WO2000006924A1 - Systeme de transmission de force - Google Patents

Systeme de transmission de force Download PDF

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Publication number
WO2000006924A1
WO2000006924A1 PCT/EP1999/005311 EP9905311W WO0006924A1 WO 2000006924 A1 WO2000006924 A1 WO 2000006924A1 EP 9905311 W EP9905311 W EP 9905311W WO 0006924 A1 WO0006924 A1 WO 0006924A1
Authority
WO
WIPO (PCT)
Prior art keywords
power transmission
transmission system
primary part
secondary part
damping
Prior art date
Application number
PCT/EP1999/005311
Other languages
German (de)
English (en)
Inventor
Franz Brenner
Gregor Polifke
Original Assignee
Voith Turbo Gmbh & Co. Kg
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 Voith Turbo Gmbh & Co. Kg filed Critical Voith Turbo Gmbh & Co. Kg
Publication of WO2000006924A1 publication Critical patent/WO2000006924A1/fr

Links

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
    • 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
    • F16F15/13142—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 method of assembly, production or treatment
    • 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
    • F16F2230/00—Purpose; Design features
    • F16F2230/32—Modular design

Definitions

  • the invention relates to a power transmission system, in particular an arrangement of a device for vibration damping in a power transmission system for a drive system, in particular with the
  • Each vibration damping device comprises at least one
  • Primary mass and a secondary mass which can be rotated relative to one another in the circumferential direction and which are connected to one another via means for spring and damping coupling.
  • the primary mass replaces the flywheel in drive trains.
  • Device for vibration damping can be assembled in a particularly simple and quick manner and is characterized by an inexpensive production.
  • the device for vibration damping is designed, for example, as in the document DE 37 21 708 C2. This comprises at least two against one another via damping means
  • Rolling bearing mounted flywheel masses one of which can be connected to a motor and the other to a gearbox via a clutch, e.g. a friction clutch, and at least one of the flywheel masses can be at least partially filled with a viscous or pasteous medium and externally via at least one Seal sealed
  • Chamber has.
  • a damping arrangement is made in the chamber, which opposes a relative rotation between the centrifugal masses.
  • the device is assembled in such a way that two preassembled subunits are designed such that they can be axially joined together and connected to one another via a connecting means, a sealing element being attached to one of the subunits, that after assembly is in a non-flat area intended for the other unit.
  • Either the roller bearing is positively fixed to one of the subunits and can be pushed onto a seat of the other subunit during assembly and / or one of the subunits carries one component with a profile and a plug connection, while the other unit has the counter profile of a plug connection coupling the two units in a rotationally locking manner wearing.
  • the invention has for its object a possibility of integrating a device for vibration damping in one
  • the solution according to the invention should be characterized by a simple structural design and low manufacturing and assembly costs.
  • rapid expansion of the vibration damping device must be ensured in every integration situation.
  • the power transmission system comprises one with a
  • the Drive machine at least indirectly connectable flywheel arrangement and a coupling device arranged downstream of the flywheel arrangement in the force transmission direction and a device for vibration damping arranged between the flywheel arrangement and the coupling device.
  • the device comprises at least two components - a first component and a second component -, which are designed as a primary part and a secondary part and which are designed to be rotatable relative to one another in the circumferential direction.
  • the device for vibration damping further comprises means for realizing a spring coupling between the two components and damping the system. The means for realizing the spring coupling enable the
  • a preassembled structural unit is understood to mean an independently tradable structural unit which, however, can consist of prefabricated subunits and / or individual parts.
  • the two components - primary part and secondary part - are supported by a bearing arrangement.
  • a first element in the form of the primary part is non-rotatably coupled to the flywheel.
  • the other second element is non-rotatably connectable to a connecting flange for the coupling device.
  • Means for fixing the bearing in the axial direction are assigned to the bearing arrangement.
  • the clutch device is preferably designed as a friction clutch.
  • the device for vibration damping is flanged to the flywheel arrangement, which can consist of several components or is made in one piece.
  • the so-called primary part is preferably attached directly to the flywheel. This offers the advantage that the entire vibration damping device can be replaced in a simple manner if necessary, without additional modifications having to be made or the flywheel having to be replaced.
  • Means for fixing the bearing arrangement in the axial direction are preferably provided.
