CN114183499A - Torsional vibration damper - Google Patents

Torsional vibration damper Download PDF

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Publication number
CN114183499A
CN114183499A CN202111069971.8A CN202111069971A CN114183499A CN 114183499 A CN114183499 A CN 114183499A CN 202111069971 A CN202111069971 A CN 202111069971A CN 114183499 A CN114183499 A CN 114183499A
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CN
China
Prior art keywords
damper
friction
vibration damper
torsional vibration
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202111069971.8A
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Chinese (zh)
Inventor
拉尔夫·埃德尔
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of CN114183499A publication Critical patent/CN114183499A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F16F15/13469—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • F16F15/13476—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
    • F16F15/13484—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/139—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by friction-damping means
    • F16F15/1397—Overload protection, i.e. means for limiting torque
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/13164—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by the supporting arrangement of the damper unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F16F15/1343—Wound springs characterised by the spring mounting

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

The invention relates to a torsional vibration damper (100), in particular a dual mass flywheel, the torsional vibration damper (100) having an input part (102) and an output part (104) which have a common axis of rotation (106), a spring-damper arrangement acting between the input part (102) and the output part (104), the input part (102) and the output part (104) being rotatable together about the axis of rotation and being rotatable to a limited extent relative to one another, and a friction arrangement (136) acting as a torque limiter between the input part (102) and the output part (104), the spring-damper arrangement having at least one mechanical energy store, in particular an arc spring (112), which is arranged in a receiving chamber (126), characterized in that the friction arrangement (136) is arranged outside the receiving chamber (126).

