CA2044094C - Flexible torsion coupling - Google Patents
Flexible torsion couplingInfo
- Publication number
- CA2044094C CA2044094C CA002044094A CA2044094A CA2044094C CA 2044094 C CA2044094 C CA 2044094C CA 002044094 A CA002044094 A CA 002044094A CA 2044094 A CA2044094 A CA 2044094A CA 2044094 C CA2044094 C CA 2044094C
- Authority
- CA
- Canada
- Prior art keywords
- ring
- coupling
- chambers
- radial
- rings
- 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 - Fee Related
Links
- 230000008878 coupling Effects 0.000 title claims abstract description 45
- 238000010168 coupling process Methods 0.000 title claims abstract description 45
- 238000005859 coupling reaction Methods 0.000 title claims abstract description 45
- 238000013016 damping Methods 0.000 claims abstract description 37
- 230000004323 axial length Effects 0.000 abstract description 4
- 230000005540 biological transmission Effects 0.000 abstract description 3
- 238000010276 construction Methods 0.000 description 6
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 239000013013 elastic material Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005549 size reduction Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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
- F16D3/72—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 with axially-spaced attachments to the coupling parts
- F16D3/74—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 with axially-spaced attachments to the coupling parts the intermediate member or members being made of rubber or other rubber-like flexible 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
-
- 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
- F16D3/76—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 shaped as an elastic ring centered on the axis, surrounding a portion of one coupling part and surrounded by a sleeve of the other coupling part
-
- 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
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/36—Pulleys
- F16H2055/366—Pulleys with means providing resilience or vibration damping
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Pulleys (AREA)
- Support Of The Bearing (AREA)
Abstract
A flexible torsion coupling for two machine elements is disclosed. The coupling includes a pair of rings which are respectively provided on the machine elements and partially surround each other at a radial distance. A first ring of the pair of rings has an axially open, U-shaped profile and defines a space that is at least partly divided by the second ring of the rings into a pair of chambers, which surround each other in radial direction. A radial bearing is provided in one of the chambers and a damping element is provided in the other chamber. The torsion coupling has a smaller axial length and permits, for example, the transmission of rotational forces of a shaft to a pulley connected with the shaft by the torsion coupling.
Description
20140!3~
FLEXIBLE TORSION COUPLING
The invention relates to a flexible torsion coupling for two machine elements, wherein a pair of rings are respectively provided on the machine elements, which rings surround each other at a radial spacing and wherein a damping element of rubber and a radial bearing are positioned in the gap resulting from the radial spacing to connect the rings parallel to each other. Particularly, the invention relates to a flexible torsion coupling for use in, for example, torsion dampers of internal combustion engines.
Such a coupling is used in the torsion damper disclosed in German Utility Model 89 12 387.5. The damping element and the radial bearing are therein positioned side by side in axial direction. This construction creates a coupling of a relatively large axial length.
It is an aspect of the invention to provide an improved flexible torsion coupling of a shorter axial length.
Accordingly, the invention provides a flexible torsion coupling for two machine elements. The coupling includes a pair of first and second rings, which rings are respectively connected to the two machine elements and radially spaced apart surround each other. A
damping element and a radial bearing are positioned in the radial gap created by the radial spacing of the rings. The first ring has an axially open, U-shaped cross-section and the space defined by the U-shaped first ring is at least partly divided by a second ring into a pair of first chambers, which at least partly surround each other in radial direction. The radial bearing is positioned in one of the first chambers and the damping element is positioned in the other of the first chambers. The damping element and the radial bearing may be positioned to overlap in an axial direction, which provides for a relatively shorter axial length of a torsion coupling in accordance with the invention.
- 204~094 Nonetheless, a good supporting of the rings on each other is guaranteed, which allows the transmission of radial forces and renders the use of such a torsion coupling in connection with pulleys and torsion dampers more suitable.
The damping element may connect two axially spaced apart opposing surfaces of the two rings, which permits the use of a damping element of relatively large dimensions and the transmission of large relative mutual rotations of the rings.
