WO2014135143A1 - Dispositif de friction pour un amortisseur de vibrations de torsion - Google Patents

Dispositif de friction pour un amortisseur de vibrations de torsion Download PDF

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Publication number
WO2014135143A1
WO2014135143A1 PCT/DE2014/000090 DE2014000090W WO2014135143A1 WO 2014135143 A1 WO2014135143 A1 WO 2014135143A1 DE 2014000090 W DE2014000090 W DE 2014000090W WO 2014135143 A1 WO2014135143 A1 WO 2014135143A1
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WO
WIPO (PCT)
Prior art keywords
friction
torsional vibration
vibration damper
primary
friction element
Prior art date
Application number
PCT/DE2014/000090
Other languages
German (de)
English (en)
Inventor
Ulrich Rohs
Original Assignee
Ulrich Rohs
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Ulrich Rohs filed Critical Ulrich Rohs
Priority to CN201480001733.5A priority Critical patent/CN104508319B/zh
Priority to DE112014001174.6T priority patent/DE112014001174A5/de
Publication of WO2014135143A1 publication Critical patent/WO2014135143A1/fr

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Classifications

    • 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
    • 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
    • F16F15/1395—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 characterised by main friction means acting radially outside the circumferential lines of action of the elastic members
    • 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

Definitions

  • the invention relates to a friction device for a torsional vibration damper and a torsional vibration damper and a method for mounting a friction device and a method for operating a torsional vibration damper.
  • Torsional vibration dampers are known in a wide variety of concrete embodiments. They have a primary mass or primary side and a secondary mass or secondary side, the secondary side being rotationally movable with respect to the primary side and a spring-damper device acting between the primary side and the secondary side being provided.
  • a central task in the design of torsional vibration dampers is, in particular, to influence the damping properties as a function of the respective operating state, that is to say in particular as a function of the relative rotation between the primary side and the secondary side. So one is usually anxious to provide a comparatively high damping at comparatively large rotational amplitudes between the primary side and secondary side.
  • a comparatively high damping is provided at rotational speeds or rotational frequencies at which the respective system - with which the torsional vibration damper is in mechanical operative connection - reaches the resonance region.
  • Known torsional vibration dampers are adapted in only a limited way to provide a damping adapted to the respective operating state. For example, e.g. From EP 1 058 028 A2 a torsional vibration damper with a friction device is known, which comprises a dragging wedge for damping adaptation.
  • a damping device for a dual mass flywheel in which a plurality of components are provided which are pressed together with a rotation of the two masses as a result of the provision of mutually slidable wedge surfaces between the masses and in pressed together state a friction between provide the two rotating masses rotating relative to each other.
  • the damper part of the known from WO 2005/064198 AI dual mass clutch flywheel is based on components with wedge surfaces.
  • a torsional vibration damper is known in which the friction device is annular.
  • the present invention has for its object to provide an alternative friction device for a torsional vibration damper, with which on the torsional vibration damper in a simple and practical way desired damping properties can be realized.
  • the inlet slopes and the design of the primary-side control of the same material as the friction element for the first time allow a correspondingly good decoupling, which then leads to an operation of the torsional vibration damper with correspondingly small hystereses.
  • the friction device can have at least two friction elements, which can be moved independently of one another about a main rotational axis, at least in the circumferential direction, and which can be actuated via a drive on the outside. Furthermore, complementary secondary-side friction surfaces can be provided, which can be controlled via a secondary-side control and to which a respective friction element is rubbed.
  • the primary-side control for driving the friction elements is arranged to transmit torque of the primary side or the primary mass of the torsional vibration damper on the friction elements.
  • the secondary-side drive is provided for driving the secondary-side friction surfaces and in particular configured to transmit torque from the secondary side or the secondary mass to the secondary-side friction surfaces and thus to the friction elements.
  • the friction elements are rubbing against the complementary secondary-side friction surfaces and cause damping by sliding rubbing against the complementary secondary-side friction surfaces, namely in the presence of relative rotation between the primary side and the secondary side, and particularly preferably when they are present or exceeded one of the secondary-side drive for the respective friction element predetermined angle of rotation between the primary side and the secondary side.
  • the friction surfaces and the surface regions of the friction elements resting on the friction surfaces are aligned radially and in the circumferential direction relative to the main axis of rotation.
  • This has the advantage that the frictional forces acting between the secondary-side friction surfaces and the friction elements or the surface regions are independent of the rotational speeds or rotational frequencies of the primary side or secondary side in the first order or first approximation since there are no centrifugal forces in the direction of the corresponding normal force Act.
  • the friction surfaces are arranged on a common friction disc.
  • a compact friction device having a simple structure can be advantageously provided.
  • a simple and compact friction device allows in particular a simple assembly and possibly also a correspondingly easy disassembly of the friction device.
