A method for assembling and balancing the dual-mass flywheel 100 provides that, in a method step, the rivet shank 148 of the rivet 142 is pushed through the opening 158 of the first component 144 (output flange part 122). In a subsequent method step, a force 160 is applied to the setting head 146 of the rivet 142, so that an end of the rivet shaft 148 facing away from the setting head 146 is pressed against a bottom 162 of the recess 156 of the second component 154 (hub part 124) in such a way that the closing head 150 is formed at the end of the rivet shaft 148 facing away from the setting head 146. The second component 154 serves as a tool, in particular as the only tool, for forming the closing head 150 during the method according to the invention. The setting head diameter 162 and / or the setting head length 164 and / or the shank diameter 166 and / or the shank length 168 are selected depending on the size of an imbalance to be balanced, in particular the rivet 142 is selected from a construction kit with different rivets.

A second exemplary embodiment of a torsional vibration damper designed as a dual mass flywheel 200 is shown in FIGS. 4 and 5. The dual mass flywheel 200 corresponds to the previously described dual mass flywheel 100 in terms of structure and function, unless otherwise described. A method for assembling and balancing the dual-mass flywheel 200 corresponds to the previously described method for assembling and balancing the dual-mass flywheel 100, unless otherwise described.

The dual mass flywheel 200 has an input part 202 and an output part 204. The input part 202 and the output part 204 can be rotated together about a common axis of rotation 206 and rotated to a limited extent relative to one another. A spring damper device is effective between the input part 202 and the output part 204. The spring damper device has a mechanical energy store, in the present case an arc spring arrangement with two arc springs 208, and a sliding shell 210.

The input part 202 has an input flange part 212 and a cover part 214.

The inlet flange part 212 and the cover part 214 delimit a receiving space 216. The bow springs 208 and a centrifugal pendulum device 218 are arranged in the receiving space 216. A starter ring gear 220 is arranged radially on the outside on the input flange part 212 and is fastened to the input flange part 212.

The output part 204 has an output flange part 222 and an output part, in the present case a hub part 224. The hub part 224 has a flange section 226 and a hub section 228. The hub section 228 has an internal toothing 230. The output flange part 222 is distributed over the circumference by means of several arranged rivet connections, not shown in FIGS. 4 and 5, are connected to the hub part 224.

The inlet flange part 212 and the cover part 214 have passages, not shown in FIGS. 4 and 5, which protrude into the receiving space 216 and form support sections for the arc springs 208 on the inlet side. The output flange part 222 has extensions 232 radially on the outside, which protrude into the receiving space 216 and form the output-side support sections for the arc springs 208.

A sealing arrangement seals off the receiving space 216. The sealing arrangement has a disc spring membrane 234 and a friction ring 236. A radially inner region of the disc spring membrane 234 rests against the outlet flange part 222. A radially outer area of the plate spring membrane 234 rests on the friction ring 236. The friction ring 236 is connected to the cover part 214.

The centrifugal pendulum device 218 has a pendulum mass carrier 238 integrated into the output flange part 222. The output flange part 222 is largely in the form of an annular disk. In a radially inner region of the extensions 232, the output flange part 222 is bent in such a way that a radially outer region of the extensions 232 supporting the arc springs is axially offset from the region of the output flange part 222 serving as a pendulum mass carrier 238.

Pendulum masses, such as 240, are arranged on pendulum mass carrier 238 so as to be displaceable along one or more pendulum tracks. The outlet flange part 222 is connected to the hub part 224 by means of the rivet connections not shown in FIGS. 4 and 5. The flange section 226 of the hub part 224 is arranged axially next to the output flange part 222. The output flange part 222 is arranged axially between the input part 202 and the flange section 226 of the hub part 224.

A rivet 242 that acts as a balancing mass is attached to a first component 244 of the output part 204, in this case the hub part 224. The rivet 242 is attached to the flange portion 226 of the hub portion 224. The rivet 242 has a setting head 246, a rivet shank 248 and a closing head 250. The closing head 250 of the rivet 242 is partially in a recess of a second component 252, in this case the Output flange part 222 arranged. In addition, the closing head 250 is partially arranged in a recess of the first component 244 (of the hub part 224). The rivet shank 248 extends through an opening in the first component 244 (of the hub part 224). The setting head 246 is arranged on the side of the first component 244 facing away from the input part 202.