  • the bearing arrangement takes on the function of a fixed bearing, ie this transmits axial forces as well as radial forces.
  • the bearing arrangement preferably comprises at least one rolling bearing with an inner ring and an outer ring, the inner ring preferably being assigned to the primary part in terms of components, while the outer ring is assigned to the secondary part.
  • the assignment of the inner ring to the primary part takes place via the coupling with the flywheel arrangement, in particular one assigned to the flywheel arrangement
  • the bearing journal carries the inner ring, this is preferably pressed onto the bearing journal.
  • the bearing journal can in turn be designed as a separate component which can be coupled to the flywheel arrangement or as a structural unit with the flywheel arrangement.
  • the outer ring is preferably the component
  • the stops for the bearing arrangement are formed by the bearing journal or a component that can be coupled to it and a component that can be coupled to the secondary part, for example in the form of a tensioning element, and the connecting flange for the coupling device.
  • the component that is connected to the element associated with the inner ring — secondary part — rotatably connected — comprises
  • Coupling device - at least one bearing pin, which forms the seat for the inner ring.
  • connection between the primary part and the flywheel arrangement is radial
  • Coupling device and secondary part takes place. Both options are conceivable, although the former is preferred.
  • the device for vibration damping on rotating components can be designed in many forms, preferably this always includes a
  • Primary part and a secondary part which can be rotated relative to one another to a limited extent in the circumferential direction.
  • the primary part and the secondary part can be coupled to one another via a damping and spring coupling.
  • the means for realizing the spring coupling each comprise at least one spring device.
  • Secondary part - is formed by at least two disc-shaped elements which enclose an interior space which can be at least partially filled with a damping medium and in which the respective other component, secondary part or primary part, is arranged.
  • Damping can be integrated in one device or can be designed as separate units. In the latter case, it is conceivable to assign the first means for realizing the spring coupling and the second means for realizing the damping of the system to different devices, for example to arrange them in separate, spatially separated chambers which are formed between the primary part and the secondary part .
  • the means for implementing the damping can act hydraulically or mechanically. For this purpose, these comprise at least one chamber which can be filled with a hydraulic fluid and / or another damping medium, which in turn has means for
  • Influencing the damping behavior can be assigned.
  • the means for influencing the damping behavior comprise at least one throttle point associated with a damping chamber, which is integrated in the device for vibration damping.
  • the throttle point is then preferably arranged directly in the damping chamber.
  • the device for vibration damping with further third means for limiting the angle of rotation between the primary part and the secondary part, wherein these means can be assigned to the damping chamber and divide the damping chamber into two partial chambers which are connected to one another via at least one throttle point , the third means being involved in the formation of the throttle point.
  • these means can be assigned to the damping chamber and divide the damping chamber into two partial chambers which are connected to one another via at least one throttle point , the third means being involved in the formation of the throttle point.
  • the formation of the throttle point a) integration of the throttle point in the third means; b) formation of the throttle point between the third means and the spatial limits of the damping chamber by the primary part and the secondary part.
  • a damping grease is used, the viscosity of which is adjusted so that it is at the operating temperatures of
  • Vibration damper can move back and forth between the damping part chamber.
  • the design of the vibration damping device is not restricted to any of these options.
  • 1 shows an embodiment of a power transmission system with the inventive integration of a device for vibration damping
  • Fig. 2 illustrates a further embodiment of the integration of
  • 3a show a non-proportional representation and 3b embodiment of a device for
  • Vibration damping as can be used for the designs according to FIGS. 1 and 2.
  • FIG. 1 illustrates a preferred embodiment of a power transmission system 100 designed according to the invention for a drive system.
  • This comprises at least one flywheel arrangement 2, a device for vibration damping 1 of a rotating component, in particular a vibration damper, and a coupling device 101.
  • the device for vibration damping 1 is arranged and mounted in the power transmission system 100 between the flywheel arrangement 2 and the coupling device 101.
  • the device for vibration damping 1 comprises two elements, a first element 3 and a second element 4.
  • the first element 3 of the device for vibration damping 1 is formed by the so-called primary part.