Description

Torsional vibration damper
Technical Field
The invention relates to a torsional vibration damper, in particular a dual mass flywheel, having an input part and an output part which have a common axis of rotation, a spring damper arrangement acting between the input part and the output part, which can rotate together about the axis of rotation and can rotate to a limited extent relative to one another, and a friction arrangement serving as a torque limiter between the input part and the output part, the spring damper arrangement having at least one mechanical energy store, in particular at least one bow spring, which is arranged in a receiving space.
Background
DE 102016223413 a1 discloses a dual mass flywheel having a primary side and a secondary side which can be rotated relative to one another against the action of at least one energy accumulator, wherein a friction device is arranged between the primary side and the secondary side and is arranged radially outside a connecting piece for connecting a damper flange of the secondary side to the secondary mass. The dual mass flywheel comprises an outer damper with a first energy accumulator and a secondary flange and an inner damper with an inner damper flange and a second energy accumulator, wherein the secondary flange couples the energy accumulators of the outer damper and the inner damper to one another, and wherein the friction device is arranged radially outside of a connection for connecting the inner damper flange to the secondary mass. The sealing plate is riveted to the secondary mass on the internal damper. The sealing plate is in contact at its radially outer region with a sealing ring arranged on the primary mass cover.
A torsional vibration damper is known from DE 102018128996 a1, which has an input part and an output part arranged so as to be rotatable relative to one another, a spring damper arrangement comprising a first spring damper arrangement arranged radially on the outside and a second spring damper arrangement arranged radially on the inside, wherein the first spring damper arrangement is arranged in the torque flow between the input part and the second spring damper arrangement is arranged in the torque flow between the first spring damper arrangement and the output part, wherein a slip clutch is provided in the torque flow between the first spring damper arrangement and the second spring damper arrangement.
Disclosure of Invention
The object of the present invention is to improve the torsional vibration damper described above with respect to structure and/or function.
This object is achieved by a torsional vibration damper having the features of claim 1. Preferred embodiments and further developments are the subject matter of the dependent claims.
By arranging the friction device outside the receiving space, the friction device is reliably protected against the ingress of grease from the receiving space, thereby ensuring very low fluctuations in the friction value.
The receiving cavity may be disposed between the input flange member and the input cover member. The arc-shaped spring flange can extend into the accommodating cavity. The circumferential gap between the input flange part and the curved spring flange can be sealed in order to prevent grease from escaping from the receiving space. The circumferential gap between the input flange part and the curved spring flange can be sealed by means of a sealing ring. The circumferential gap between the curved spring flange and the input cover part can be sealed in order to prevent grease from escaping from the receiving space. The circumferential gap between the curved spring flange and the input cover part can be sealed by means of a sealing ring and a disk spring diaphragm.
A plurality of arcuate springs may be disposed in the receiving cavity. The arcuate spring channel for receiving the plurality of arcuate springs may be an integral part of the receiving chamber. The arcuate springs may be supported on one side on the input flange member and the input cover member and on the other side on a radially outer projection of the arcuate spring flange.
The spring damper arrangement can have an external damper. The external shock absorber can comprise at least one mechanical accumulator. The at least one mechanical energy accumulator of the external vibration damper can have at least one bow spring arranged in the receiving space. An external damper may be disposed in the receiving cavity. This allows the external damper to be oiled without the friction device being affected by grease. The external damper may be arranged completely in the receiving chamber. Preferably, the outer damper has at least two arcuate springs.
The spring damper arrangement can have an internal damper comprising at least one mechanical energy store. The at least one mechanical accumulator of the internal vibration damper may have at least one compression spring. Preferably, the internal damper has at least two compression springs. The at least one mechanical energy accumulator of the internal vibration damper can be arranged outside the receiving space. The internal damper may be disposed outside the receiving cavity. The internal vibration damper is preferably arranged completely outside the receiving space. The internal damper can advantageously be integrated into the friction device.
The spring damper arrangement can have only an external damper. In a preferred embodiment, the spring damper arrangement has an outer damper and an inner damper. The outer damper and the inner damper may be connected in series. The isolation effect of the torsional vibration damper can thereby be further improved.
The outer and inner dampers may absorb energy as the input and output members rotate relative to each other against the force of the mechanical accumulator. Whereas the input part and the output part can be swivelled relative to one another by means of the force stored in the mechanical energy storage.
The friction device can have a friction lining carrier cup, at least one outer friction lining which is guided on the friction lining carrier cup in an axially displaceable manner and is coupled to the friction lining carrier cup in a rotationally fixed manner, and at least one inner friction lining which is tensioned against the outer friction lining by means of a pretensioned force store. The preloaded force accumulator is preferably a coil spring, which requires only a small installation space in the axial direction. At least one inner friction plate of the internal vibration damper and at least one mechanical energy accumulator arranged outside the receiving space can be supported by each other in the circumferential direction. Whereby at least one inner friction plate simultaneously has the function of a side plate of the inner damper. A separately constructed side plate can thus be dispensed with, which saves costs and weight.