A method for assembling and balancing the dual mass flywheel 200 provides that the rivet shank 248 of the rivet 242 is pushed through the opening 258 of the first component 244 (hub part 224) in a method step. In a subsequent process step, a force is applied to the setting head 246 of the rivet 242 so that an end of the rivet shaft 248 facing away from the setting head 246 is pressed against a bottom of the recess of the second component 252 (output flange part 222) in such a way that the The end of the rivet shank 248 facing away from the setting head 246, the closing head 250 is formed.

The second component 252 serves as a tool, in particular as the only tool, for forming the closing head 250 during the method according to the invention. A setting head diameter and / or a setting head length and / or a shank diameter and / or a shank length are selected as a function of the size of an unbalance to be balanced, in particular the rivet 242 is selected from a modular system with different rivets.

6 shows a third exemplary embodiment of a torsional vibration damper designed as a dual mass flywheel 300. The dual-mass flywheel 300 corresponds in terms of structure and function to the previously-described dual-mass flywheel 100 of the first exemplary embodiment, unless otherwise described or shown differently in FIG. 6. A method for mounting and balancing the dual-mass flywheel 300 corresponds to the previously described method for mounting and balancing the dual-mass flywheel 100 of the first exemplary embodiment, unless otherwise described.

The dual mass flywheel 300 has an input part 302 and an output part 304. The input part 302 and the output part 304 are around a common one Axis of rotation 306 rotatable together and rotatable to a limited extent relative to one another. A spring damper device is operative between the input part 302 and the output part 304. The spring damper device has a mechanical energy store, in the present case an arc spring arrangement with two arc springs 308, and a sliding shell 310.

The input part 302 has an input flange part 312 and a cover part 314.

The inlet flange part 312 and the cover part 314 delimit a receiving space 316. The arc springs 308 are arranged in the receiving space 316. A centrifugal pendulum device 318 is arranged outside the receiving space 316 on a side of the cover part 314 facing away from the input part 302. A burst protection for the external centrifugal pendulum device 318 is integrated into the cover part 314. A starter ring gear 320 is arranged radially on the outside on the input flange part 312 and is fastened to the input flange part 312.

The output part 304 has an output flange part 322 and an output part, in the present case a hub part 324. The hub portion 324 has a flange portion 326 and a hub portion 328. The hub section 328 has an internal toothing 330. The output flange part 322 is connected to the hub part 324 by means of a plurality of rivet connections, not shown in FIG. 6, which are arranged distributed over the circumference.

The inlet flange part 312 and the cover part 314 have passages, not shown in FIG. 6, which protrude into the receiving space 316 and form support sections for the arc springs 308 on the inlet side. The output flange part 322 has radially outward extensions, not shown in FIG. 6, which protrude into the receiving space 316 and form the output-side support sections for the arc springs 308.

A sealing arrangement seals off the receiving space 316. The sealing arrangement has a disc spring membrane 332 and a friction ring 334. A radially inner region of the disc spring membrane 332 rests against the outlet flange part 322. A radially outer area of the plate spring membrane 332 rests on the friction ring 334. The friction ring 334 is connected to the cover part 314. The centrifugal pendulum device 318 has a pendulum mass carrier 336. The pendulum mass carrier 336 is axially angled once and otherwise largely in the shape of an annular disk. Pendulum masses, such as 338, are arranged on pendulum mass carrier 336 such that they can be displaced along one or more pendulum tracks. The pendulum tracks are formed in the pendulum mass carrier 336. The pendulum mass carrier 336 is connected to the hub part 324 and the output flange part 322 by means of the rivet connections not shown in FIG. 6. The flange section 326 of the hub part 324 is arranged axially between the pendulum mass carrier 336 and the output flange part 322.