  • the primary-side control has a radially inwardly acting centrifugal force compensation for at least one of the friction elements.
  • the primary-side control comprises a control disk with at least one recess in which a friction element is arranged, wherein the recess is larger in the circumferential direction about the main axis of rotation than the corresponding extent of the friction element arranged in it.
  • control disk as a primary-side control rotatably connected to the primary side or the primary mass or operatively connected to this.
  • a primary-side drive can be provided, in which only when exceeding or existing for the respective friction element predetermined rotation angle or predetermined minimum rotation angle between the primary side and the secondary side - which depends on the extension of the corresponding recess in the circumferential direction - uses a rubbing or sliding rubbing of the respective friction element on the friction surfaces, that uses a damping caused by the respective friction element.
  • the friction element In the presence of the damping caused by the friction element, the friction element is then preferably in contact with a stop surface bounding the respective recess in the circumferential direction or in contact with a stop region delimiting the respective recess in the circumferential direction. Only on contact with this stop surface or the stop area can then transmit the control disk torque of the primary side to the respective friction element to bring about a damping by rubbing the respective friction element on the friction surfaces.
  • the control disk can also be firmly connected to at least one friction element, so that even at very small non-zero angles of rotation between the primary side and the secondary side rubbing or a frictional movement of the friction element on the friction surfaces occurs.
  • a basic friction can be provided, which can be advantageous in particular in the operation of the torsional vibration damper in very high speed ranges.
  • At least two recesses may be provided in the control disk, in each of which a friction element is arranged, wherein the difference between the size of the recess in the circumferential direction and the corresponding extension of each arranged in her friction element for the Both recesses is different. Since the predetermined for the respective friction element torsional angle or predetermined minimum angle of rotation between the primary side and the secondary side of the extension of the corresponding recess in the circumferential direction depends (see above), by providing the different or variable difference between the size the recess in the circumferential direction and the corresponding extent of each arranged in their friction element a stepwise reinforcement of the friction or damping are provided.
  • the stepwise reinforcement of the friction or damping is possible because due to the variable difference, the frictional effect or damping effect of the friction elements at different angles of rotation between the primary side and the secondary side begins.
  • By providing the stepwise reinforcement of the friction it is advantageously possible to provide an attenuation behavior that is individually matched to the respective system.
  • the recess has radially inwardly facing guide surfaces for interaction with associated radially outwardly facing surfaces of the friction element disposed in the recess. In this way can be advantageously very effectively avoided unwanted movement of the friction elements radially outward.
  • the recess and the friction element arranged in it have at least one circumferentially effective inlet bevel.
  • the provision of the inlet slopes allows for a suitable alignment of the inlet slopes an advantageous centrifugal force compensation.
  • the circumferentially effective inlet slopes also advantageously allows a slow shrinkage of the friction element in the respective stop position, ie in the position in which the friction element is in contact with the recess in the circumferential direction limiting stop surface or in contact with a the respective recess is in the circumferential direction limiting stop area (see also above). Due to the slow shrinkage in particular rattling noises or a very gurartiges onset of the corresponding friction can be advantageously minimized.
  • a pressing which presses the friction elements against the friction surfaces.
  • a contact pressure as such arises that the friction elements with the corresponding friction surfaces are in a defined frictional contact.
  • a common contact causes on the one hand an advantageous uniform contact pressure of the friction elements, which in turn has the consequence that the friction elements in the axial direction - in contrast to the independent mobility in the circumferential direction - are movable identically in the first approximation. This identical mobility advantageously promotes a uniform frictional movement.
  • a simple structure can advantageously also be realized for the friction device according to the invention.
  • a simply constructed friction device allows in particular a simple assembly and disassembly of the same.
  • a friction device for a torsional vibration damper with at least one friction element which can be controlled via a primary-side drive, are characterized in that the friction element or an axially acting on the friction element pressure element has an axial projection, and a complementary secondary side friction surface, which can be controlled via a secondary-side control and on which the friction element is pressed by means of a pressing action acting on the axial projection in a frictional manner.
  • the axial projection in conjunction with the pressure acting on this can be advantageously provided a defined friction by a defined contact force, with a defined friction in turn is advantageously associated with a defined damping of the respective system.
  • the axial projection can point away in the direction of the friction element or else also away from the friction element and preferably defines a point of application at which the contact pressure of the contact pressure defines, which then leads accordingly to a defined friction.
  • the contact pressure comprises a plate spring.