Preferably, the friction device has two outer friction disks, two inner friction disks and a carrier flange. The carrier flange may be fixedly connected to the arcuate spring flange. The friction lining support cup can be fixedly connected to the carrier flange. Preferably, the two inner friction plates are on one side and the first end region of the at least one mechanical energy accumulator of the internal vibration damper arranged outside the receiving space is on the other side, which support each other in the circumferential direction.
A particularly effective friction device can be realized in that one of the two inner friction disks is arranged between the two outer friction disks. The other of the two inner friction plates may be arranged between the carrier flange and one of the two outer friction plates. The two inner friction plates are axially displaceable relative to the friction plate support cup. The two inner friction linings can be coupled to the friction lining support cup in a rotationally fixed manner. The friction lining support cup can have at least one axial groove, in which at least one inner friction lining, preferably all inner friction linings, can be guided axially displaceably and non-rotatably.
The second end region of the at least one mechanical energy accumulator of the internal vibration damper, which is arranged outside the receiving space, and the driven sleeve, which can be rotated in a limited manner about the axis of rotation relative to the at least one inner friction disk, can be supported on one another in the circumferential direction.
At least one bolt, in particular a stepped bolt, can be arranged at least partially axially between the two inner friction linings. The two inner friction plates can be positioned axially opposite one another by means of a screw, so that the axial distance between the inner friction plates is predetermined by the screw. The bolt may pass through an opening in the driven sleeve. In this way, a rotational stop for limiting the relative rotation between the at least one inner disk and the driven sleeve can be provided without the use of further components.
The at least one inner friction disk preferably has at least one pressure plate which engages in a recess of the driven sleeve and which serves as a further torsional stop which defines the relative rotatability between the at least one inner friction disk and the driven sleeve. The first and further torsional stops preferably together define a relative rotation between the at least one inner disk and the driven sleeve. This reduces the load on the respective rotation stop and accordingly optimizes the installation space of the rotation stop. Preferably, a plurality of further rotation stops are arranged distributed uniformly over the circumference. The two inner friction plates can have rotational stops arranged mirror-symmetrically to one another.
The torsional vibration damper may be adapted to be provided in the drive train. The torsional vibration damper may be adapted to be disposed in a hybrid drive train. The torsional vibration damper can be designed as a dual mass flywheel. The torsional vibration damper may be arranged between the internal combustion engine and the friction clutch. The torsional vibration damper may be adapted to be provided on a crankshaft. The torsional vibration damper may be adapted to be provided on the friction clutch. The torsional vibration damper can be used for being arranged on the hydraulic torque converter. The torsional vibration damper may be adapted to be provided on the transmission. A torsional vibration damper may be provided on the secondary unit drive.
The terms "input component" and "output component" relate in particular to the direction of the power flow from the internal combustion engine. The terms "axial", "radial" and "circumferential" relate to the direction of extension of the axis of rotation if not indicated to the contrary or differently from the context. Here, "axial direction" 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 the axis of rotation. "circumferential" corresponds to the direction of a circular arc about the axis of rotation.
In summary, and in other words, a torsional vibration damper is thus realized, in particular, having a torque limiter which is arranged outside the damper chamber (receiving chamber) and therefore always operates dry. The two friction plates (inner friction plates) of the torque limiter simultaneously serve as side plates of the compression spring damper (inner damper). The carrier plate (carrier flange) is preferably connected to the curved spring flange by means of rivets. The carrier plate carries the torque limiter and the (light load) internal damper. The torque limiter is preferably formed by a friction lining support cup, the outer friction lining being inserted in an axial groove of the friction lining support cup in a rotationally fixed manner. The friction lining support cup can be connected in its outer region to the carrier plate by means of rivets. Preferably, the side plates of the internal damper, which are lightly loaded between the outer friction plates, serve as the associated inner friction plates. The entire lamination stack can be pre-tensioned by means of a coil spring. The two side plates can be provided with friction linings made of paper or other friction material on both sides in the outer area. The (compression) springs of the internal vibration damper can be accommodated by spring windows (recesses) in the two side plates, which are ideally embodied symmetrically. Preferably, each spring then corresponds to a spring window in the driven sleeve.
The two side plates may be spaced apart via riveted stepped bolts. The stepped screw may be located in an opening of the driven sleeve, each two sides of the driven sleeve forming a torsional stop for the light load damper in both the pull and push directions. In order to achieve the installability of the stepped bolt as the main rivet, it is preferable to include through holes in the side plate and the flange of the driven sleeve. Since the engine torque also flows through the light-load internal damper after exceeding the light-load internal damper torque, a sufficiently firm torsional stop must be provided. Thus, a further twist stop may be provided in addition to the stepped bolt. The additional rotation stop can be formed by a plurality of lugs projecting from the side plate, which project into a wider recess (depression) of one of the driven flanges of the driven sleeve, which recess is arranged according to the rotation angle of the light-load internal damper. The rotation stop is achieved by the contact of the lug on the side of the recess. Preferably, the lugs are also arranged symmetrically in the two side plates. All the rotation stops preferably act simultaneously.