A rivet 340 that acts as a balancing mass is attached to a first component 342 of the output part 304, in the present case the pendulum mass carrier 336. The rivet 340 is attached to the flange portion 326 of the hub portion 324. The rivet 340 has a setting head 344, a rivet shaft 346 and a closing head 348. The closing head 348 of the rivet 340 is partially arranged in a recess of a second component 350, in this case the hub part 324. In addition, the closing head 348 is partially arranged in a recess in the first component 342 (of the pendulum mass carrier 336).

The rivet shaft 346 runs through an opening in the first component 342 (the pendulum mass carrier 336). The setting head 344 is arranged on the side of the first component 342 facing away from the input part 302.

A method for assembling and balancing the dual mass flywheel 300 provides that the rivet shaft 346 of the rivet 340 is pushed through the opening of the first component 342 (pendulum mass carrier 336) in a method step. In a subsequent method step, a force is applied to the setting head 344 of the rivet 340, so that an end of the rivet shaft 346 facing away from the setting head 344 is pressed against a bottom of the recess of the second component 350 (hub part 324) in such a way that the setting head 344 facing away from the end of the rivet shaft 346 the locking head 348 is formed.

The second component 350 serves as a tool, in particular as the only tool, for forming the closing head 348 during the method according to the invention. A setting head diameter and / or a setting head length and / or a shank The diameter and / or a shaft length are selected as a function of the size of an unbalance to be balanced, in particular the rivet 340 is selected from a modular system with different rivets.

7 shows a fourth exemplary embodiment of a torsional vibration damper designed as a dual mass flywheel 400. The dual-mass flywheel 400 corresponds in terms of structure and function to the previously described dual-mass flywheel 200 of the second exemplary embodiment, unless otherwise described. A method for mounting and balancing the dual-mass flywheel 400 corresponds with regard to the previously described method for mounting and balancing the dual-mass flywheel 200 of the second exemplary embodiment, unless otherwise described.

The dual mass flywheel 400 has an input part 402 and an output part 404. The input part 402 and the output part 404 can be rotated together about a common axis of rotation 406 and rotated to a limited extent relative to one another. A spring-damper device is operative between the input part 402 and the output part 404. The spring damper device has a mechanical energy store, in the present case an arc spring arrangement with two arc springs 408, and a sliding shell 410.

The input part 402 has an input flange part 412 and a cover part 414.

The inlet flange part 412 and the cover part 414 delimit a receiving space 416. The bow springs 408 are arranged in the receiving space 416. A starter ring gear 418 is arranged radially on the outside on the input flange part 412 and is fastened to the input flange part 412.

The output part 404 has an output flange part 420 and an output part, in the present case a hub part 422. The hub part 422 has a flange section 424 and a hub section 426. The hub section 426 has an internal toothing 428. The output flange part 420 is connected to the hub part 422 by means of a plurality of rivet connections, not shown in FIG. 7, which are arranged distributed over the circumference. The inlet flange part 412 and the cover part 414 have passages, not shown in FIG. 1, which protrude into the receiving space 416 and form the inlet-side support sections for the arc springs 408. The output flange part 420 has extensions, not shown radially on the outside in FIG. 7, which protrude into the receiving space 416 and form the output-side support sections for the bow springs 408.

A sealing arrangement seals off the receiving space 416. The sealing arrangement has a disc spring membrane 430 and a friction ring 432. A radially inner area of the disc spring membrane 430 rests against the outlet flange part 420. A radially outer area of the plate spring membrane 430 rests on the friction ring 432. The friction ring 432 is connected to the cover part 414. A sealing ring 434 also seals an annular gap between the inlet flange part 412 and the outlet flange part 420.

A rivet 436 that acts as a balancing mass is attached to a first component 438 of the output part 404, in this case the hub part 422. The rivet 436 is attached to the flange portion 424 of the hub portion 422. The rivet 436 has a setting head 440, a rivet shank 442 and a closing head 444. The closing head 444 of the rivet 436 is partially arranged in a recess of a second component 446, in this case the output flange part 420. In addition, the closing head 444 is partially arranged in a recess of the first component 438 (of the hub part 422). The rivet shank 442 extends through an opening in the first component 438 (of the hub part 422). The setting head 440 is arranged on the side of the first component 438 facing away from the input part 402.