  • a contact pressure which includes a plate spring, causes on the one hand an advantageous uniform contact pressure of the friction elements, which in turn has the consequence that the friction elements in the axial direction - in contrast to the independent mobility in the circumferential direction - are movable identically in the first approximation. This identical mobility advantageously promotes a uniform frictional movement.
  • the plate spring can be realized for the friction device according to the invention advantageously also a simple structure.
  • a simple design friction device allows in particular a simple assembly and possibly also a corresponding simple disassembly of the same.
  • the plate spring acts directly on the axial projection, along with a very effective and compact construction contact pressure of the friction element to the complementary secondary side friction surface.
  • a friction device for a torsional vibration damper with at least one friction element characterized in that the friction element can be controlled via a primary-side drive of the same material as the friction element and a complementary secondary side friction surface, which can be controlled via a secondary side drive , rubbing against.
  • the at least one friction element can be controlled via a primary-side control of the same material as the friction element, along with the advantageous effect that a defined friction between the primary-side drive and the friction element is provided.
  • a suitable design of the friction element and the primary-side activation as a result of the provision of the same material advantageously a significant wear minimization can be provided.
  • the friction element consists of metal, preferably with hardened or rolled contact areas between the friction element and the drive, or of plastic.
  • the formation of the friction element made of metal, preferably with hardened or rolled contact areas between the friction element and the drive, is advantageously associated with a wear-minimizing effect.
  • To provide a formed of plastic friction has the advantage that rattling and concomitant "rattling noises" can be avoided or significantly minimized.
  • the primary-side drive in the vicinity of the friction surface in the axial direction is thinner than the friction element. Due to this thinner design of the primary-side control in the vicinity of the friction surface, any friction of the primary-side control is advantageously avoided.
  • the primary-side drive may in particular be formed in one piece, wherein an integrally formed primary-side control in a simple and practical way z. B. can be produced by injection molding of a sprayable material.
  • a torsional vibration damper that mates with the friction device may include a primary side and a secondary side or secondary mass rotatable about a main rotational axis of the torsional vibration damper with respect to the primary side, and a spring-damper device having a corresponding friction device acting between the primary side and the secondary side include.
  • the primary-side control is positively mounted axially on the primary side.
  • the intended attachability allows easy assembly and disassembly, the positive attachment of the control in any friction of a torsional vibration damper in terms of ease of assembly and disassembly can be beneficial.
  • the spring-damper device can be made viscous Liquid comprising spring means and a sealed against the viscous fluid of the spring means friction device.
  • the viscous liquid advantageously serve as a lubricant and / or for viscous damping.
  • the sealing of the friction device with respect to the lubricant advantageously ensures the formation of a defined friction for setting desired or adapted damping properties.
  • the friction device is sealed by a non-contact seal.
  • a non-contact seal or by providing a labyrinth seal advantageously undesirable or uncontrolled friction can be avoided.
  • the friction device is particularly preferably arranged in a fluid path between the spring device and a bearing, preferably a sliding bearing, between the primary side and the secondary side.
  • a bearing preferably a sliding bearing
  • the spring Damper device using a spring system have a static characteristic curve which has a hysteresis of less than 15 Nm or less than 10% of the maximum engine torque within 90% of the maximum angle of rotation or within an angle of rotation of less than ⁇ 10 °.
  • a static characteristic here means a characteristic at very low speed, specifically at a speed at which centrifugal forces are negligible.
  • the provided within the limits hysteresis less than 15 Nm and less than 10% of the maximum engine torque advantageously allows the formation of a defined friction, which is correspondingly effectively defined especially at high frequencies and independent of the spring system.
  • the angle of rotation is the angle of rotation or angle of rotation between the primary side and the secondary side. The consequence of such a low friction by the spring system of the spring-damper device is that the friction is provided substantially by the friction system of the spring-damper device.
  • the definition of the hysteresis of the spring system is advantageous because a friction system with a suitable design of the spring-damper device can certainly be removed, shut down or bypassed to perform appropriate measurements, while removing the spring system ultimately to a complete change in the function of the torsional vibration damper and thus lead to non-comparable measurement results.
  • the hysteresis is less than 13 Nm or less than 8% of the maximum engine torque, preferably less than 10 Nm or less than 7% of the maximum engine torque.
  • the spring-damper device comprises a spring system with a dynamic characteristic curve, which within 90% of the maximum rotation angle or within a rotation angle of less than ⁇ 10 °, a hysteresis less than 25 Nm and less than 15% of the maximum engine torque.
  • a dynamic characteristic curve is understood to mean a characteristic curve at the maximum rotational speed of the respective drive system.
  • the hysteresis of the dynamic characteristic especially in engines with a maximum torque of 200 Nm, less than 50 Nm, preferably less than 40 Nm.
