EP0382735A1 - Amortisseur de vibrations dues a la torsion - Google Patents

Amortisseur de vibrations dues a la torsion

Info

Publication number
EP0382735A1
EP0382735A1 EP19880907045 EP88907045A EP0382735A1 EP 0382735 A1 EP0382735 A1 EP 0382735A1 EP 19880907045 EP19880907045 EP 19880907045 EP 88907045 A EP88907045 A EP 88907045A EP 0382735 A1 EP0382735 A1 EP 0382735A1
Authority
EP
European Patent Office
Prior art keywords
ring
torsional vibration
vibration damper
spring
flywheel
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.)
Withdrawn
Application number
EP19880907045
Other languages
German (de)
English (en)
Inventor
Hubert Pletsch
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.)
PLETSCH, HUBERT
Original Assignee
Woco Franz Josef Wolf and Co GmbH
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 Woco Franz Josef Wolf and Co GmbH filed Critical Woco Franz Josef Wolf and Co GmbH
Publication of EP0382735A1 publication Critical patent/EP0382735A1/fr
Withdrawn legal-status Critical Current

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
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/1414—Masses driven by elastic elements
    • F16F15/1435—Elastomeric springs, i.e. made of plastic or rubber
    • F16F15/1442—Elastomeric springs, i.e. made of plastic or rubber with a single mass
    • 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
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/1414—Masses driven by elastic elements
    • F16F15/1435—Elastomeric springs, i.e. made of plastic or rubber
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2121—Flywheel, motion smoothing-type
    • Y10T74/2131—Damping by absorbing vibration force [via rubber, elastomeric material, etc.]

Definitions

  • the invention relates to a torsional vibration damper of conventional design, which consists of three mutually concentric ring elements, namely a hub ring, a flywheel ring and a spring ring, the spring ring, which can also be composed of several individual spring ring segments or spring ring elements, the hub ring and the flywheel ring relative connected to each other and sprung against each other rotatably.
  • Torsional vibration dampers of this type are used as absorbers for very specific torsional vibration interference frequencies, particularly in automotive engineering.
  • the mass and the design of the spring washer of these known torsional vibration dampers or absorbers are matched to one another in such a way that the inherent frequency of the torsional vibration damper is as exactly as possible equal to the interference vibration, so that the interference frequency is canceled out by the resonance vibration of the torsional vibration damper.
  • a torsional vibration damper is known from German utility model DE 19 97 151 U1, which, in a closed design, tries to produce a sequence of resonance vibration systems by using different flywheel masses, which become active at the corresponding interference frequencies.
  • German utility model DE 19 97 151 U1 which, in a closed design, tries to produce a sequence of resonance vibration systems by using different flywheel masses, which become active at the corresponding interference frequencies.
  • the individual combined vibration systems do not act in isolation from each other, but act as a coupled system, the practically usable coordination becomes this Vibration damper problematic.
  • there is the relatively large weight of this torsional vibration damper due to the construction, as well as its production costs, which are quite critical for series production.
  • a torsional vibration damper which, in contrast to the known torsional vibration damper described above, does not change the masses of the resonance vibration system but the spring force introduced into the vibration system in two discrete stages so that the torsional vibration damper has two distinct resonance frequencies.
  • Creation of a torsional vibration damper with two resonance frequencies has not yet been solved, but in principle, with the simple, robust and inexpensive construction of the torsional vibration damper in question, two resonance frequencies and therefore two repayment frequencies are in any case better than just one.
  • the object of the invention is to create a torsional vibration damper of the type mentioned at the outset which is capable of covering not only one, two or a small number of specific resonance frequencies, but rather a continuously broad interference frequency band.
  • the torsional vibration damper according to the invention is characterized by the features mentioned in the characterizing part of claim 1.
  • the basic idea of the invention is therefore not to place the actual flywheel mass ring of the torsional vibration damper radially on the outside around the hub ring and around the spring ring, namely as an effectively closed flywheel mass element, but to move it radially inward, that is, as the innermost flywheel ring of the torsional vibration damper , which is followed radially outward by the spring ring and finally the hub ring.
  • the flywheel mass elements of this ring are subjected to increasing radial outward force as the speed of the shaft on which the torsional vibration damper is mounted increases.
  • the flywheel mass ring is divided into two, so that the two are diametrically and symmetrically to one another arranged and designed flywheel mass parts can actually be moved radially outwards under the influence of the centrifugal force and thereby bring about the compression deformation of the spring ring elements and, as a result of this compression deformation, the stiffening of the spring ring elements, which in the resonance vibration system. of the torsional vibration damper lead to a continuous increase in the resonance frequency and thus the effective absorber frequency.
  • the flywheel ring does not only have to be divided into this one pair of flywheel parts, but can also have two, three or even more pairs of flywheel parts, which together form a rotating flywheel ring.
  • These flywheel mass pairs will then preferably have masses which differ from one another in pairs, in such a way that they amplify the increase in resonance frequency brought about by the spring stiffening by increasing the mass.
  • differently dimensioned spring ring sections can also be realized, which in principle can act both in the sense of a more progressive design of the characteristic curve and in the sense of mitigating the quite pronounced centrifugal effect.
  • FIG. 2 shows a section according to II-II in FIG. 1.
  • the torsional vibration damper shown in the figures in axial section and in radial section, each in partial representation, is composed of three mutually concentric ring elements, namely a hub ring 1, a flywheel ring 2 and a spring ring 3, which relate the hub ring 1 and the flywheel ring 3 relative to one another connected to each other in a spring-mounted manner.
  • the flywheel mass ring 2 is arranged radially on the inside, so that when it is mentioned from radially inward to radially outward there is a structure in which the "swing mass ring" is two lies innermost, then the spring ring follows as the middle ring and the actual hub ring follows only as the outer ring.
  • the torsional vibration damper according to the invention has as a second essential feature that the flywheel ring 2 is divided into at least two identical, that is to say two segments of equal size and weight, this minimum division of the flywheel ring enables that the flywheel mass ring does not symmetrically center at high speeds, but that the segments or sections of the flywheel mass ring 2 are increasingly pulled radially outwards due to the attacking centrifugal force.
  • a segmented flywheel ring 2 ", 2” does not need to be equipped with only identical flywheel ring segments 2 "or 2", but rather can be paired with each other in the individual sub-segments opposite, also composed of flywheel mass pieces 2 *, 2 "with different masses.
  • the only thing that is decisive here is that the individual flywheel mass pieces of the flywheel mass ring face each other in pairs in identical pieces, so that the damper does not have any, even at higher speeds Unbalance is forced.
  • the tuning of the fundamental resonance frequency for the individual segments can of course be carried out with identical masses of the individual flywheel partial masses in that the individual spring ring segments 3 ' , 3 '' are already set to different hardnesses from the material and / or are of different thicknesses in the radial direction in the structural design.
  • the torsional vibration damper according to the invention based on a speed , not only has a pronounced fundamental frequency, but also has two or more without thereby being burdened with an oversized dimension or with an oversized weight.
  • This embodiment makes the torsional vibration damper according to the invention particularly interesting for motor vehicle construction, in which the interference frequencies are shifted at least to a first approximation with the speed of the drive shaft, and thus the interference frequencies themselves are increased to higher values under normal operating conditions.