In applications where harder spring characteristics are desired, the damping element preferably connects two radially spaced apart opposing surfaces of the two rings. In such an embodiment, the damping element is preferably rotation- symmetrical and, thus, especially well supported against deformations caused by centrifugal forces.
During the intended application of a torsion coupling in accordance with the invention, the radial bearing may be especially well protected from axial forces, when the bearing and the damping element are positioned in a common radial plane. This is also advantageous with respect to a size reduction of the coupling, which is desired for economic reasons.
Embodiments wherein the radial bearing is a slide bearing are preferred for their advantageous, especially short radial length. On the other hand, if sufficient space is available in radial direction, the use of a deep-groove ball bearing is preferred. Deep-groove ball bearings are available ready for installation and guarantee, in addition to an especially good relative rotatability of the two rings, a good guiding and support of the rings in radial direction.
The second ring may have an annular projection that is radially spaced apart from and surrounds that leg of the U-shaped first ring, which radially outwardly surrounds the second ring. The radial gap 20440~
resulting from the radial spacing of the annular protrusion and the first ring is at least partly divided by a third ring into a pair of second chambers, which second chambers at least partially surround each other in radial direction. A second radial bearing is preferably positioned in one of the second chambers and a second damping element is positioned in the other of the second chambers to relatively rotatably and elastically support the third ring. All the damping elements and radial bearings are preferably positioned in a common radial plane whereby the radial bearings may alternate with the damping elements in radial direction.
The last described embodiment may be generally termed a "cascade-type" construction. This construction may be modified by the addition of supplementary intermediate rings similar to the third ring in the manner described above.
The invention will now be explained by way of example only and with reference to the following drawings, wherein:
Fig. 1 shows a half axial cross-section of a flexible torsion coupling, which is used in a torsion damper and wherein two rings are connected by a damping element which interconnects axially spaced apart surfaces of the rings;
Fig. 2 is a half axial cross-section of an embodiment similar to the one shown in Figure 1, wherein the radial bearing is a slide bearing;
Fig. 3 illustrates a half axial cross-section of an embodiment similar to the one shown in Figure 2, wherein the damping element connects radially spaced apart surfaces of the two rings; and Fig. 4 shows a half axial cross-section of a cascade-type embodiment of a flexible torsion coupling in accordance with the invention.
_ 4 _ 2044094 A preferred embodiment of a flexible torsion coupling in accordance with the invention as shown in Figure 1 is integrated into a fly-wheel torsion damper, which is affixed to an end of a crank-shaft 13 of an internal combustion engine (not illustrated) and includes an inertia ring or fly-wheel ring 14 and a pulley 15.
The flexible torsion coupling generally includes a first ring 1, which has an axially open U-shaped cross-section. The space defined by the U-shaped section is partially divided by a second ring 2 into a pair of radially inner and outer first chambers 5 and 6, whereby the outer chamber 6 partially surrounds the inner charnber 5. Second ring 2 is rigidly connected with pulley 15. A radial bearing 4 is positioned in the radially inner first chamber 5, which bearing is a deep-groove ball bearing and relatively rotatably supports the second ring 2 on the radially inwardly located leg 20 of the U-shaped profile of the first ring. Thus, the pulley 15 is also supported in radial direction and may therefore be used for the take up of belt transmitted forces, since relative radial displacements of the pulley 15 in relation to shaft 13 are prevented by second ring 2 and radial bearing 4.
An annular`damping element 3 is positioned in second chamber 6. Damping element 3 is made of rubber-elastic material and connects two axially spaced apart opposing surfaces of the first and second rings 1,2. Damping element 3 axially connects first and second rings 1 and 2. Ring portion 2a of second ring 2 is relatively non-rotatably connected therewith. It will be readily apparent to the art skilled person that this connection may be achieved by press-fitting or welding. The radially extending sections of damping element 3 extending between the second ring 2 and the ring portion 2a provides for an additional contact surface and, thus, improved fixation of the damping element.