  • the hysteresis of the dynamic characteristic especially in motors with different power, less than 17% of the maximum engine torque, preferably less than 10% of the maximum engine torque, which accordingly leads to a good decoupling especially at high speeds or at high frequencies.
  • the abovementioned absolute values refer in particular to motors with low power, in particular with a torque of 200 Nm.
  • the relative values are more general and, in particular, also sufficient for engines with higher power, whereby, of course, the lower absolute values may of course be correspondingly advantageous, since then an even better decoupling is present.
  • a friction device contributes more than 300 Nm, preferably more than 400 Nm or more than 500 Nm, to the damping, the proportion of the rest of the system, in particular of the Spring system can then turn out correspondingly low.
  • At least one friction element and an associated control of the friction device can first be integrally connected to one another and be separated from one another after the positioning or during the positioning of the friction element.
  • a very simple assembly can be carried out in the connected state thus provided, which would be much more complicated and cumbersome without the existing connection.
  • the drive Only with or after completion of the assembly, where the friction element is positioned, is the drive, which is preferably connected to the at least one friction element by at least one material web, separated from the at least one friction element. If a connection is preferably provided via the at least one material web, it is severed to separate the actuation from the at least one friction element during positioning or after positioning.
  • the severing can be done for example by an offset between the friction element and control before assembly, which is then changed by the assembly, or by a first offset during commissioning.
  • a control of the friction device for a friction element of the friction device can be plugged axially onto a primary side of a torsional vibration damper in a form-fitting manner.
  • the attachment of the control on the Primary side can be carried out in a simple and practical way and therefore allows easy assembly and disassembly of the friction device.
  • the positive axial attachment also creates a secure rotationally fixed connection between the control and the primary side.
  • FIG. 1 is a sectional view (radial section) of a first embodiment of a torsional vibration damper according to the invention
  • FIG. 2A and B are each a plan view of the friction device of the torsional vibration damper shown in Fig. 1,
  • FIG. 3 is a plan view of a second embodiment of a torsional vibration damper according to the invention, which differs from that shown in FIG. 1 in that four springs and four flyer rings are provided instead of three springs and three flyer rings in this embodiment.
  • FIG. 4 is an enlarged view of a detail of Fig. 2A
  • FIG. 5 is an enlarged view of a detail of Fig. 1,
  • FIG. 6 is a sectional view (radial section) of a third embodiment of a torsional vibration damper according to the invention.
  • FIG. 7 is a sectional view (radial section) of a portion of a fourth embodiment of a torsional vibration damper according to the invention.
  • FIG. 8 is a plan view of an alternative friction device for a torsional vibration damper
  • FIG. 9 is a sectional view (radial section) of the friction device of FIG. 8
  • 10A to 10D are each a perspective view, a plan view and sectional views (radial sections) of primary-side drives, which consist of the same material as the friction elements also shown,
  • 1 1A to 1 IC are each a plan view, sectional views (radial sections) and a detailed representation (radial section) of a primary-side control with unilaterally open recesses, together with friction elements and a secondary-side friction disc
  • 12 shows a plan view of a primary-side activation together with friction elements, which differs from that shown in FIG. 11, in particular in that, in this activation, no receptacle is provided for the positive axial attachment to the primary side
  • 13A and 13B are a plan view and a sectional view (radial section) of a friction device together with the springs of the spring-damper device of the torsional vibration damper,
  • FIG. 15 shows a static characteristic of an overall system from the spring system with the characteristic curve according to FIG. 14 and an exemplary friction system
  • FIG. 1 shows a radial section of a first exemplary embodiment of a torsional vibration damper 10.
  • the torsional vibration damper 10 comprises a primary side 12 or primary mass 12, a secondary side 16 or secondary mass 16 which is rotatable about a main rotational axis 14 of the torsional vibration damper 10 with respect to the primary side 12 and an effective between the primary side 12 and the secondary side 16 spring-damper device 18 with a friction device 20 according to the invention as a torsional vibration damper 10, which is intended for use in a motor vehicle, the secondary side 16 is provided for contact with a clutch of the motor vehicle , and the primary side 12 has bores 22 for producing a screw connection with the crankshaft of the motor vehicle. Further, a starter ring gear 13 is provided on the primary side 12.
  • the friction device 20 comprises eight (see also FIGS. 2A and B) in the circumferential direction about the main rotation axis 14 (see FIG. 1) independently movable friction elements 26, which comprise a primary-side drive 28, which comprises a control disk 28, can be controlled, and complementary secondary-side friction surfaces 30, which can be controlled via a secondary-side drive 32 and to each of which a friction element 26 rubbing.
  • the control disk 28 is thinner in the axial direction than the friction elements 26 in the vicinity of the friction surfaces 30.
  • the secondary-side drive 32 comprises, on the one hand, a housing 38 composed of two sheet metal parts 34, 36 made of a sheet metal material, wherein a first housing part 34 is designed in the form of a common friction disk 34, on which the friction elements 26 are arranged. Furthermore, the secondary-side drive 32 comprises a contact pressure in the form of a plate spring 40 and a rotationally fixed connection to the secondary side 16.