  • the second element 4 is designed as a so-called secondary part 4.
  • the primary part 3 is understood to mean the component which is coupled to the drive side in the direction of the force action, preferably in traction mode, while the secondary part 4 is connected to the driven side. Both - primary part 3 and secondary part 4 - viewed in the circumferential direction, can be rotated relative to one another and can be coupled to one another via a damping and spring coupling in addition to one
  • the device for vibration damping 1 can be designed in many different ways. With regard to a possible embodiment variant, reference is made to FIG. 3.
  • the device for vibration damping 1 can be mounted as a modular and preassembled structural unit between the flywheel arrangement 2 and the clutch device 101. Pre-assembled is understood to mean a structural unit that can be traded independently as a whole.
  • the bearing arrangement 102 comprises at least one roller bearing 103 with an outer ring 104 and an inner ring 105.
  • the inner ring 105 is assigned to the first component 3, here the primary part 3, while the outer ring 104 is assigned to the second component, the
  • the bearing arrangement 102 in particular the inner ring 105 of the roller bearing 103, is arranged on a bearing journal 106.
  • the inner ring 105 is preferably pressed onto the outer circumference 107 of the bearing journal 106.
  • the bearing journal 106 is assigned to the flywheel arrangement 2.
  • the bearing journal preferably forms
  • the bearing journal 106 at the same time the bearing journal of the flywheel arrangement 2.
  • the bearing journal 106 can be designed as a separate component which is in a form-fitting and / or non-positive connection with the flywheel arrangement 2. Another possibility, which is not shown here in detail, however, is the bearing journal 106 and the
  • Integrate flywheel assembly 2 in a component or execute as an integral component.
  • the primary part the latter is connected to the flywheel arrangement 2 in a rotationally fixed manner.
  • the primary part 3 thus does not replace any
  • the rotationally fixed coupling which is designated here by 108, is preferably implemented via positive and / or non-positive connections, which, not shown here, are preferably made in a uniform manner
  • the positive and / or non-positive connection is realized in the case shown via a plurality of fastening elements 109.
  • the connection is preferably non-positively by means of
  • the flywheel arrangement 2 itself consists of a disk-shaped element 110, but can also comprise several elements.
  • the primary mass 4 can be coupled to a coupling device 101.
  • the secondary part 4 is preferably connected in a rotationally fixed manner to the input side 111 of the coupling device 101.
  • the input side 111 is from a coupling flange
  • the clutch device 101 itself is preferably designed as a friction clutch.
  • the specific design of the friction clutch can take many forms. It is conceivable to use a friction type clutch.
  • the coupling flange 112 carries at least one of the friction surfaces 113 involved in the power transmission, or an element carrying the friction surface.
  • other designs for friction clutches are also conceivable, for example with a large number of disk-shaped elements in the form of plates.
  • the coupling of the Coupling flange 112 with the secondary part 104 is preferably also positive and / or non-positive. In the illustrated case, the coupling takes place via connecting elements 114, which connect the coupling flange 112 to the secondary part 4.
  • the bearing arrangement 102 is preferably designed as a fixed bearing comprising a roller bearing 103. If only one roller bearing 103 is used, a stop, here the stops 115 and 116, is assigned to the inner ring 105 on both sides in the axial direction. The stop 115 is formed directly by executing a shaft shoulder on the journal 106.
  • the stop 116 is formed by an element 117 that can be formed as a structural unit with the bearing journal 106.
  • This element 117 is preferably designed in the form of a disk and has at least two regions with different diameters in the axial direction.
  • the stops in the axial direction for the outer ring 104 are preferably directly from
  • Coupling flange 112 and a clamping element 118 which can be at least indirectly coupled to it are formed.
  • the clamping element 118 is assigned to the secondary part 4 in terms of component. To implement a possible rotation in the circumferential direction between the primary part 3 and the secondary part 4 by corresponding assignment of the inside and
  • Clamping element 118 which is designed as an annular element and has at least one projection aligned in the radial direction to the axis of symmetry S or a plurality of circumferential projections, which can also be combined into a single circumferential projection, and an axial one
  • Stop 119 forms in the axial direction, is the component Secondary part 4 and thus assigned to the coupling device 101.
  • the clamping element 118 has an outer diameter d AS , which forms a gap with the inner diameter d l3 of the primary part 3, which permits a relative movement between the primary part 3 and the clamping element 118.
  • Additional sealing devices are preferably provided, which at
