WO1981001731A1 - Amortisseur de vibrations en torsion - Google Patents

Amortisseur de vibrations en torsion Download PDF

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Publication number
WO1981001731A1
WO1981001731A1 PCT/US1979/001086 US7901086W WO8101731A1 WO 1981001731 A1 WO1981001731 A1 WO 1981001731A1 US 7901086 W US7901086 W US 7901086W WO 8101731 A1 WO8101731 A1 WO 8101731A1
Authority
WO
WIPO (PCT)
Prior art keywords
plates
pack
flywheel
central
radially
Prior art date
Application number
PCT/US1979/001086
Other languages
English (en)
Inventor
W Windish
Original Assignee
W Windish
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 W Windish filed Critical W Windish
Priority to PCT/US1979/001086 priority Critical patent/WO1981001731A1/fr
Publication of WO1981001731A1 publication Critical patent/WO1981001731A1/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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/64—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts
    • F16D3/66—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts the elements being metallic, e.g. in the form of coils
    • 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
    • F16F15/129—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 characterised by friction-damping means

Definitions

  • Torsional vibration dampening assemblies are frequently interposed between the flywheel of an engine and a transmission for isolating and damping torsional vibrations occurring in the drive line formed thereby.
  • a number of structures are commercially available and they typically include one or more of the features of construction illustrated in the various embodiments of the above identified Stromberg patent.
  • springs such as shown by Stromberg interconnect two or more spaced damping plates and tend to isolate drive line shock.
  • the springs also will return to the system torsional energy applied to them, it is also necessary to provide damping. This is typicaly achieved by utilizing fric ⁇ tion material at the interfaces of the plates.
  • the prior art has generally located the springs at positions relatively radially outwardly of the axis of rotation of the assemblies with the friction material being located at -a relatively radially inward position.
  • the friction produced at the friction material upon relative movement between the plate acts over a relatively short moment arm. Damping action is thereby limited by the length of the damping arm.
  • a vibration damping assembly composed of a plurality of plates with friction material interposed therebetween along with the usual springs.
  • the same is sandwiched between a fly ⁇ wheel and an annular flange with the latter being secured to the flywheel.
  • Unthreaded reaction pins are supported by both the flange and the flywheel, that is, the pins are supported at both ends, to thereby resist bending forces and thereby provide a long-lived assembly.
  • the springs are located radially inwardly with respect to the plates forming the damping assembly while the friction material is located radially outwardly thereof. Consequently, the moment arm over which friction acts to damp vibration in the drive line is increased pro ⁇ viding enhanced damping.
  • the plates making up the vibration damping assem- bly include aligned central apertures with the central aperture of the central plate in the assembly being of smaller size that the apertures in the adjacent plates and provided with radially inwardly directed spline teeth having an axial length no greater than the thickness of the plate. Consequently, a coup.ling having an ex ⁇ ternal spline can be connected to the central plate and be canted through substantial angles with respect thereto to facilitate alignment with the input shaft of a transmission, torque converter, or the like.
  • Fig. 1 is a fragmentary, end view of a vibra ⁇ tion damping assembly made according to the invention.
  • Fig. 2 is an enlarged sectional view taken approximately along the line 2-2 in Fig. 1 and addition ⁇ ally illustrating in phantom, components of a drive train with which the damping assembly is to be used.
  • FIG. 1 An exemplary embodiment of a vibration damping assembly made according to the invention is illustrated in the drawings and with reference thereto is adapted to the interposed between a flywheel 10 of an engine and the input end 12 of a transmission having a transmission shaft (not shown) .
  • the damping assembly consists of three plates 14, 16 and 18 although a greater number could be
  • the plates 14, 16 and 18 are generally circular in configuration and each is provided with a central aperture 20, 22 and 24 respectively. As can be seen in Fig. 2, the apertures 20 and 24 in the plates 14 and 18 have substantially the same diameter and both are considerably larger than the aperture 22 in the plate 16. Moreover, the aperture 22 includes radially inwardly directed spline teeth 25 for purposes to be seen.
  • each of the plates 14, 16 and 18 there are provided a plurality of aligned radially outwardly opening slots 36 with the slots 36 in the plate 16 being somewhat elongated to permit relative movement between the plates to allow compres ⁇ sion of the springs 28.
  • Axially extending reaction pins 38 extend through the slots 36 and, as seen in Fig. 2, each such pin 38 has one end received in a bore 40 in the flywheel 10 and an opposite end re ⁇ ceived in a bore 42 formed in an annular flange 44 secure to the flywheel 10 by a series of bolts 46 (only one of which is shown) .
  • the pack defined by the plates (14,16 and 18) is sandwiched between the flange 44 and the flywheel 10. Relative movement, to a
  • UR OKP ⁇ limited degree, between the plates 14, 16, and 18 can occur by reason of the fact that the slots 36 are formed to be somewhat larger than the pins 38 as shown in Fig. 1.
  • the sides of the slots 36 do, however, limit relative movement between the plates 14, 16 and 18 as is well known.
  • the central plate 16 constitutes a driven plate being driven by friction provided by the friction material 30, forces generated in the springs 28 and/or abutment with the reaction pins 38 when maximum spring deflection has occurred.
  • the plate 16, is therefore, the one to be coupled to the input shaft of the transmission or the like.
  • a coupling 50 having a sleeve-like body 52 provided with an internal spline 54 which may receive a mating external spline on the input shaft (not shown) of the. transmission.
  • One end of the body 52 is provided with a peripheral, radially out- wardly directed web 56 which terminates in a peripheral, ex ⁇ ternal spline 58 which is engaged with the spline teeth 25 on the plate 16.
  • the spline 58 is also spaced from the bounds of the apertures 20 and 24 and the plates 14 and 18. It will be observed that the internal spline de- fined by the spline teeth 24 have an axial length equal to the thickness of the plate 16.
  • this axial length should be substantially no greater than the thickness of the plate 16.
  • the assembly of the present invention reduces spacial requirements re- quired for assembly and thereby minimizes the time re ⁇ quired for assembly in many instances.

