GB1582314A - Torsional vibration damper - Google Patents
Torsional vibration damper Download PDFInfo
- 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
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
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Health & Medical Sciences (AREA)
- Child & Adolescent Psychology (AREA)
- Springs (AREA)
- Pulleys (AREA)
- Vibration Prevention Devices (AREA)
- Motor Power Transmission Devices (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
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)
- **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 surface10 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.
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 (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2207975A (en) * | 1987-07-30 | 1989-02-15 | Stephenson Blake | Resilient mounting for a wheeled vehicle |
DE20304434U1 (en) | 2003-03-19 | 2003-05-22 | Trelleborg Automotive Technical Centre GmbH, 56203 Höhr-Grenzhausen | Bearing bush has core with polygonal cross sectional shape, and longitudinal slot formed in outer sleeve and rubber body vulcanized onto core is located in region of core's longitudinal edge |
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)
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 |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
-
1976
- 1976-05-15 DE DE2621787A patent/DE2621787C2/en not_active Expired
- 1976-05-15 DE DE7615588U patent/DE7615588U1/en not_active Expired
-
1977
- 1977-02-14 FR FR7704093A patent/FR2351320A1/en active Granted
- 1977-02-18 JP JP1631277A patent/JPS52139873A/en active Pending
- 1977-02-21 IT IT20498/77A patent/IT1115606B/en active
- 1977-05-13 GB GB20267/77A patent/GB1582314A/en not_active Expired
- 1977-05-13 SE SE7705634A patent/SE7705634L/en unknown
Cited By (6)
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 |
DE20304434U1 (en) | 2003-03-19 | 2003-05-22 | Trelleborg Automotive Technical Centre GmbH, 56203 Höhr-Grenzhausen | Bearing bush has core with polygonal cross sectional shape, and longitudinal slot formed in outer sleeve and rubber body vulcanized onto core is located in region of core's longitudinal edge |
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 |
---|---|
FR2351320A1 (en) | 1977-12-09 |
SE7705634L (en) | 1977-11-16 |
DE2621787A1 (en) | 1977-12-08 |
FR2351320B1 (en) | 1983-02-11 |
IT1115606B (en) | 1986-02-03 |
DE2621787C2 (en) | 1982-11-18 |
DE7615588U1 (en) | 1978-04-06 |
JPS52139873A (en) | 1977-11-22 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
PS | Patent sealed | ||
PCNP | Patent ceased through non-payment of renewal fee |