Fly-wheel ring 14 is of L-shaped cross-section and has an axially extending leg 18, which is radially spaced apart from and connected with first ring 1 by a fly-wheel damping element or damping layer 19.
c ~
- 4a - 2 0 4 4 0 9 4 The embodiment shown in Figure 2 is similar in construction to the one described above. However, instead of the deep-groove ball bearing, a slide bearing is used in ~is embodiment. The slide bearing includes a bearing sleeve 4.1, which is rigidly affixed to the second ring 2 and relatively rotatably engages the inner surface of the radially S outer axially extending leg 21 of the U-shaped first ring 20~034 1. The space taken up by the coupling in radial direction is thereby comparatively reduced.
The embodiment shown in Figure 3 is similar in construction to the one described immediately above. However, in contrast to the previous embodiment, wherein axially opposite surfaces are connected by damping element 3, a damping element 3.1 relatively rotatably and elastically connects radially opposite surfaces of the first and second rings 1 and 2. The damping element 3.1, the slide bearing sleeve 4.1 and the pulley 15 are positioned in a common radial plane.
Relative radial displacements of these parts of the coupling are therefore counteracted during the intended uses of the coupling.
Figure 4 shows a schematic illustration of a coupling in accordance with the invention having a cascade-type construction. In this embodiment, as in all the above described embodiments, the outer leg 21 of the U-shaped cross-section of the first ring 1 radially outwardly surrounds the second ring 2. However, second ring 2 further includes an annular protrusion 7, which is radially outwardly spaced from and surrounds the outer axially extending leg 21 of the first ring 1. The resulting radial gap between the annular protrusion 7 and the outer leg 21 of the first ring 1 is at least partially separated by a third ring 8 into a second pair of radially inner and outer chambers 10,9, whereby second radially outer chamber 9 at least partially surrounds second radially inner chamber 10. A second radial bearing 11 is positioned in second outer chamber 9 and a second damping element 12 for the rotatably elastic supporting of the third ring 8 is positioned in the second inner chamber 10.
Thus, damping elements and deep-groove ball bearings alternate in radial direction in this embodiment. This substantially prevents an eccentric compensation movement of the fly-wheel ring 14 relative to shaft 13 upon introduction of belt-transmitted forces. Furthermore, it is possible to include supplementary U-shaped intermediate rings such as third ring 8 and to affix additional fly-wheel rings 16,17 to 20~409~
second ring 2 and third ring 8 and to the intermediate rings. These additional fly-wheel rings may also be used for the introduction of belt-transmitted forces into the flexible torsion coupling.
FLEXIBLE TORSION COUPLING
The invention relates to a flexible torsion coupling for two machine elements, wherein a pair of rings are respectively provided on the machine elements, which rings surround each other at a radial spacing and wherein a damping element of rubber and a radial bearing are positioned in the gap resulting from the radial spacing to connect the rings parallel to each other. Particularly, the invention relates to a flexible torsion coupling for use in, for example, torsion dampers of internal combustion engines.
Such a coupling is used in the torsion damper disclosed in German Utility Model 89 12 387.5. The damping element and the radial bearing are therein positioned side by side in axial direction. This construction creates a coupling of a relatively large axial length.
It is an aspect of the invention to provide an improved flexible torsion coupling of a shorter axial length.
Accordingly, the invention provides a flexible torsion coupling for two machine elements. The coupling includes a pair of first and second rings, which rings are respectively connected to the two machine elements and radially spaced apart surround each other. A
damping element and a radial bearing are positioned in the radial gap created by the radial spacing of the rings. The first ring has an axially open, U-shaped cross-section and the space defined by the U-shaped first ring is at least partly divided by a second ring into a pair of first chambers, which at least partly surround each other in radial direction. The radial bearing is positioned in one of the first chambers and the damping element is positioned in the other of the first chambers. The damping element and the radial bearing may be positioned to overlap in an axial direction, which provides for a relatively shorter axial length of a torsion coupling in accordance with the invention.