A torsional vibration damper is provided in which a torque limiter is arranged outside a damper chamber (accommodating chamber) and thus always operates dry.
Drawings
Embodiments of the present invention are described in detail below with reference to the accompanying drawings. Additional features and advantages will be derived from the description. The specific features of this embodiment may present general features of the invention. Features of this embodiment in combination with other features may also present various features of the invention.
Schematically and exemplarily shown:
fig. 1 shows a partial sectional view of a torsional vibration damper, wherein the sectional view cuts through the compression spring of the inner damper,
FIG. 2 shows a further partial sectional view of the torsional vibration damper in FIG. 1, wherein the sectional view cuts a torsional stop for defining the torsion angle of the internal vibration damper, and
fig. 3 shows a partial plan view of the torsional vibration damper of fig. 1, wherein the toothing of the driven sleeve is not shown.
Detailed Description
Fig. 1 and 2 show schematically and exemplarily a torsional vibration damper 100 designed as a dual-mass flywheel, which has an input part 102 and an output part 104. The input member 102 and the output member 104 have a common axis of rotation 106. The input member 102 and the output member 104 are rotatable together about an axis of rotation 106 and are capable of limited rotation relative to each other.
A spring-damper arrangement having an outer damper 108 and an inner damper 110 acts between the input part 102 and the output part 104. The outer damper 108 has a mechanical energy store designed as a curved spring 112 and a sliding cover 114. Internal shock absorber 110 has a mechanical accumulator designed to compress spring 116.
Torsional vibration damper 100 is intended to be arranged in the drive train of a vehicle having an internal combustion engine, for example a hybrid electric vehicle, in order to damp rotational irregularities in the drive train, in particular excited by the internal combustion engine.
The input part 102 has a hood-shaped input flange part 118 with a bottom region and an edge region, and a ring-disk-shaped input cover part 120. The input flange part 118 can be screwed radially on the inside to another component of the drive train, for example a crankshaft of an internal combustion engine, by means of screws 122. In this embodiment, the support plate 124 can be screwed together with the input flange part 118 by means of screws 122.
The input flange member 118 and the input cover member 120 define a receiving cavity 126 for the arcuate spring 112. The input flange member 118 and the input cover member 120 are preferably welded to each other radially outwardly. A substantially disc-shaped arcuate spring flange 128 is axially disposed between the bottom section of the input flange member 118 and the input cover member 120. An arcuate spring flange 128 is partially disposed in the receiving cavity 126.
The curved spring flange 128 has two diametrically opposed projections on the radial outside, which are not visible in the drawing due to the profile. The arcuate springs 112 of the outer damper 108 are supported on one side on the input flange member 118 and the input cover member 120 and on the other side on radially outer projections of the arcuate spring flanges 128.
The seal assembly seals the receiving cavity 126. The seal assembly has a friction ring 130 disposed axially between the radially inner edge of the arcuate spring flange 128 and the input flange member 118 and another friction ring 132 disposed axially between the arcuate spring flange 128 and the radially inner edge of the input cover member 120 and preloaded axially by a disc spring diaphragm 134.
The torsional vibration damper 100 has a friction device 136 that serves as a torque limiter. The friction device 136 serves to protect the torsional vibration damper 100 against excessive torques and, by limiting the torque which can be transmitted and which ensures operation, to prevent damage to the torsional vibration damper 100. By means of the friction device 136, torques up to a maximum torque can be transmitted in a frictionally engaged manner before the input part 102 and the output part 104. When the friction device 136 is loaded with a torque greater than the maximum torque, the torque transmission is reduced or interrupted. The friction device 136 is designed as a slip clutch.
The friction device 136 is integrated in the output part 104. The friction device 136 is fixedly connected to the arcuate spring flange 128 by means of a carrier flange 138. The carrier flange 138 is designed here in the form of a ring disk and is embodied in an axially stepped manner. The carrier flange 138 is riveted to the arcuate spring flange 128 by a plurality of rivets 140. The radially outer region of the carrier flange 138 is arranged axially on the side of the input cover part 120 facing away from the curved spring flange 128. The carrier flange 138 is disposed entirely outside of the receiving cavity 126.
The friction lining support cup 142 of the friction device 136 is fixedly connected to the radially outer region of the carrier flange 138. The friction lining support cup 142 is embodied in an axially stepped manner. The disk-shaped radially outer region of the friction lining support cup 142 is riveted to the radially outer region of the carrier flange 138 by means of a plurality of rivets 144. A cylindrical section of the friction lining support cup 142 is provided between a disk-shaped radially outer region of the friction lining support cup 142 and a disk-shaped radially inner region of the friction lining support cup 142, which is arranged offset from the radially outer region in the axial direction. The cylindrical section of the friction lining support cup 142 has at least one groove 146 extending in the axial direction.