A method for assembling and balancing the dual mass flywheel 400 provides that the rivet shank 442 of the rivet 436 is pushed through the opening of the first component 438 (hub part 422) in a method step. In a subsequent method step, a force is applied to the setting head 440 of the rivet 436, so that an end of the rivet shaft 442 facing away from the setting head 440 is pressed against a bottom of the recess of the second component 446 (output flange part 420) in such a way that the end of the rivet shank 442 facing away from the setting head 440, the closing head 444 is formed. The second component 446 serves as a tool, in particular as the only tool, for forming the closing head 444 during the method according to the invention. A setting head diameter and / or a setting head length and / or a shank diameter and / or a shank length are selected as a function of the size of an unbalance to be balanced, in particular the rivet 436 is selected from a modular system with different rivets.

8 shows a fifth exemplary embodiment of a torsional vibration damper designed as a dual mass flywheel 500. The dual-mass flywheel 500 corresponds in terms of structure and function to the previously described dual-mass flywheel 300 of the third exemplary embodiment, unless otherwise described or shown differently in the figures. A method for mounting and balancing the dual-mass flywheel 500 corresponds to the previously described method for mounting and balancing the dual-mass flywheel 300 of the third exemplary embodiment, unless otherwise described.

The dual mass flywheel 500 has an input part 502 and an output part 504. The input part 502 and the output part 504 can be rotated together about a common axis of rotation 506 and rotated to a limited extent relative to one another. A spring damper device is effective between the input part 502 and the output part 504. The spring-damper device has a mechanical energy store, in the present case an arc spring arrangement with two arc springs 508 and a sliding shell 510.

The input part 502 has an input flange part 512 and a cover part 514.

The inlet flange part 512 and the cover part 514 delimit a receiving space 516. The arc springs 508 are arranged in the receiving space 516. A centrifugal pendulum device 518 is arranged outside the receiving space 516 on a side of the cover part 514 facing away from the input part 502. A burst protection for the external centrifugal pendulum device 518 is attached to the cover part 514. A starter ring gear 520 is arranged radially on the outside on the input flange part 512 and is fastened to the input flange part 512. The output part 504 has an output flange part 522 and an output part, in the present case a hub part 524. The hub portion 524 has a flange portion 526 and a hub portion 528. The hub section 528 has an internal toothing 530. The output flange part 522 is connected to the hub part 524 by means of a plurality of rivet connections, not shown in FIG. 8, which are arranged distributed over the circumference.

The inlet flange part 512 and the cover part 514 have passages, not shown in FIG. 8, which protrude into the receiving space 516 and form support sections for the arc springs 508 on the inlet side. The output flange part 522 has radially outside extensions (not shown in FIG. 8) which protrude into the receiving space 516 and form support sections for the arc springs 508 on the output side.

A sealing arrangement seals the receiving space 516. The sealing arrangement has a disc spring membrane 532 and a friction ring 534. A radially inner area of the disc spring membrane 532 rests against the outlet flange part 522. A radially outer area of the plate spring membrane 532 rests on the friction ring 534. The friction ring 534 is connected to the cover part 514.

The centrifugal pendulum device 518 has a pendulum mass carrier 536. The pendulum mass carrier 536 is axially angled once and otherwise largely in the shape of an annular disk. Pendulum masses, such as 538, are arranged on pendulum mass carrier 536 such that they can be displaced along one or more pendulum tracks. The pendulum tracks are formed in the pendulum mass carrier 536. The pendulum mass carrier 536 is connected to the hub part 524 and the output flange part 522 by means of the rivet connections not shown in FIG. 8. The flange section 526 of the hub part 524 is arranged axially between the pendulum mass carrier 536 and the output flange part 522, a spacer ring 540 being arranged between the output flange part 522 and the flange section 526.

A rivet 542 that acts as a balancing mass is attached to a first component 544 of the output part 504, in this case the pendulum mass carrier 536. The rivet 542 is attached to the flange portion 526 of the hub portion 524. The rivet 542 has a setting head 546, a rivet shank 548 and a closing head 550. The closing head 550 of the rivet 542 is partially arranged in a recess of a second component 552, in this case the hub part 524. In addition, the closing head 550 is partially arranged in a recess of the first component 544 (of the pendulum mass carrier 536).