  • two complementary secondary-side friction surfaces 30 are provided, wherein one of the friction surfaces 30 is provided on the friction disk 34 and the other friction surface 30 on the disk spring 40. On both friction surfaces 30, the friction elements 26 rub against.
  • the friction surfaces 30 and the frictionally abutting the friction surfaces 30 surface portions 42 of the friction elements 26 are aligned radially and circumferentially to the main axis of rotation 14.
  • the plate spring 40 is provided as a common contact pressure to press all the friction elements 26 against the provided on the friction plate 34 friction surface 30, as shown in particular in FIG. 5, which shows an enlarged view of a corresponding detail of FIG. The enlarged view is best seen that the friction elements 26 have an axial projection 44 on which the plate spring 40 acts directly.
  • FIGS. 2A and 2B each show a plan view of the friction device 20 of the torsional vibration damper 10 shown in FIG. 1.
  • the structure of the control disk 28 is particularly apparent from these figures.
  • the control disk 28, which is rotatably connected to the primary side 12, has eight recesses 46, wherein in each recess 46, a single friction element 26 (see FIG. 4) is arranged.
  • Each of the recesses 46 is larger in the circumferential direction about the main axis of rotation 14 than the corresponding extent of the friction element 26 arranged in it.
  • the control disk 28 has a recess 48 in the form of a hexagon 48.
  • a center piece 50 designed to be complementary to this recess 48 is provided, which can be inserted axially into the recess 48 in a positive-locking manner so that the control disk 28 is mounted in a form-fitting manner axially on the primary side 12 or the center piece 50 (cf. Fig. 1).
  • a primary-side drive 28 can be provided, in which only for the respective friction element is exceeded or present 26 predefined angle of rotation or predetermined minimum angle of rotation between the primary side 12 and the secondary side 16 - the angle of rotation depends on the extent of the corresponding recess 46 in the circumferential direction - a rubbing or sliding Rubbing of the respective friction element 26 on the friction surfaces 30 sets, so uses a caused by the respective friction element 26 damping.
  • the friction element 26 is in contact with a stop surface 52 delimiting the respective recess 46 in the circumferential direction. Only upon contact with this stop surface 52 can the control disk 28 "take along" the respective friction element or torque the primary side 12 transmitted to the respective friction element 26 in order to bring about a damping by rubbing the respective friction element 26 on the friction surfaces 30.
  • FIG. 2B illustrates the situation where a damping effect due to the existing contact of the friction member 26 with the stopper surface 52 is caused by the uppermost and lowermost friction member 26 in FIG. 2B.
  • the angle of rotation or the minimum angle of rotation is not or not yet reached, so that no rubbing of the friction elements 26 takes place on the friction surfaces 30 and these friction elements 26 therefore do not contribute to the damping.
  • FIG. 2A illustrates the situation in which for none of the friction elements 26 is the angle of rotation or the minimum angle of rotation achieved, so that there is still no damping effect due to friction element friction.
  • Each of the recesses 46 and the friction element 26 arranged in it have two inlet diameters 54 which are effective in the circumferential direction (cf., for example, FIG. 2A, right and FIG. 4).
  • the provision of the inlet slopes 54 allows for an advantageous centrifugal force compensation for the friction elements 26.
  • Femer is also provided by providing the circumferentially effective inlet slopes 54 a slow running of the friction element 26 in the respective stop position, ie in the position in which the friction element 26 is in contact with the recess 46 in the circumferential direction limiting stop surface 52 is located.
  • a frictional contact of the friction elements 26 with secondary-side regions or secondary-side surface regions as a result of centrifugal force can advantageously be avoided or substantially reduced when driving by means of the primary-side control 28 the secondary-side surface areas in the embodiment shown here around the circumferentially extending surface 56 of the second housing part 36 of the housing 38 of the secondary-side drive 32 (see also Fig. 1, and in particular also Fig. 4, which shows an enlarged view of an area in the vicinity of a friction element 26 from Fig. 2A).
  • the spring-damper device 18 (see Fig. 1) comprises a spring device 60, which has a viscous liquid or a lubricant, wherein the friction device 20 is sealed against the lubricant of the spring device 60.
  • the friction device 20 is in this case arranged in a fluid path between the spring device 60 and a slide bearing 62, via which the secondary side 16 is rotatably mounted on the primary side 12.
  • the friction device 20 is sealed by a non-contact seal 64 in the manner of a labyrinth seal, which is in the form of an integrally formed on the friction plate 34 projection 64 which extends from the friction disc 34 radially inward and thereby penetration of the lubricant in the friction device 20 avoids which can be pressed radially outward due to the centrifugal force.
  • Fig. 3 shows a top view of a second embodiment of a torsional vibration damper 10, which differs from that shown in Fig. 1 in that instead of three springs 66 and three flyer rings 68 in this embodiment, four springs 66 and four flyer rings 68 are provided are.
  • the flyer rings 68 serve to hold down the springs 66 of the spring-damper device 18 in order to compensate for or counteract the centrifugal forces.
  • FIG. 6 shows a radial section of a third embodiment of a torsional vibration damper 10.
  • the torsional vibration damper 10 shown here differs from that shown in FIG. 1, inter alia, in that a rivet connection 70 is provided for the rotationally fixed connection of the control disk 28 to the primary side 12 is.
  • the axial projection 44 on the friction elements 26 in the axial direction is larger or more clearly formed than in the friction device 20 of the torsional vibration damper 10 shown in FIG. 1.
