GB1582314A - Torsional vibration damper - Google Patents

Torsional vibration damper Download PDF

Info

Publication number
GB1582314A
GB1582314A GB20267/77A GB2026777A GB1582314A GB 1582314 A GB1582314 A GB 1582314A GB 20267/77 A GB20267/77 A GB 20267/77A GB 2026777 A GB2026777 A GB 2026777A GB 1582314 A GB1582314 A GB 1582314A
Authority
GB
United Kingdom
Prior art keywords
parts
rubber tube
vibration damper
inner part
respect
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.)
Expired
Application number
GB20267/77A
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.)
Goetze GmbH
Original Assignee
Goetze 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 Goetze GmbH filed Critical Goetze GmbH
Publication of GB1582314A publication Critical patent/GB1582314A/en
Expired legal-status Critical Current

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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
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/38—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type
    • F16F1/3863—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type characterised by the rigid sleeves or pin, e.g. of non-circular cross-section
    • 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
    • F16D3/56—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 metal lamellae, elastic rods, or the like, e.g. arranged radially or parallel to the axis, the members being shear-loaded collectively by the total load
    • F16D3/58—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 metal lamellae, elastic rods, or the like, e.g. arranged radially or parallel to the axis, the members being shear-loaded collectively by the total load the intermediate members being made of rubber or like material
    • 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
    • F16D3/68—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 made of rubber or similar material
    • 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
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/42—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by the mode of stressing
    • F16F1/52—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by the mode of stressing loaded in combined stresses
    • 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
    • F16F2236/00—Mode of stressing of basic spring or damper elements or devices incorporating such elements
    • F16F2236/12—Mode of stressing of basic spring or damper elements or devices incorporating such elements loaded in combined stresses