The rivet shaft 548 extends through an opening in the first component 544 (the pendulum mass carrier 536). The setting head 546 is arranged on the side of the first component 544 facing away from the input part 502.

A method for assembling and balancing the dual mass flywheel 500 provides that the rivet shank 548 of the rivet 542 is pushed through the opening of the first component 544 (pendulum mass carrier 536) in a method step. In a subsequent process step, a force is applied to the setting head 546 of the rivet 542, so that an end of the rivet shaft 548 facing away from the setting head 546 is pressed against a bottom of the recess of the second component 552 (hub part 524) in such a way that the setting head 546 opposite end of the rivet shaft 548 the closing head 550 is formed.

The second component 552 serves as a tool, in particular as the only tool, for forming the closing head 550 during the method according to the invention. A setting head diameter and / or a setting head length and / or a shank diameter and / or a shank length are selected depending on the size of an unbalance to be balanced, in particular the rivet 542 is selected from a modular system with different rivets.

List of reference symbols

Dual mass flywheel

Input part

Output part

Axis of rotation

Bow feather

Sliding cup

Inlet flange part

Cover part

Recording room

Centrifugal pendulum device

Starter ring gear

Outlet flange part

Hub part

Flange section

Hub section

Internal gearing

Appendix

Disc spring diaphragm

Friction ring

Pendulum mass carrier

Pendulum mass

rivet

first component

Setting head

Rivet shank

Closing head

Recess (of the first component 144) second component

Recess (of the second component 154)

opening

force Setting head diameter

Set head length

Shaft diameter

Shaft length

ground

first hole diameter second hole diameter closing head diameter

Dual mass flywheel

Input part

Output part

Axis of rotation

Bow feather

Sliding cup

Inlet flange part

Cover part

Recording room

Centrifugal pendulum device

Starter ring gear

Outlet flange part

Hub part

Flange section

Hub section

Internal gearing

Appendix

Disc spring diaphragm

Friction ring

Pendulum mass carrier

Pendulum mass

rivet

first component

Setting head

Rivet shank Closing head

second component

Dual mass flywheel

Input part

Output part

Axis of rotation

Bow feather

Sliding cup

Inlet flange part

Cover part

Recording room

Centrifugal pendulum device

Starter ring gear

Outlet flange part

Hub part

Flange section

Hub section

Internal gearing

Disc spring diaphragm

Friction ring

Pendulum mass carrier

Pendulum mass

rivet

first component

Setting head

Rivet shank

Closing head

second component

Dual mass flywheel

Input part

Output part

Axis of rotation Bow feather

Sliding cup

Inlet flange part

Cover part

Recording room

Starter ring gear

Outlet flange part

Hub part

Flange section

Hub section

Internal gearing

Disc spring diaphragm

Friction ring

Sealing ring

rivet

first component

Setting head

Rivet shank

Closing head

second component

Dual mass flywheel

Input part

Output part

Axis of rotation

Bow feather

Sliding cup

Inlet flange part

Cover part

Recording room

Centrifugal pendulum device

Starter ring gear

Outlet flange part

Hub part Flange section

Hub section

Internal gearing

Disc spring diaphragm

Friction ring

Pendulum mass carrier

Pendulum mass

Spacer ring

rivet

first component set head

Rivet shank

Closing head second component

Claims

1. Torsional vibration damper, in particular dual-mass flywheel (100, 200, 300, 400, 500), the torsional vibration damper having an input part (102, 202, 302, 402, 502) and an output part (104, 204, 304, 404, 504) with a

common axis of rotation (106, 206, 306, 406, 506) about which the input part (102, 202, 302, 402, 502) and the output part (104, 204, 304, 404, 504) can be rotated together and rotated to a limited extent relative to one another are, a spring-damper device effective between the input part (102, 202, 302, 402, 502) and the output part (104, 204, 304, 404, 504) with at least one mechanical energy storage device, in particular an arc spring (108, 208 , 308, 408, 508), and at least one rivet (142, 242, 340, 436, 542) effective as a balancing mass, the at least one rivet (142, 242, 340, 436, 542) by means of a setting head (146, 246 , 344, 440, 546) and a closing head (150, 250, 348, 444, 550) on a first component (144, 244, 342, 438, 544) of the

Output part (104, 204, 304, 404, 504) is attached, characterized in that the closing head (150, 250, 348, 444, 550) of the at least one rivet (142, 242, 340, 436, 542) at least partially in a recess (156) of a second component (154, 252, 350, 446, 552) of the output part (104, 204, 304, 404, 504) is arranged.