  • the two housing parts 34, 36 of the housing 38 of the friction device 20 are formed radially inwardly extended , in analogy to the Embodiment of FIG. 1 form a non-contact seal in the manner of a labyrinth seal for sealing the friction device 20 against the lubricant of the spring device 60.
  • FIG. 7 shows a radial section of a partial region of a fourth exemplary embodiment of a torsional vibration damper 10, the partial region illustrating the friction device 20 of this fourth exemplary embodiment in more detail.
  • an axially acting on the friction elements 26 pressure element 72 is provided with an axial projection 44.
  • the friction elements 26 abut against a complementary secondary-side friction surface 30 of the friction disk 34, wherein the friction elements 26 abut on the axial projection 44 acting pressing in the form of a plate spring rubbing frictionally.
  • FIG. 8 shows a plan view of an alternative friction device 20 for a torsional vibration damper.
  • lenticular frictional elements 26 are provided here, which are each arranged in a recess 46 of a control disk 28 which is open on one side, each of the recesses 46 being open towards a secondary-side annular region 74.
  • this friction device 20 in the case of a relative movement between the primary side and the secondary side, the friction elements 26 are rubbed against secondary-side inner surfaces 78 of the annular region 74 as a result of centrifugal force and run into the slopes of the inlet slopes. Even a damping provided in this way may be advantageous in certain applications.
  • FIG. 9 shows a radial section of the friction device 20 of FIG. 8.
  • a pressure element 72 acting axially on the friction elements 26 is also provided with an axial projection 44.
  • the friction elements 26 abut against a complementary secondary-side friction surface 30, wherein the friction elements 26 abut on the pressure acting on the axial projection 44 in the form of a plate spring 40 rubbing frictionally.
  • FIGS. 10A to 10D each show a perspective view, a plan view and radial sections of two further primary-side actuators 28, which each comprise a control disk 28, which consist of the same material as the friction elements 26 likewise shown.
  • each control disk 28 has a recess 48 or receptacle 48, which is of a circumferential wavy boundary 80 is limited.
  • the differences between the control disks 28 which can not be seen in FIGS. 10A and 10B can be seen from the radial sections (see FIGS. 10C and 10D), which show that, with the exception of one friction element 26, all friction elements 26 on both control disks 28 Material webs 82 are connected to the control discs 28. Furthermore, it can be seen from FIG.
  • control disks 28 according to FIG. 10C and 10D are suitable for different embodiments of the method according to the invention for mounting a friction device.
  • the friction members 26 and the control disk 28 are first integrally connected with each other as shown in FIG. 10C, and after the friction members 26 are positioned, the control disk 28 and the friction members 26 are separated from each other during running operation a relative rotation between the primary side and the secondary side, in which the material webs 82 tear.
  • the separation of control disc 28 and friction elements 26 already takes place during positioning, since during positioning the material webs 82 tear as a result of the axial offset.
  • a friction element 26 (in the figures, the right outer one) is integral with the respective control disk 28 and is thus firmly connected to it in order to provide a basic friction in very high speed ranges and at to provide very small rotational amplitudes.
  • a radially inwardly acting centrifugal force compensation for the friction elements 26 is provided in that for each recess 46, a radially outer boundary 84 is provided, which extends in the circumferential direction.
  • a possibly disadvantageous circumferential rubbing of the friction element 26 at the boundary 84 may take place in the case of the centrifugal force compensation provided here, in particular during return movements or reverse rotations.
  • FIGS. 1A to 1C each show a plan view, radial sections and a detailed representation in the form of a radial section of a primary-side control 28, which comprises a control disk 28 with recesses 46 open on one side, together with friction elements 26 and a secondary-side friction disk 34.
  • the control disk 28 shown here also has a recess 48 or receptacle 48 for positive axial attachment to the primary side, which recess is delimited by a circumferential wavy boundary 80, wherein the friction elements 26 each have a recess 46 open on one side the control disk 28 are arranged and also as an assembly aid a one-piece connection Uber material webs 82 is provided.
  • a friction member 26 for providing a base friction is integral with the control disk 28.
  • the friction members 26 are not illustrated, however, to be taken from the radial cuts is that the primary-side control disc 28 and the secondary-side friction plate 34 are also integrally connected to provide a mounting aid material webs 86 which can tear during assembly or after assembly in the presence of relative rotation between the primary side and secondary side.
  • FIG. 12 shows a plan view of a primary-side drive 28, which comprises a control disk 28, together with friction elements 26, wherein the control disk 28 differs from that shown in FIG. 11 inter alia in that no control disk 28 is provided Recording is provided for positive axial attachment to the primary side.
  • FIG. 12 also shows six primary bores 22 (analogous to FIG. 3) for producing a screw connection with the crankshaft of the respective motor vehicle.
  • Figs. 13A and 13B show a plan view and a radial section of a friction device 20 together with the springs 66 of the spring-damper mechanism of the corresponding torsional vibration damper.
  • the springs 66 of the spring-damper device of the torsional vibration damper are arranged radially inwardly relative to the friction elements 26 here.
  • the spring device 60 contributes as little as possible to the friction and the friction is mainly caused by the friction device 20.
  • a correspondingly advantageous design of the spring device 60 is shown by way of example in FIGS. 14 to 16, wherein the friction device 60 according to FIG. 14 has a hysteresis of less than 20 Nm in the range of 90% of the maximum deflection and, by the way, an even lower hysteresis.