Landscapes

  • 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

Amortisseur de vibrations dues à la torsion, comprenant trois éléments annulaires concentriques, à savoir, une bague de moyeu, une bague à masse d'inertie et une rondelle élastique, dans lequel la bague à masse d'inertie est prévue radialement à l'intérieur de la bague de moyeu et de la rondelle élastique disposée entre la bague de moyeu et la bague à masse d'inertie. La fréquence effective de l'amortisseur est ainsi fonction de la vitesse de rotation, et ceci de façon que la fréquence effective active de l'amortisseur prenne des valeurs plus élevées lors d'une vitesse de rotation croissante, par suite de l'accroissement de rigidité de l'accouplement élastique entre la bague à masse d'inertie et la bague de moyeu, sous l'effet de la force centrifuge.
EP19880907045 1988-07-22 1988-07-22 Amortisseur de vibrations dues a la torsion Withdrawn EP0382735A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP1988/000663 WO1990001126A1 (fr) 1988-07-22 1988-07-22 Amortisseur de vibrations dues a la torsion

Publications (1)

Publication Number Publication Date
EP0382735A1 true EP0382735A1 (fr) 1990-08-22

Family

ID=8165308

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19880907045 Withdrawn EP0382735A1 (fr) 1988-07-22 1988-07-22 Amortisseur de vibrations dues a la torsion

Country Status (4)