Description

(54) TORSIONAL VIBRATION DAMPER (71) We, GOETZE A.G., formerly known as GOETZEWERKE FRIEDRICH GOETZE AKTIENGESELLSCHAFT, a Body Corporate organised and existing under the laws of the Federal Republic of Germany, of Biirgermeister-Schmidt-Strasse 17, 5093 Burscheid, Germany, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: The present invention relates to a torsional vibration damper comprising inner and outer coaxial parts for connection one to a driving member and the other to a driven member and a rubber body interposed between the two parts to transmit torque. Such a torsional vibration damper may be used for driving shafts and axles in machines, motor vehicles and the like.
In accordance with the invention there is provided a torsional vibration damper comprising inner and outer coaxial polygonal parts for connection one to a driving member and the other to a driven member and a rubber tube interposed and compressed between the two parts to transmit torque, in which the inner part and the outer part are oriented with their faces generally parallel to one another, the rubber tube surrounding the inner part and lying between the faces but not contacting the corners of more than one of the inner and outer parts.
Conveniently such a vibration damper can be assembled by placing the rubber tube in an uncompressed condition between the two coaxial parts and subsequently de forming one or both of the parts in a radial direction to effect the compression of the rubber tube. This allows the vibration damper to be made of any required axial length.
Deformation of the coaxial parts is effected chiefly by the rolling-in of axially extending grooves, when in the case of certain uses, it may be advantageous if the deformation of the two parts is different in magnitude in the axial direction.
By the intensity of deformation in the radial direction, as well as by the different degree of deformation in the axial direction, it is possible to obtain any desired spring characteristic and hence to predetermine the damping ability.
For production-engineering reasons, it is advantageous if the outer part has a circular cross-section before deformation, while after deformation, the cross-section has alternately concave and convex peripheral regions. For obtaining the most uniform deformation possible of the parts, preferably consisting of metal, it is furthermore proposed that the radii of the concave and convex peripheral regions of the parts should be approximately equal.
The coaxial parts are preferably of tubular form, so that the entire system has a relatively low inherent weight and hence a low flywheel moment.
To avoid the notching effect of the angles of the inner part with respect to the surface tension in the rubber hose, the rubber tube may bear on the inner peripheral surface of the outer part, the internal diameter of the rubber hose before assembly being larger than the transverse dimension of the inner part.
Preferably, the smallest internal transverse dimension of the outer part is less than the largest external transverse di mension of the inner part. In this way, full rotation of the coaxial parts with respect to one another is prevented, even after destruction of the rubber tube.
The invention will now be described in more detail with the aid of an example illustrated in the accompanying drawing, in which: Figures 1 and 2 show respectively a longitudinal section and cross-section through a propeller shaft with integrated torsional vibration damper according to the invention.
Figure 1 shows a propeller shaft for motor vehicles, which comprises an inner part 1, an outer part 2 and a rubber tube 3 connecting the two parts together. The parts 1 and 2 are connected by their opposite ends to the link heads 4 and 5, serving to introduce or to lead off the torque. For the torsionally resilient, vibration-damping connection of the parts 1 and 2 to one andther, the rubber tube 3 is radially compressed by means of grooves 6 which are rolled in the outer part 2, after the parts 1, 2 and 3 have been pushed one within the other. The tube 3 is thus pressed against the middle surface region 7 between every two angles 8 and 9 of the inner axle part 1. Thus, the parts 1, 2 and 3 previously fitted loosely one within the other are, after rolling-in of the grooves 6 of the tubular part 2 of initially circular crosssection, connected together by corresponding frictional locking connections between the rubber tube 3 and the two metal parts 1 and 2 to form an assembly unit. The rubber tube 3 is brought to bear exclusively on the faces 7 of the inner part 1 in order to prevent the arigles or corners 8 and- 9 from digging into the inner surface 10 of the tube 3 in the event of relative rotation of the inner part 1 with respect to the outer part 2. Consequently, the inter nal diameter of tube 3 is selected to be substantially greater than the transverse dimension (diagonal) of the inner part.
The axial length of grooves 6 as well as their particular radial depth are adapted to the particular requirements with respect to damping power and the load-carrying capacity of the rubber material.
The inner and outer parts are so shaped that the maximum transverse dimension of the inner part is always greater than the internal distance apart of the grooves 6, with respect to the axis of rotation, so that even in the case of destruction of the rubber tube, complete rotation of the inner part with respect to the outer part is prevented.
WHAT WE CLAIM IS:- 1. A torsional vibration damper comprising inner and outer coaxial polygonal parts for connection one to a driving member and the other to a driven member and a rubber tube interposed and compressed between the two parts to transmit torque, in which the inner part and the outer part are oriented with their faces generally parallel to one another, the rubber tube surrounding the inner part and lying between the faces but not contacting the corners of more than one of the inner and outer parts.
2. A vibration damper as claimed in claim 1 in which the inner and outer parts are both tubular.
3. A vibration damper as claimed in claim 1 or 2 in which the rubber tube engages essentially the whole internal surface of the outer part.
4. A vibration damper as claimed in any of claims 1 to 3 in which the smallest internal transverse dimension of the outer part is less than the largest external transverse dimension of the inner part.
5. A vibration damper as claimed in any of the preceding claims in which the inner part is square in cross-section.
6. A torsional vibration damper substantially as described with reference to the accompanying drawings.
**WARNING** end of DESC field may overlap start of CLMS **.

Claims (6)