- 204~094 Nonetheless, a good supporting of the rings on each other is guaranteed, which allows the transmission of radial forces and renders the use of such a torsion coupling in connection with pulleys and torsion dampers more suitable.
The damping element may connect two axially spaced apart opposing surfaces of the two rings, which permits the use of a damping element of relatively large dimensions and the transmission of large relative mutual rotations of the rings.
In applications where harder spring characteristics are desired, the damping element preferably connects two radially spaced apart opposing surfaces of the two rings. In such an embodiment, the damping element is preferably rotation- symmetrical and, thus, especially well supported against deformations caused by centrifugal forces.
During the intended application of a torsion coupling in accordance with the invention, the radial bearing may be especially well protected from axial forces, when the bearing and the damping element are positioned in a common radial plane. This is also advantageous with respect to a size reduction of the coupling, which is desired for economic reasons.
Embodiments wherein the radial bearing is a slide bearing are preferred for their advantageous, especially short radial length. On the other hand, if sufficient space is available in radial direction, the use of a deep-groove ball bearing is preferred. Deep-groove ball bearings are available ready for installation and guarantee, in addition to an especially good relative rotatability of the two rings, a good guiding and support of the rings in radial direction.
The second ring may have an annular projection that is radially spaced apart from and surrounds that leg of the U-shaped first ring, which radially outwardly surrounds the second ring. The radial gap 20440~
resulting from the radial spacing of the annular protrusion and the first ring is at least partly divided by a third ring into a pair of second chambers, which second chambers at least partially surround each other in radial direction. A second radial bearing is preferably positioned in one of the second chambers and a second damping element is positioned in the other of the second chambers to relatively rotatably and elastically support the third ring. All the damping elements and radial bearings are preferably positioned in a common radial plane whereby the radial bearings may alternate with the damping elements in radial direction.
The last described embodiment may be generally termed a "cascade-type" construction. This construction may be modified by the addition of supplementary intermediate rings similar to the third ring in the manner described above.
The invention will now be explained by way of example only and with reference to the following drawings, wherein:
Fig. 1 shows a half axial cross-section of a flexible torsion coupling, which is used in a torsion damper and wherein two rings are connected by a damping element which interconnects axially spaced apart surfaces of the rings;
Fig. 2 is a half axial cross-section of an embodiment similar to the one shown in Figure 1, wherein the radial bearing is a slide bearing;
Fig. 3 illustrates a half axial cross-section of an embodiment similar to the one shown in Figure 2, wherein the damping element connects radially spaced apart surfaces of the two rings; and Fig. 4 shows a half axial cross-section of a cascade-type embodiment of a flexible torsion coupling in accordance with the invention.
_ 4 _ 2044094 A preferred embodiment of a flexible torsion coupling in accordance with the invention as shown in Figure 1 is integrated into a fly-wheel torsion damper, which is affixed to an end of a crank-shaft 13 of an internal combustion engine (not illustrated) and includes an inertia ring or fly-wheel ring 14 and a pulley 15.
The flexible torsion coupling generally includes a first ring 1, which has an axially open U-shaped cross-section. The space defined by the U-shaped section is partially divided by a second ring 2 into a pair of radially inner and outer first chambers 5 and 6, whereby the outer chamber 6 partially surrounds the inner charnber 5. Second ring 2 is rigidly connected with pulley 15. A radial bearing 4 is positioned in the radially inner first chamber 5, which bearing is a deep-groove ball bearing and relatively rotatably supports the second ring 2 on the radially inwardly located leg 20 of the U-shaped profile of the first ring. Thus, the pulley 15 is also supported in radial direction and may therefore be used for the take up of belt transmitted forces, since relative radial displacements of the pulley 15 in relation to shaft 13 are prevented by second ring 2 and radial bearing 4.
An annular`damping element 3 is positioned in second chamber 6. Damping element 3 is made of rubber-elastic material and connects two axially spaced apart opposing surfaces of the first and second rings 1,2. Damping element 3 axially connects first and second rings 1 and 2. Ring portion 2a of second ring 2 is relatively non-rotatably connected therewith. It will be readily apparent to the art skilled person that this connection may be achieved by press-fitting or welding. The radially extending sections of damping element 3 extending between the second ring 2 and the ring portion 2a provides for an additional contact surface and, thus, improved fixation of the damping element.