  • the coupling flange 112, the secondary part 4 and the clamping element 118 are thus clamped together in the axial direction via the connecting elements 114.
  • At least two connecting elements 114.1 and 114.2 are provided to implement the bracing.
  • a plurality of connecting elements 114.n are preferably arranged at uniform intervals in the circumferential direction on a diameter d v .
  • the dimensions of the clamping element 118 in the axial direction and of the flange-shaped end 122 of the coupling flange 112 are preferably selected such that, viewed in the installed position, they do not extend, or only insignificantly, beyond the axial extent of the device for vibration damping 1 in cooperation with the secondary part 4.
  • the assembly in the drive system takes place in such a way that the device for vibration damping 1 is completely flanged to the flywheel arrangement 2 as a pre-assembled unit.
  • the flange surfaces are preferably formed on the one hand by the end face 123 of the flywheel arrangement 2 pointing towards the vibration damping device 1 and the surface
  • the area 124 which is oriented towards the flywheel arrangement 2 in the installed position is formed by the first element, ie the primary part 3.
  • FIG. 1 represents a preferred possibility of integrating the device for vibration damping 1 in a power transmission system 100 for a drive train.
  • FIG. 2 discloses a further embodiment, in which the assignment of the races of the bearing arrangement 102 to the secondary part 4 and primary part 3, and thus to the elements of the flywheel arrangement 2 and / or coupling device 101, has been exchanged with respect to the possibility shown in FIG. 1.
  • the flywheel 2 is viewed in the radial direction, compared to the possibility shown in FIG.
  • FIGS. 1 and 2 are not tied to a specific form of the design of the device for vibration damping 1 or 1.2.
  • the configuration of the device for vibration damping 1 can be implemented, for example, as described in FIG. 3.
  • 3a illustrates an embodiment of a device for vibration damping 1.3 of a rotating component in axial section
  • FIG. 3b shows a view of a section of the primary part 3.3 corresponding to FIG. 3a.
  • FIG. 3a shows in axial section, not in proportion to the proportions, an embodiment of a device for vibration damping 1.3 of a rotating component which is used for damping longitudinal and / or torsional vibrations on a rotating component, in particular according to FIG. 1 on the flywheel arrangement 2, and in a modification of the assignment of
  • the primary part and the secondary part can also be used for the embodiment according to FIG. 2, it being possible for the individual disk-shaped elements used to be composed of several elements as a structural unit.
  • the device for vibration damping 1.3 comprises two
  • the primary part 3.3 is non-rotatably coupled to the rotating component whose vibrations are to be damped, i.e. for the designs according to FIGS. 1 and 2 with the flywheel arrangement 2.
  • the primary part 3.3 comprises in the simplest
  • Case two disc-shaped elements 3.3.1 and 3.3.2 with a first part are coupled in the form of a housing part 6.3.
  • a second part 7.3 which is coupled to the housing part 6.3 in a rotationally fixed manner, is additionally provided. Both are also components of the primary part 3.3.
  • the connection between the first part 6.3 and the second part 7.3 takes place via connecting elements 8.3, which are preferably designed in the form of screw connections.
  • the primary part 3.3 is guided radially via the bearing arrangement 102 shown in FIGS. 1 and 2.
  • the secondary part 4.3 is designed as a disk-shaped element which has recesses 5.3, preferably in the form of, in the circumferential direction on a specific diameter d 1
  • the secondary part 4.3 is loosely arranged or stored in relation to the primary mass 3.3.
  • a coupling between the two masses is implemented to implement the spring coupling via at least one spring device 12 which comprises at least one spring element 12.1.
  • the spring elements of the spring device 12 are arranged in recesses 5.3 in the secondary part 4.3 and extend in the circumferential direction of the secondary part 4.3 and are supported on the primary part 3.3.
  • the arrangement, design and function of the spring elements 12.1, 12.n is explained in more detail in FIG. 3b.
  • the function of the spring device 12 is to transmit torque to the secondary part at least during the entire operation in order to set it in rotation and to lower the resonance frequency.
  • both parts 6.3 and 7.3 of the primary part 3.3 have window-shaped cutouts running in the circumferential direction on a certain diameter d 2 , which are essentially complementary to the spring devices 12 with regard to their distance from one another and their size
  • Recesses are formed on the secondary part 4.3 and are arranged offset to this in the circumferential direction in the installed position in the unloaded state by approximately half the extent of the recess in the circumferential direction. Both parts engage tangentially on both sides of the spring devices or, as shown in FIG. 3b, on the guide pieces assigned to their ends
  • damping takes place via a hydraulic fluid. This is filled into a space between the primary part 3.3 and the secondary part 4.3, which is referred to here as 13.