The carrier flange 138 and the friction lining support cup 142, in this case the radially inner region of the friction lining support cup 142, form a radially inwardly open circumferential space in which the two outer friction linings 148, 150, the two inner friction linings 152, 154 and the disk spring 156 of the friction device 136 are arranged. The two inner friction plates 152, 154 are each provided in the radially outer region, preferably on both sides, with friction linings, which are made of paper or other friction material in particular. The carrier flange 138, the two outer friction disks 148, 150 and the two inner friction disks 152, 154 form a friction disk pack which is prestressed in the axial direction by means of a disk spring 156.
The two outer friction disks 148, 150 each have a projection on the radially outer side, which engages in the at least one axial groove 146. The outer friction disks 148, 150 are thus coupled to the friction disk support cup 142 in a rotationally fixed and axially displaceable manner. The radially outer region of the first inner friction disk 152 is disposed axially between the carrier flange 138 and the first outer friction disk 148. A radially outer region of the second inner friction plate 154 is disposed axially between the first outer friction plate 148 and the second outer friction plate 150. The disk spring 156 is supported on one side on the friction disk bearing cup 142 and on the other side on the second outer friction disk 150, so that the friction disk pack is prestressed in the axial direction. The maximum torque of the friction device 136 that can be transmitted from the friction disk support cup 142 via the outer friction disks 148, 150 to the inner friction disks 152, 154 is related to the pretensioning of the friction partners and the disk spring 156. The friction plate support cup 142 and the inner friction plates 152, 154 are able to rotate relative to one another about the axis of rotation 106 when a maximum torque is exceeded.
The inner friction plates 152, 154 of the friction device 136 also serve as side plates for the inner damper 110. A separately constructed side plate can therefore be dispensed with. The inner friction plates 152, 154 have a plurality of recesses for receiving one of the compression springs 116 of the inner damper 110, respectively. The radially outer region of the driven flange 160 of the driven sleeve 158, which is arranged axially between the radially inner regions of the inner friction disks 152, 154, likewise has a plurality of recesses each accommodating one of the compression springs 116 of the inner damper 110. Thus, the compression springs 116 of the inner damper 110 are supported on one side on the inner friction plates 152, 154 and on the other side on the driven flange 160, respectively. The inner friction disks 152, 154 and the driven flange 160 can rotate relative to one another to a limited extent about the axis of rotation 106 when the pretension of the compression spring 116 is changed. The driven sleeve 158 has gear teeth 162 for connecting the output part 104 to a shaft not shown in the drawings, in particular to a transmission input shaft aligned with the rotational axis 106 of the drive train.
The two inner friction plates 152, 154 are riveted to one another by means of stepped screws 164, spaced apart from one another in the axial direction. The two inner friction plates 152, 154 are axially positioned relative to each other by means of a stepped bolt 164. The stepped screw 164 extends through an opening 166 of the driven flange 160 in the radially outer region arranged axially between the inner friction disks 152, 154. This enables the inner friction plates 152, 154 and the driven flange 160 to rotate to a limited extent relative to one another about the axis of rotation 106. The angle of twist between the inner friction plates 152, 154 and the driven flange 160 is thus defined such that the stepped bolt 164 hits the periphery of the opening 166 when the maximum angle of twist is reached in both directions of rotation. The stepped bolt 164 and the associated opening 166 thus form a rotation stop 168, also referred to below as first rotation stop 168. Preferably, the torsional vibration damper 100 has a plurality of torsion stops 168, which are distributed in a particularly uniform manner over the circumference and which are each formed by the stepped screw 164 and the opening 166 in the driven flange 160.
The two inner friction disks 152, 154 also each have a pressure plate 170 which extends substantially in the axial direction and faces one another. The two pressure plates each engage a recess 172 in the driven flange 160 of the driven sleeve 158. The angle of twist between the inner friction disks 152, 154 and the driven flange 160 is additionally defined such that the pressure plate 170 in both rotational directions strikes the side faces 174 of the recess 172 when the maximum angle of twist is reached. Thereby providing an additional torsional stop 176 for limiting relative rotational movement between the inner friction plates 152, 154 and the driven flange 160 of the driven sleeve 158. Preferably, the torsional vibration damper 100 has a plurality of such further torsional stops 176, which are formed in each case by the pressure plate 170 and the recess 172, which are distributed in a particularly uniform manner over the circumference.
The first torque stop 168 (or first torque stops 168) and the additional torque stop 176 (or additional torque stops 176) collectively define the relative rotatability between the inner friction plates 152, 154 and the driven sleeve 158. In a modification of this embodiment, the torsional vibration damper has only a first torsion stop 168 for defining the torsion angle. In a further variant of this embodiment, the torsional vibration damper has only a further torsional stop 176 for defining the torsional angle.
List of reference numerals
100 torsional vibration damper
102 input unit
104 output member
106 axis of rotation
108 external vibration damper
110 internal vibration damper
112 arc spring
114 sliding cover
116 compression spring
118 input flange component
120 input cover part
122 screw
124 support plate
126 accommodating cavity
128 arc spring flange
130 friction ring
132 friction ring
134 disc spring diaphragm
136 friction device
138 carrier flange
140 rivet
142 friction plate support cup
144 rivet
146 groove
148 outer friction plate
150 outer friction plate
152 inner friction plate
154 inner friction plate
156 coil spring
158 driven socket
160 driven flange
162 gear shaping
164 step bolt
166 opening
168 twist stop
170 pressing plate
172 concave part
174 side surface
176 twist the stop.