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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)
  • Vibration Prevention Devices (AREA)

Abstract

L'invention concerne un dispositif de friction (20) pour un amortisseur de vibrations de torsion (10) comprenant au moins deux éléments de friction (26) à mouvement indépendant au moins dans le sens périphérique autour d'un axe de rotation principal (14), ces éléments de friction pouvant être entraînés par une commande (28) côté primaire, ainsi que des surfaces de friction (30) complémentaires côté secondaire, lesquelles peuvent être entraînées par une commande (32) côté secondaire et contre lesquelles appuie en friction un élément de friction (26) respectif. L'invention concerne en outre un amortisseur de vibrations de torsion et un procédé de montage d'un dispositif de friction d'un amortisseur de vibrations de torsion.
PCT/DE2014/000090 2013-03-05 2014-03-05 Dispositif de friction pour un amortisseur de vibrations de torsion WO2014135143A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201480001733.5A CN104508319B (zh) 2013-03-05 2014-03-05 用于扭振减振器的摩擦装置
DE112014001174.6T DE112014001174A5 (de) 2013-03-05 2014-03-05 Reibeinrichtung für einen Torsionsschwingungsdämpfer sowie Torsionsschwingungsdämpfer und Verfahren zur Montage einer Reibeinrichtung sowie Verfahren zum Betrieb eines Torsionsschwingungsdämpfers