  • the filling of the intermediate space can take place in such a way that either only the area in which the spring devices 12 are located or additional chambers, not shown here in detail, which between Primary and secondary part can be formed, filled or the entire space between the primary part 3 and the secondary part 4.
  • Hydraulic fluid has a variety of different possibilities. A possibility, not shown here, of supply via a corresponding hydraulic fluid supply device via the bearing pin arrangement of the flywheel arrangement is conceivable. The filling of the space 13 can be done once or depending on
  • Another possibility, not shown here, is to fill the chambers with fat or another pasty agent.
  • the angle of rotation alpha in the circumferential direction of the primary part 3.3 relative to the secondary part 4.3, which causes the spring device 12 to be compressed, which preferably comprise at least compression springs 12.n, can be additionally limited, for example.
  • the limitation is then made by appropriate stops on the primary part 3.3. These attacks are via slots 16 in the primary part 3.3, which are on a certain Diameter arranged in the circumferential direction and are distributed in the circumferential direction preferably at equal distances from each other, realized.
  • the secondary part 4.3 is assigned projections in the area of the diameter d 3 , which protrude into the recesses or the elongated holes of the primary part 3.3 in the installed position.
  • the projections are to be carried out in such a way that the elongated holes can be displaced in the circumferential direction relative to the projections without problems. It is also conceivable to assign the function of the protruding element to the primary mass and to provide the cutouts on the secondary part or the secondary mass.
  • the projections can be part of the secondary part 4.3 or the primary part 3.3, i.e. form a structural unit with these or can be realized with additional elements.
  • the connecting elements 8.3, which connect the first part 6.3 of the primary part 3.3 to the second part 7.3 in a rotationally fixed manner, can take over the function of these projections.
  • the connecting element 8.3 extends through the slot 16 of the secondary part 4.3. Via this coupling and assignment to the secondary part 4.3, i.e.
  • the secondary part 4 is fixed in the axial direction.
  • Connecting element 8.3 which limits the possible rotation angle alpha when the primary part 3.3 moves relative to the secondary part 4.3.
  • the angle of rotation alpha is limited by the extent I of the elongated holes 16 in the circumferential direction.
  • Limiting function for the angle of rotation alpha enables a to create a compact system with simple, easily interchangeable components.
  • FIG. 3b illustrates a section of a view of the secondary part 4.3 corresponding to FIG. 3a. This shows the elongated holes 16.
  • Vibration damping device is hereby to be included in full in the disclosure content of this application.
  • a so-called floating damping ring is arranged in the interior space filled with a damping medium between the two components primary part and secondary part, which is not positively connected to either one or the other mass.
  • This floating damping ring forms with the first component, for example the primary part, at least one first displacement chamber and with the second component, in this case the secondary part, at least one second displacement chamber.
  • the floating damping ring is exposed to the free play of forces during the relative movement of primary part 3 and secondary part 4, whereby it can be rotated to a limited extent in relation to each of the two components.
  • the damping ring can be made in one piece or in multiple pieces in the circumferential direction.
  • Solutions represent examples which can preferably be used, but do not limit the scope of protection of the solution according to the invention.
  • the specific design of the individual elements is at the discretion of the responsible specialist.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (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 système de transmission de force (100) comprenant un dispositif volant (2) pouvant être relié au moins indirectement à une machine d'entraînement; un dispositif de couplage placé en aval du dispositif volant (2) dans le sens de la puissance; un dispositif destiné à l'amortissement des vibrations (1) comportant au moins un élément primaire (3) et un élément secondaire (4) qui tournent l'un par rapport à l'autre dans le sens périphérique et qui peuvent être couplés par un couplage élastique et d'amortissement. L'invention est caractérisée en ce que le dispositif d'amortissement de vibrations peut être relié comme composant prémonté entre le dispositif volant (2) et le dispositif de couplage (101) à l'aide d'un palier (103) et avec le dispositif volant (2) et le dispositif de couplage (101); l'élément primaire (3) est relié pivotant au dispositif volant (2) et ce, au moins indirectement; l'élément secondaire (4) peut être relié pivotant à un élément du dispositif de couplage (101) et ce, au moins indirectement.
PCT/EP1999/005311 1998-07-27 1999-07-26 Systeme de transmission de force WO2000006924A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE29813308.3 1998-07-27
DE29813308U DE29813308U1 (de) 1998-07-27 1998-07-27 Kraftübertragungssystem