Claims (10)

1. A torsional vibration damper (100), in particular a dual mass flywheel, the torsional vibration damper (100) having an input part (102) and an output part (104), a spring damper device acting between the input part (102) and the output part (104), and a friction device (136) acting as a torque limiter between the input part (102) and the output part (104), the input part (102) and the output part (104) have a common axis of rotation (106), are rotatable together about the axis of rotation and are rotatable to a limited extent relative to one another, the spring-damper arrangement has at least one mechanical energy store, in particular a curved spring (112), arranged in a receiving space (126), characterized in that the friction means (136) are arranged outside the housing chamber (126).
2. The torsional vibration damper (100) according to claim 1, characterized in that the spring damper arrangement can have an external damper (108), wherein the external damper (108) has at least one mechanical energy store arranged in the receiving chamber (126).
3. The torsional vibration damper (100) according to claim 1 or 2, characterized in that the spring-damper arrangement has an internal damper (110), wherein the internal damper (110) has at least one mechanical energy store, in particular a compression spring (116), which is arranged outside the receiving space (126).
4. The torsional vibration damper (100) as claimed in claim 3, characterized in that the friction device (136) has a friction lining cup (142), at least one outer friction lining (148, 150) which is guided on the friction lining cup (142) in an axially displaceable manner and is connected to the friction lining cup (142) in a rotationally fixed manner, and at least one inner friction lining (152, 154) which is braced against the outer friction lining (148, 150) by means of a pretensioned force store, in particular a coil spring (156), wherein the at least one inner friction lining (152, 154) and at least one mechanical energy store of the inner damper (110) which is arranged outside the receiving space (126) are supported against one another in the circumferential direction.
5. Torsional vibration damper (100) according to at least one of the preceding claims, characterized in that the friction device (136) has two outer friction plates (148, 150), two inner friction plates (152, 154) and a carrier flange (138), wherein the two inner friction plates (152, 154) on the one hand and the first end region of at least one mechanical energy accumulator of the inner damper (110) on the other hand, which is arranged outside the receiving space (126), bear against one another in the circumferential direction.
6. A torsional vibration damper (100) as claimed in claim 5, characterized in that one of the two inner friction plates (152, 154) is arranged between the two outer friction plates (148, 150) and the other of the two inner friction plates (152, 154) is arranged between the carrier flange (138) and one of the two outer friction plates (148, 150).
7. The torsional vibration damper (100) as claimed in claim 5 or 6, characterized in that a second end region of the at least one mechanical energy accumulator of the internal vibration damper (110) which is arranged outside the receiving chamber (126) and a driven sleeve (158) which can be rotated to a limited extent about the rotational axis (106) relative to the at least one inner friction disk (152, 154) are supported on one another in the circumferential direction.
8. The torsional vibration damper (100) as claimed in claim 7, characterized in that at least one bolt, in particular a stepped bolt (164), is arranged at least partially axially between the two inner friction plates (152, 154), in particular the two inner friction plates (152, 154) are positioned axially opposite one another by means of the bolt, wherein the bolt passes through an opening (166) in the driven sleeve (158) and in particular serves as a first torsional stop (168) which defines the relative rotatability between the at least one inner friction plate (152, 154) and the driven sleeve (158).
9. The torsional vibration damper (100) as set forth in claim 7 or 8, characterized in that the at least one inner friction plate (152, 154) has at least one pressure plate (170) which engages into a recess (172) of the driven sleeve (158) and which serves as a further torsional stop (176) defining the relative rotatability between the at least one inner friction plate (152, 154) and the driven sleeve (158).
10. A torsional vibration damper (1) as claimed in claims 8 and 9, characterized in that the first torsion stop (168) and the further torsion stop (176) jointly define a relative rotatability between the at least one inner friction plate (152, 154) and the driven sleeve (158).
CN202111069971.8A 2020-09-14 2021-09-13 Torsional vibration damper Pending CN114183499A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020123817.7A DE102020123817A1 (en) 2020-09-14 2020-09-14 torsional vibration damper
DE102020123817.7 2020-09-14

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CN114183499A true CN114183499A (en) 2022-03-15

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DE (1) DE102020123817A1 (en)

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016223413A1 (en) 2015-11-30 2017-06-01 Schaeffler Technologies AG & Co. KG Dual mass flywheel with friction control disc
DE102018128996A1 (en) 2017-12-06 2019-06-06 Schaeffler Technologies AG & Co. KG torsional vibration dampers

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