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013003628.3A DE102013003628A1 (de) 2013-03-05 2013-03-05 Reibeinrichtung für einen Torsionsschwingungsdämpfer sowie Torsionsschwingungsdämpfer und Verfahren zur Montage einer Reibeinrichtung
DE102013003628.3 2013-03-05

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WO2014135143A1 true WO2014135143A1 (fr) 2014-09-12

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Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3096100B1 (fr) * 2019-05-16 2022-07-22 Valeo Embrayages Dispositif de transmission de couple équipé d’un moyen de rétention

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1575746B1 (de) * 1966-05-06 1970-04-23 Borg Warner Drehelastische Kupplung
DE3608829A1 (de) * 1985-03-27 1986-10-09 LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl Einrichtung zum kompensieren von drehstoessen
EP0641956A1 (fr) * 1993-09-07 1995-03-08 Unisia Jecs Corporation Amortisseur de torsion avec dispositif générateur de friction
US5503595A (en) 1992-02-20 1996-04-02 Valeo Torsion damping device for a motor vehicle, being in particular a double damped flywheel or a clutch friction wheel
EP1058028A2 (fr) 1999-06-04 2000-12-06 Rohs-Voigt Patentverwertungsgesellschaft mbH Amortisseur de vibrations torsionelles et sa méthode de production
FR2845745A1 (fr) * 2002-10-15 2004-04-16 Zf Sachs Ag Amortisseur d'oscillations de torsion pour une transmission de vehicule automobile
WO2005064198A1 (fr) 2003-12-26 2005-07-14 Rohs-Voigt Patentverwertungsgesellschaft Mbh Volant d'inertie a deux masses d'un embrayage ; embrayage et procede de production d'un tel volant d'inertie a deux masses d'un embrayage
WO2006079306A1 (fr) 2005-01-26 2006-08-03 Ulrich Rohs Dispositif d'amortissement, en particulier pour un volant d'inertie a deux masses
EP2159445A2 (fr) * 2008-08-27 2010-03-03 Aisin Seiki Kabushiki Kaisha Dispositif d'amortisseur

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19709343B4 (de) * 1997-03-07 2010-04-08 Zf Sachs Ag Torsionsschwingungsdämpfer mit einer Reibvorrichtung

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1575746B1 (de) * 1966-05-06 1970-04-23 Borg Warner Drehelastische Kupplung
DE3608829A1 (de) * 1985-03-27 1986-10-09 LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl Einrichtung zum kompensieren von drehstoessen
US5503595A (en) 1992-02-20 1996-04-02 Valeo Torsion damping device for a motor vehicle, being in particular a double damped flywheel or a clutch friction wheel
EP0641956A1 (fr) * 1993-09-07 1995-03-08 Unisia Jecs Corporation Amortisseur de torsion avec dispositif générateur de friction
EP1058028A2 (fr) 1999-06-04 2000-12-06 Rohs-Voigt Patentverwertungsgesellschaft mbH Amortisseur de vibrations torsionelles et sa méthode de production
FR2845745A1 (fr) * 2002-10-15 2004-04-16 Zf Sachs Ag Amortisseur d'oscillations de torsion pour une transmission de vehicule automobile
WO2005064198A1 (fr) 2003-12-26 2005-07-14 Rohs-Voigt Patentverwertungsgesellschaft Mbh Volant d'inertie a deux masses d'un embrayage ; embrayage et procede de production d'un tel volant d'inertie a deux masses d'un embrayage
WO2006079306A1 (fr) 2005-01-26 2006-08-03 Ulrich Rohs Dispositif d'amortissement, en particulier pour un volant d'inertie a deux masses
EP2159445A2 (fr) * 2008-08-27 2010-03-03 Aisin Seiki Kabushiki Kaisha Dispositif d'amortisseur

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CN104508319A (zh) 2015-04-08
DE102013003628A1 (de) 2014-09-11

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