Publications (1)

Publication Number Publication Date
WO2000006924A1 true WO2000006924A1 (fr) 2000-02-10

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PCT/EP1999/005311 WO2000006924A1 (fr) 1998-07-27 1999-07-26 Systeme de transmission de force

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WO (1) WO2000006924A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10117709B4 (de) * 2000-05-17 2007-04-05 Heidelberger Druckmaschinen Ag Tilger zur Schwingungsdämpfung eines rotierenden Bauteiles, insbesondere in einer Rotationsdruckmaschine

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2168780A (en) * 1984-12-22 1986-06-25 Fichtel & Sachs Ag Divided fly-wheel
FR2586071A1 (fr) * 1985-08-10 1987-02-13 Fichtel & Sachs Ag Volant en plusieurs parties avec amortisseur de vibrations de torsion
DE3721708A1 (de) * 1986-07-05 1988-01-07 Luk Lamellen & Kupplungsbau Einrichtung zur daempfung von drehschwingungen
DE3635043C1 (de) 1986-10-15 1988-07-07 Voith Gmbh J M Drehelastische Kupplung
FR2618200A1 (fr) * 1987-07-15 1989-01-20 Valeo Volant amortisseur de torsion.
EP0339805A2 (fr) * 1988-04-01 1989-11-02 Toyota Jidosha Kabushiki Kaisha Volant d'inertie du type à amortisseur de torsion avec un mécanisme d'amortissement fluide
DE3916575C1 (fr) 1989-05-22 1990-11-22 J.M. Voith Gmbh, 7920 Heidenheim, De
DE3923749C1 (fr) 1989-07-18 1991-02-21 J.M. Voith Gmbh, 7920 Heidenheim, De
US5059156A (en) * 1988-01-26 1991-10-22 Daimler-Benz Ag Divided flywheel
EP0481268A1 (fr) * 1990-10-04 1992-04-22 Deere & Company Arrangement d'un amortisseur de vibrations de torsion
US5569086A (en) * 1993-06-24 1996-10-29 Kabushiki Kaisha Daikin Seisakusho Viscous fluid torsional vibration dampening device having an elastic slider configured to provide friction dampening

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2168780A (en) * 1984-12-22 1986-06-25 Fichtel & Sachs Ag Divided fly-wheel
FR2586071A1 (fr) * 1985-08-10 1987-02-13 Fichtel & Sachs Ag Volant en plusieurs parties avec amortisseur de vibrations de torsion
DE3721708A1 (de) * 1986-07-05 1988-01-07 Luk Lamellen & Kupplungsbau Einrichtung zur daempfung von drehschwingungen
DE3721708C2 (de) 1986-07-05 1998-06-04 Luk Lamellen & Kupplungsbau Einrichtung zur Dämpfung von Drehschwingungen
DE3635043C1 (de) 1986-10-15 1988-07-07 Voith Gmbh J M Drehelastische Kupplung
FR2618200A1 (fr) * 1987-07-15 1989-01-20 Valeo Volant amortisseur de torsion.
US5059156A (en) * 1988-01-26 1991-10-22 Daimler-Benz Ag Divided flywheel
EP0339805A2 (fr) * 1988-04-01 1989-11-02 Toyota Jidosha Kabushiki Kaisha Volant d'inertie du type à amortisseur de torsion avec un mécanisme d'amortissement fluide
DE3916575C1 (fr) 1989-05-22 1990-11-22 J.M. Voith Gmbh, 7920 Heidenheim, De
DE3923749C1 (fr) 1989-07-18 1991-02-21 J.M. Voith Gmbh, 7920 Heidenheim, De
EP0481268A1 (fr) * 1990-10-04 1992-04-22 Deere & Company Arrangement d'un amortisseur de vibrations de torsion
US5569086A (en) * 1993-06-24 1996-10-29 Kabushiki Kaisha Daikin Seisakusho Viscous fluid torsional vibration dampening device having an elastic slider configured to provide friction dampening

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10117709B4 (de) * 2000-05-17 2007-04-05 Heidelberger Druckmaschinen Ag Tilger zur Schwingungsdämpfung eines rotierenden Bauteiles, insbesondere in einer Rotationsdruckmaschine

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DE29813308U1 (de) 1999-12-09

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