Fly-wheel ring 14 is of L-shaped cross-section and has an axially extending leg 18, which is radially spaced apart from and connected with first ring 1 by a fly-wheel damping element or damping layer 19.
c ~
- 4a - 2 0 4 4 0 9 4 The embodiment shown in Figure 2 is similar in construction to the one described above. However, instead of the deep-groove ball bearing, a slide bearing is used in ~is embodiment. The slide bearing includes a bearing sleeve 4.1, which is rigidly affixed to the second ring 2 and relatively rotatably engages the inner surface of the radially S outer axially extending leg 21 of the U-shaped first ring 20~034 1. The space taken up by the coupling in radial direction is thereby comparatively reduced.
The embodiment shown in Figure 3 is similar in construction to the one described immediately above. However, in contrast to the previous embodiment, wherein axially opposite surfaces are connected by damping element 3, a damping element 3.1 relatively rotatably and elastically connects radially opposite surfaces of the first and second rings 1 and 2. The damping element 3.1, the slide bearing sleeve 4.1 and the pulley 15 are positioned in a common radial plane.
Relative radial displacements of these parts of the coupling are therefore counteracted during the intended uses of the coupling.
Figure 4 shows a schematic illustration of a coupling in accordance with the invention having a cascade-type construction. In this embodiment, as in all the above described embodiments, the outer leg 21 of the U-shaped cross-section of the first ring 1 radially outwardly surrounds the second ring 2. However, second ring 2 further includes an annular protrusion 7, which is radially outwardly spaced from and surrounds the outer axially extending leg 21 of the first ring 1. The resulting radial gap between the annular protrusion 7 and the outer leg 21 of the first ring 1 is at least partially separated by a third ring 8 into a second pair of radially inner and outer chambers 10,9, whereby second radially outer chamber 9 at least partially surrounds second radially inner chamber 10. A second radial bearing 11 is positioned in second outer chamber 9 and a second damping element 12 for the rotatably elastic supporting of the third ring 8 is positioned in the second inner chamber 10.
Thus, damping elements and deep-groove ball bearings alternate in radial direction in this embodiment. This substantially prevents an eccentric compensation movement of the fly-wheel ring 14 relative to shaft 13 upon introduction of belt-transmitted forces. Furthermore, it is possible to include supplementary U-shaped intermediate rings such as third ring 8 and to affix additional fly-wheel rings 16,17 to 20~409~
second ring 2 and third ring 8 and to the intermediate rings. These additional fly-wheel rings may also be used for the introduction of belt-transmitted forces into the flexible torsion coupling.
Claims (14)
1. A flexible portion coupling for a pair of machine elements and having an axis of rotation, comprising first and second mutually surrounding, radially spaced apart rings respectively attachable to the machine elements and defining an intermediate gap, a damping element and a radial bearing positioned in the intermediate gap for relatively rotatably connecting the first and second rings, the first ring having a U-shaped cross-section and defining an annular space, the annular space being opened in axial direction of the coupling and being divided by the second ring into a first pair of inner and outer chambers which at least partly surround one another in radial direction, and the radial bearing being positioned in one of the first inner and outer chambers and a dampening element being positioned in the other of the first inner and outer chambers.
2. A coupling as defined in Claim 1, wherein the damping element connects a pair of radially opposite, spaced apart surfaces of the first and second rings.
3. A coupling as defined in Claim 1, wherein the damping element connects a pair of radially opposite, spaced apart surfaces of the first and second rings.
4. A coupling as defined in Claim 3, wherein the damping element and the radial bearing are positioned in a common radial plane.