Country Link
US (1) US5036726A (fr)
EP (1) EP0382735A1 (fr)
JP (1) JPH03501285A (fr)
WO (1) WO1990001126A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4025848A1 (de) * 1990-08-16 1992-02-20 Pahl Gummi Asbest Drehschwingungstilger
JPH0544778A (ja) * 1991-08-09 1993-02-23 Toyoda Gosei Co Ltd ダンパプーリ
DE4406481C3 (de) * 1994-02-28 2002-04-25 Isad Electronic Sys Gmbh & Co Anlasser für Antriebsaggregate, insbesondere Verbrennungsmotoren
US5558066A (en) * 1995-02-02 1996-09-24 Cummins Engine Company, Inc. Fuel system vibration damper
DE19631384C1 (de) 1996-08-02 1997-10-16 Clouth Gummiwerke Ag Elektrische Maschine in einem Antriebsstrang, z. B. eines Kraftfahrzeuges
DE19821165A1 (de) * 1998-05-12 1999-11-18 Volkswagen Ag Übertragungselement zur Kraft- und/oder Momentenübertragung, Schwingungstilger und Verfahren zur Dämpfung von Schwingungen
DE19907216C1 (de) * 1999-02-19 2000-10-12 Univ Hannover Drehschwingungstilger
US7178423B2 (en) * 2002-11-27 2007-02-20 Torque-Traction Technologies Llc Noise and vibration damper for a vehicular driveshaft assembly
DE102008052902A1 (de) 2008-10-23 2010-04-29 Voith Patent Gmbh Vorrichtung zur Verminderung von Drehschwingungen
ES1072574Y (es) * 2010-05-25 2010-10-27 Arteca Caucho Metal S A Dispositivo atenuador de vibraciones en un vehiculo de motor
US8732927B2 (en) 2011-09-20 2014-05-27 General Electric Company Method for adjusting torsional frequency of a power train

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3314304A (en) * 1965-02-12 1967-04-18 Wallace Murray Corp Series compound torsional vibration damper
US3559502A (en) * 1969-07-24 1971-02-02 Caterpillar Tractor Co Pendulum damper
US3606802A (en) * 1969-08-05 1971-09-21 Kenneth Tsunoda Vibration-damped rotatable cylindrical member
DE2734769A1 (de) * 1977-08-02 1979-02-15 Maschf Augsburg Nuernberg Ag Resonanz-drehschwingungsdaempfer
JPS58146745A (ja) * 1982-02-24 1983-09-01 N O K Megurasuteitsuku Kk ト−シヨナルダンパ
DE3529687A1 (de) * 1985-08-20 1987-03-05 Opel Adam Ag Drehschwingungstilger fuer eine antriebswelle
JPS63293344A (ja) * 1987-05-26 1988-11-30 Mitsubishi Electric Corp 粘性ダンパ−

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9001126A1 *

Also Published As

Publication number Publication date
WO1990001126A1 (fr) 1990-02-08
JPH03501285A (ja) 1991-03-22
US5036726A (en) 1991-08-06

Similar Documents

Publication Publication Date Title
DE4201049C2 (de) Drehzahladaptiver Drehschwingungsdämpfer
DE3447926C2 (de) Einrichtung zum Kompensieren von Drehstößen
EP0521446B1 (fr) Amortisseur
DE2912090A1 (de) Drehschwingungsdaempfer
DE3418671A1 (de) Daempfungseinrichtung zum aufnehmen bzw. ausgleichen von drehstoessen
DE3875926T2 (de) Schwungrad mit einem schwingungsdaempfer.
EP1041309A1 (fr) Amortisseur de vibrations adaptif à la vitesse de rotation
EP0382735A1 (fr) Amortisseur de vibrations dues a la torsion
DE2906675A1 (de) Kupplungsscheibe
DE2739583A1 (de) Torsionsschwingungsdaempfer
DE3937669C1 (fr)
WO2014060191A1 (fr) Système d'amortissement des vibrations de torsion à précontrainte
DE19857110A1 (de) Dämpfungsscheibenanordnung
DE3825062A1 (de) Torsionsschwingungsdaempfer
DE4013101C2 (de) Drehschwingungsdämpfer mit dynamischem Schwingungsdämpfer, insbesondere für Kraftfahrzeuge
DE1600192B2 (de) Kupplungsscheibe mit Schwingungsdämpfer
DE3802106A1 (de) Geteiltes schwungrad
DE3411091A1 (de) Daempfungseinrichtung zum aufnehmen bzw. ausgleichen von drehstoessen
DE2746127C3 (de) Drehschwingungsdämpfer
DE3529687C2 (fr)
DE3411090A1 (de) Daempfungseinrichtung zum aufnehmen bzw. ausgleichen von drehstoessen
DE69534365T2 (de) Drehschwingungsdämpfer mit mehreren reibungsstufen
DE3535286A1 (de) Drehschwingungstilger fuer eine antriebswelle
DE2518258A1 (de) Torsionsdaempfende einrichtung
EP1975458B1 (fr) Dispositif d'amortissement de vibrations de torsion d'un arbre

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19900809

17Q First examination report despatched

Effective date: 19910510

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: PLETSCH, HUBERT

RIN1 Information on inventor provided before grant (corrected)

Inventor name: PLETSCH, HUBERT

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19930512