Landscapes

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

Abstract

Un ensemble amortisseur de vibrations en torsion est concu pour etre interpose entre le volant (10) d'un moteur et une transmission (12). L'ensemble amortisseur de vibrations comprend une pluralite de plaques (14, 16, 18) avec un materiau de friction (30) interpose entre celles-ci, avec des ressorts (28), Les ressorts (28) sont positionnes radialement vers l'interieur par rapport aux plaques (14, 16, 18) formant l'ensemble amortisseur tandis que le materiau de frottement (30) est positionne radialement vers l'exterieur par rapport a celui-ci.
PCT/US1979/001086 1979-12-13 1979-12-13 Amortisseur de vibrations en torsion WO1981001731A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/US1979/001086 WO1981001731A1 (fr) 1979-12-13 1979-12-13 Amortisseur de vibrations en torsion

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
WOUS79/01086 1979-12-13
PCT/US1979/001086 WO1981001731A1 (fr) 1979-12-13 1979-12-13 Amortisseur de vibrations en torsion

Publications (1)

Publication Number Publication Date
WO1981001731A1 true WO1981001731A1 (fr) 1981-06-25

Family

ID=22147818

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1979/001086 WO1981001731A1 (fr) 1979-12-13 1979-12-13 Amortisseur de vibrations en torsion

Country Status (1)

Country Link
WO (1) WO1981001731A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3721705A1 (de) * 1986-07-05 1988-01-07 Luk Lamellen & Kupplungsbau Einrichtung zum daempfen von schwingungen
DE3721708A1 (de) * 1986-07-05 1988-01-07 Luk Lamellen & Kupplungsbau Einrichtung zur daempfung von drehschwingungen
US4790792A (en) * 1983-12-22 1988-12-13 Eaton Corporation Torsion damping assembly

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2065601A (en) * 1931-12-04 1936-12-29 Continental Motors Corp Damping device
US2359180A (en) * 1942-08-11 1944-09-26 Gen Motors Corp Dynamic balancer
DE1962963A1 (de) * 1969-12-16 1971-06-24 Porsche Kg Reibscheibenkupplung,insbesondere Trennkupplung fuer Wechselgetriebe von Kraftfahrzeugen
US3628353A (en) * 1969-09-08 1971-12-21 Lipe Rollway Corp Damper assembly for drive train
US3695405A (en) * 1969-04-22 1972-10-03 Luk Lamellen & Kupplungsbau Clutch disc
US3817362A (en) * 1971-11-29 1974-06-18 Ferodo Sa Torsion damping device
US4122931A (en) * 1974-07-27 1978-10-31 Luk Lamellen Und Kupplungsbau Gmbh Clutch disk assembly
US4185728A (en) * 1977-10-14 1980-01-29 Borg-Warner Corporation Clutch disc with variable deflection rate vibration damper

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2065601A (en) * 1931-12-04 1936-12-29 Continental Motors Corp Damping device
US2359180A (en) * 1942-08-11 1944-09-26 Gen Motors Corp Dynamic balancer
US3695405A (en) * 1969-04-22 1972-10-03 Luk Lamellen & Kupplungsbau Clutch disc
US3628353A (en) * 1969-09-08 1971-12-21 Lipe Rollway Corp Damper assembly for drive train
DE1962963A1 (de) * 1969-12-16 1971-06-24 Porsche Kg Reibscheibenkupplung,insbesondere Trennkupplung fuer Wechselgetriebe von Kraftfahrzeugen
US3817362A (en) * 1971-11-29 1974-06-18 Ferodo Sa Torsion damping device
US3817362B1 (fr) * 1971-11-29 1986-07-22
US4122931A (en) * 1974-07-27 1978-10-31 Luk Lamellen Und Kupplungsbau Gmbh Clutch disk assembly
US4185728A (en) * 1977-10-14 1980-01-29 Borg-Warner Corporation Clutch disc with variable deflection rate vibration damper

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4790792A (en) * 1983-12-22 1988-12-13 Eaton Corporation Torsion damping assembly
DE3721705A1 (de) * 1986-07-05 1988-01-07 Luk Lamellen & Kupplungsbau Einrichtung zum daempfen von schwingungen
DE3721708A1 (de) * 1986-07-05 1988-01-07 Luk Lamellen & Kupplungsbau Einrichtung zur daempfung von drehschwingungen
DE3721705C2 (de) * 1986-07-05 1998-01-29 Luk Lamellen & Kupplungsbau Einrichtung zum Dämpfen von Schwingungen
DE3721708C2 (de) * 1986-07-05 1998-06-04 Luk Lamellen & Kupplungsbau Einrichtung zur Dämpfung von Drehschwingungen

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