5. A coupling as defined in Claim 1, 2, 3 or 4, wherein the radial bearing is a slide bearing.
6. A coupling as defined in Claim 1, 2, 3 or 4, wherein the radial bearing is a deep-groove ball bearing.
7. A coupling as defined in Claim 1, 2, 3 or 4, wherein the second ring has an annular projection that is radially spaced apart from and surrounds that leg of the U-shaped profile of the first ring which radially outwardly surrounds the second ring, wherein the annular gap resulting from the radial spacing of the annular protrusion and the second ring is at least partly divided by a third ring into a pair of second chambers, which at least partially surround each other in radial direction, and wherein a second radial bearing is provided in one of the second chambers and a second damping element is provided in the other of the second chambers for relatively rotatably and elastically supporting the third ring.
8. A coupling as defined in Claim 5, wherein the second ring has an annular projection that is radially spaced apart from and surrounds that leg of the U-shaped profile of the first ring which radially outwardly surrounds the second ring, wherein the annular gap resulting from the radial spacing of the annular protrusion and the second ring is at least partly divided by a third ring into a pair of second chambers, which at least partially surround each other in radial direction, and wherein a second radial bearing is provided in one of the second chambers and a second damping element is provided in the other of the second chambers for relatively rotatably and elastically supporting the third ring.
9. A coupling as defined in Claim 6, wherein the second ring has an annular projection that is radially spaced apart from and surrounds that leg of the U-shaped profile of the first ring which radially outwardly surrounds the second ring, wherein the radial gap resulting from the radial spacing of the annular protrusion and the second ring is at least partly divided by a third ring into a pair of second chambers, which at least partially surround each other in radial direction, and wherein a second radial bearing is provided in one of the second chambers and a second damping element is provided in the other of the second chambers for relatively rotatably and elastically supporting the third ring.
10. A flexible portion coupling for a pair of machine elements and having an axis of rotation, comprising first and second mutually surrounding, radially spaced apart rings respectively attachable to the machine elements and defining an intermediate gap, a damping element and a radial bearing positioned in the intermediate gap for relatively rotatably connecting the first and second rings, the first ring having a U-shaped cross-section and an inertia ring affixed to one of the first and second rings by an intermediate damping layer made of rubbery material, and defining an annular space, the annular space being opened in axial direction of the coupling and being divided by the second ring into a first pair of inner and outer chambers which at least partly surround one another in radial direction, and the radial bearing being positioned in one of the first inner and outer chambers and a dampening element being positioned in the other of the first inner and outer chambers.
11. A coupling as defined in claim 10, wherein the damping layer connects a contact surface of the inertia ring with a radially opposite contact surface of the one of the first and second rings associated with the inertia ring.
12. A coupling as defined in claim 11, wherein the inertia ring in cross-section has an axial leg which extends parallel to the axis of the coupling, the contact surface of the inertia ring being a surface of the leg.
13. A coupling as defined in claim 10 or 11, wherein the inertia ring in cross-section has an axial leg which extends parallel to the axis of the coupling, and the other of the first and second rings is spaced apart from and in radial direction surrounds the axial leg of the inertia ring.