  1. **WARNING** start of CLMS field may overlap end of DESC **.
    mension of the inner part. In this way, full rotation of the coaxial parts with respect to one another is prevented, even after destruction of the rubber tube.
    The invention will now be described in more detail with the aid of an example illustrated in the accompanying drawing, in which: Figures 1 and 2 show respectively a longitudinal section and cross-section through a propeller shaft with integrated torsional vibration damper according to the invention.
    Figure 1 shows a propeller shaft for motor vehicles, which comprises an inner part 1, an outer part 2 and a rubber tube 3 connecting the two parts together. The parts 1 and 2 are connected by their opposite ends to the link heads 4 and 5, serving to introduce or to lead off the torque. For the torsionally resilient, vibration-damping connection of the parts 1 and 2 to one andther, the rubber tube 3 is radially compressed by means of grooves 6 which are rolled in the outer part 2, after the parts 1, 2 and 3 have been pushed one within the other. The tube 3 is thus pressed against the middle surface region 7 between every two angles 8 and 9 of the inner axle part 1. Thus, the parts 1, 2 and 3 previously fitted loosely one within the other are, after rolling-in of the grooves 6 of the tubular part 2 of initially circular crosssection, connected together by corresponding frictional locking connections between the rubber tube 3 and the two metal parts 1 and 2 to form an assembly unit. The rubber tube 3 is brought to bear exclusively on the faces 7 of the inner part 1 in order to prevent the arigles or corners 8 and- 9 from digging into the inner surface
    10 of the tube 3 in the event of relative rotation of the inner part 1 with respect to the outer part 2. Consequently, the inter nal diameter of tube 3 is selected to be substantially greater than the transverse dimension (diagonal) of the inner part.
    The axial length of grooves 6 as well as their particular radial depth are adapted to the particular requirements with respect to damping power and the load-carrying capacity of the rubber material.
    The inner and outer parts are so shaped that the maximum transverse dimension of the inner part is always greater than the internal distance apart of the grooves 6, with respect to the axis of rotation, so that even in the case of destruction of the rubber tube, complete rotation of the inner part with respect to the outer part is prevented.
    WHAT WE CLAIM IS:- 1. A torsional vibration damper comprising inner and outer coaxial polygonal parts for connection one to a driving member and the other to a driven member and a rubber tube interposed and compressed between the two parts to transmit torque, in which the inner part and the outer part are oriented with their faces generally parallel to one another, the rubber tube surrounding the inner part and lying between the faces but not contacting the corners of more than one of the inner and outer parts.
  2. 2. A vibration damper as claimed in claim 1 in which the inner and outer parts are both tubular.
  3. 3. A vibration damper as claimed in claim 1 or 2 in which the rubber tube engages essentially the whole internal surface of the outer part.
  4. 4. A vibration damper as claimed in any of claims 1 to 3 in which the smallest internal transverse dimension of the outer part is less than the largest external transverse dimension of the inner part.
  5. 5. A vibration damper as claimed in any of the preceding claims in which the inner part is square in cross-section.
  6. 6. A torsional vibration damper substantially as described with reference to the accompanying drawings.
GB20267/77A 1976-05-15 1977-05-13 Torsional vibration damper Expired GB1582314A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2621787A DE2621787C2 (en) 1976-05-15 1976-05-15 Torsional vibration damped drive shaft

Publications (1)

Publication Number Publication Date
GB1582314A true GB1582314A (en) 1981-01-07

Family

ID=5978148

Family Applications (1)

Application Number Title Priority Date Filing Date
GB20267/77A Expired GB1582314A (en) 1976-05-15 1977-05-13 Torsional vibration damper

Country Status (6)

Country Link
JP (1) JPS52139873A (en)
DE (2) DE2621787C2 (en)
FR (1) FR2351320A1 (en)
GB (1) GB1582314A (en)
IT (1) IT1115606B (en)
SE (1) SE7705634L (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2207975A (en) * 1987-07-30 1989-02-15 Stephenson Blake Resilient mounting for a wheeled vehicle
CN114555973A (en) * 2019-10-10 2022-05-27 西门子交通有限公司 Elastic supporting device
US20220397175A1 (en) * 2019-09-19 2022-12-15 Rosta Ag Torsion spring device, bearing, and vibration damper

Families Citing this family (11)