2. Torsional vibration damper according to claim 1, characterized in that the closing head (150, 250, 348, 444, 550) of the at least one rivet (142, 242, 340, 436, 542) partially in a recess (152) of the first component ( 144, 244, 342, 438, 544) of the output part (104, 204, 304, 404, 504) is arranged.

3. A torsional vibration damper according to claim 1 or 2, characterized in that the closing head (150, 250, 348, 444, 550) of the at least one rivet (142, 242, 340, 436, 542) has the recess (152) in the first component (144, 244, 342,

438, 544) and the recess (156) in the second component (154, 252, 350, 446, 552) is essentially completely filled.

4. Torsional vibration damper according to at least one of the preceding

Claims, characterized in that the output part (104, 204, 404) has an output flange part (122, 222, 420) with extensions (132, 232) as the output side Support means for the at least one mechanical energy store and a hub part (124, 224, 422) connectable to a shaft, wherein the output flange part (122) the first component (144) and the hub part (124) the second component (154) of the Output part (104), or the hub part (224, 422) is the first component (244, 438) and the output flange part (222, 420) is the second component (254, 446) of the output part (204, 404).

5. Torsional vibration damper according to at least one of the preceding

Claims, characterized in that the output part (304, 504) has a centrifugal pendulum device (318, 518) with a pendulum mass carrier (336, 536) rotatable about the axis of rotation (306, 506) and at least one on the

Pendulum mass carrier (336, 536) can be displaced along an aerial tramway

arranged pendulum mass (338, 538), and a hub part (324, 524) connectable to a shaft, wherein the pendulum mass carrier (336, 536) the first component (342, 544) and the hub part (324, 524) the second component (350, 552) of the output part (304, 504), or the hub part is the first component and the pendulum mass carrier is the second component of the output part.

6. Torsional vibration damper according to at least one of the preceding

Claims, characterized in that a bottom of the recess of the second component (252) adjoins a receiving space (216), and the at least one mechanical energy store (208) and / or a centrifugal pendulum device (218) is arranged in the receiving space (216).

7. Torsional vibration damper according to at least one of the preceding

Claims, characterized in that a plurality of rivets acting as balancing masses, in particular arranged distributed over the circumference, are attached to the output part.

8. The method for balancing a torsional vibration damper according to one of claims 1 to 7, characterized in that in one process step a rivet shank (148, 248, 346, 442, 548) of the at least one rivet (142, 242, 340, 436, 542) is inserted through an opening (158) of the first component (144, 244, 342, 438, 544) of the output part (104, 204, 304, 404, 504), in a subsequent method step a force is applied to the setting head (146, 246, 344, 440, 546) of the at least one rivet (142, 242, 340, 436, 542) is applied, so that an end of the rivet shaft facing away from the setting head (146, 246, 344, 440, 546) (148, 248, 346, 442, 548) against a bottom (170) of the recess (156) of the second component (154, 252, 350, 446, 552) of the output part (104, 204, 304, 404, 504) is pressed so that the closing head (150, 250, 348, 444, 550) is formed on the end of the rivet shaft (148, 248, 346, 442, 548) facing away from the setting head (146, 246, 344, 440, 546).

9. The method according to claim 8, characterized in that the second component (154, 252, 350, 446, 552) of the output part (104, 204, 304, 404, 504) as a tool, in particular as the only tool, for training of

Closing head (150, 250, 348, 444, 550) is used.

10. The method according to claim 8 or 9, characterized in that a

Set head diameter (162) and / or a set head length (164) and / or a shank diameter (166) can be selected depending on the size of an unbalance to be balanced, in particular the at least one rivet (142, 242, 340, 436, 542) from a kit different rivets is selected.