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Publication number Priority date Publication date Assignee Title
GB2138100B (en) * 1983-03-18 1987-02-11 Steven Odobasic Laminated tubular link
JPS59160493U (en) * 1983-04-14 1984-10-27 本田技研工業株式会社 Auto tricycle joint device
DE3346061A1 (en) * 1983-12-21 1985-07-04 Volkswagenwerk Ag, 3180 Wolfsburg Shaft for vibration-insulating torque transmission, in particular drive shaft for motor vehicles
DE3535513A1 (en) * 1985-10-04 1987-04-09 Schneider Gesenkschmiede USE OF HIGH BODIES WITH LAYER STRUCTURE
DE8619274U1 (en) * 1986-07-18 1986-09-18 Alois Kober KG, 8871 Kötz Torsion spring axle for vehicle trailers
GB2228569A (en) * 1989-01-14 1990-08-29 Schlumberger Ind Ltd "Ultrasonic waveguide temperature sensors with mounting means"
DE4012599C1 (en) * 1990-04-20 1990-12-20 Joern Gmbh, 7012 Fellbach, De
FR2701299B1 (en) * 1993-02-05 1995-04-14 Hutchinson Suspension device comprising at least one elastic system and at least one damping system mounted in series.
FR2746472B1 (en) * 1996-03-22 1998-04-24 Valeo SPACER DAMPER WITH SPACER WASHER, PARTICULARLY FOR MOTOR VEHICLE
DE102008044321B4 (en) * 2008-12-03 2013-01-17 Semperit Ag Holding Spring element for rubber spring axles and rubber suspension axle system
DE102011110021A1 (en) * 2011-08-11 2013-02-14 Neumayer Tekfor Holding Gmbh Vibration damper for a drive train

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FR670010A (en) * 1928-06-05 1929-11-23 Coupling sleeve improvements
DE589662C (en) * 1932-08-25 1933-12-12 Kirchbach Sche Werke Kirchbach Flexible joint coupling, especially for motor vehicles
GB459029A (en) * 1936-07-06 1936-12-31 Hardy Spicer & Company Ltd Universal torque-transmitting joints
US2199926A (en) * 1937-07-19 1940-05-07 Borg Warner Resilient slip joint
FR855881A (en) * 1939-02-08 1940-05-22 Improvements to elastic joints and embodiments
FR873823A (en) * 1940-07-15 1942-07-21 Pintsch Julius Kg Elastic coupling for railway vehicle generators
BE480880A (en) * 1946-06-04 1900-01-01
CH347046A (en) * 1956-06-13 1960-06-15 Gelenkwellenbau Gmbh Cardan shaft, in particular for motor vehicles
FR1231393A (en) * 1958-07-25 1960-09-28 Rzeppa Ltd Elastic transmission coupling and method of manufacturing the same
DE1115538B (en) * 1959-11-26 1961-10-19 Atlas Werke Ag Torsional vibration damper
GB919361A (en) * 1960-06-30 1963-02-27 Tom Edgerton Clarke Hirst Power transmission flexible coupling
GB1306923A (en) * 1969-02-14 1973-02-14 Lamburn A S Drive coupling
DE2014191C3 (en) * 1970-03-24 1978-09-14 Alois Kober Kg, 8871 Grosskoetz Rubber torsion spring axle for trailers
GB1402706A (en) * 1971-04-15 1975-08-13 Lamburn A S Torque transmitting couplings
DE7434606U (en) * 1974-10-16 1976-08-19 Goetzewerke Friedrich Goetze Ag, 5673 Burscheid Torsional vibration damper, in particular a torsional vibration damping drive axle

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2207975A (en) * 1987-07-30 1989-02-15 Stephenson Blake Resilient mounting for a wheeled vehicle
GB2207975B (en) * 1987-07-30 1991-07-03 Stephenson Blake Resilient mounting
US20220397175A1 (en) * 2019-09-19 2022-12-15 Rosta Ag Torsion spring device, bearing, and vibration damper
CN114555973A (en) * 2019-10-10 2022-05-27 西门子交通有限公司 Elastic supporting device
CN114555973B (en) * 2019-10-10 2023-12-01 西门子交通有限公司 Elastic supporting device

Also Published As

Publication number Publication date
DE2621787A1 (en) 1977-12-08
FR2351320A1 (en) 1977-12-09
IT1115606B (en) 1986-02-03
JPS52139873A (en) 1977-11-22
DE7615588U1 (en) 1978-04-06
DE2621787C2 (en) 1982-11-18
FR2351320B1 (en) 1983-02-11
SE7705634L (en) 1977-11-16

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Legal Events

Date Code Title Description
PS Patent sealed
PCNP Patent ceased through non-payment of renewal fee