14. A coupling as defined in claim 12, wherein the inertia ring in cross-section has an axial leg which extends parallel to the axis of the coupling, and the other of the first and second rings is spaced apart from and in radial direction surrounds the axial leg of the inertia ring.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DEP4018596.6 | 1990-06-09 | ||
| DE4018596A DE4018596A1 (en) | 1990-06-09 | 1990-06-09 | TURN-ELASTIC CLUTCH |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2044094A1 CA2044094A1 (en) | 1991-12-10 |
| CA2044094C true CA2044094C (en) | 1995-01-17 |
Family
ID=6408164
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002044094A Expired - Fee Related CA2044094C (en) | 1990-06-09 | 1991-06-07 | Flexible torsion coupling |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0462356B1 (en) |
| JP (1) | JPH04231751A (en) |
| CA (1) | CA2044094C (en) |
| DE (2) | DE4018596A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101949423A (en) * | 2010-09-09 | 2011-01-19 | 东南大学 | Viscoelastic damping anti-torque vibration damper |
Families Citing this family (24)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4025848A1 (en) * | 1990-08-16 | 1992-02-20 | Pahl Gummi Asbest | TURNING VIBRATION |
| DE4225304B4 (en) * | 1991-08-07 | 2009-01-08 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Disk-shaped component |
| DE4311939C2 (en) * | 1993-04-10 | 1995-08-17 | Freudenberg Carl Fa | Torsional vibration damper |
| DE4312577C1 (en) * | 1993-04-17 | 1994-08-18 | Freudenberg Carl Fa | Torsionally elastic coupling |
| GB2277359A (en) * | 1993-04-20 | 1994-10-26 | Luk Lamellen & Kupplungsbau | A vibration damping and tensioning mechanism for a belt or chain drive |
| DE4420178B4 (en) * | 1993-06-16 | 2006-12-07 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | drive Windscreen |
| DE4322710A1 (en) * | 1993-07-08 | 1995-01-12 | Pahl Gummi Asbest | Belt-pulley decoupling system for piston engines |
| DE4400564C1 (en) * | 1994-01-11 | 1995-04-20 | Freudenberg Carl Fa | Torsionally elastic coupling |
| DE4404255C2 (en) * | 1994-02-10 | 1999-07-08 | Freudenberg Carl Fa | Method for producing a pressed-in torsional vibration damper |
| DE4404311C1 (en) * | 1994-02-11 | 1995-04-13 | Freudenberg Carl Fa | Torsional vibration damper |
| DE4408474C1 (en) * | 1994-03-12 | 1995-04-20 | Freudenberg Carl Fa | Torsionally elastic coupling |
| DE4430393C5 (en) * | 1994-08-26 | 2011-06-30 | Carl Freudenberg KG, 69469 | Torsionally flexible coupling with integrated torsional vibration damper |
| FR2730782B1 (en) * | 1995-02-17 | 1997-04-25 | Dampers | DRIVE DEVICE COMPRISING A TORSIONAL VIBRATION DAMPER |
| DE19506454C1 (en) * | 1995-02-24 | 1996-05-02 | Freudenberg Carl Fa | Torsionally elastic coupling with rotation axis |
| DE10013699C1 (en) * | 2000-03-21 | 2001-08-09 | Freudenberg Carl Fa | Drive belt disc for IC engine crankshaft has disc bearing fitted in radial gap between projection of visco-oscillation damper housing and drive belt disc |
| DE10056661C2 (en) * | 2000-11-15 | 2003-04-10 | Freudenberg Carl Kg | Damping device for a torsionally flexible coupling |
| DE10057822C2 (en) * | 2000-11-21 | 2003-04-10 | Freudenberg Carl Kg | Damping device for a torsionally flexible coupling |
| DE10059226C1 (en) * | 2000-11-29 | 2002-03-07 | Freudenberg Carl Kg | Damping device for rotary elastic coupling has relatively rotatable inner and outer rings with intermediate pressure element acting on pressure medium chamber communicating with equalization chamber |
| DE10064332C1 (en) * | 2000-12-21 | 2002-03-14 | Freudenberg Carl Kg | Damping device for rotary elastic coupling has working chamber compressed via pressure block for pressing friction coating against counter-surface for damping torsional oscillation |
| GB2382395A (en) * | 2001-11-21 | 2003-05-28 | Metaldyne Internat | A device for isolating fluctuations in the drive torque of a rotary drive shaft |
| DE102004035969C5 (en) * | 2004-07-23 | 2019-06-19 | Vibracoustic Gmbh | Decoupled pulley |
| JP4572739B2 (en) | 2005-05-20 | 2010-11-04 | 株式会社ジェイテクト | Rotation fluctuation absorbing damper pulley |
| DE102006034892A1 (en) * | 2006-07-25 | 2008-01-31 | A. Friedr. Flender Ag | Elastic coupling i.e. clutch, for vehicle, has guide bearings for guiding coupling halves during breakdown of rubber disk unit, where guide bearings are arranged at axial distance from rubber disk unit |
| EP3299645B1 (en) * | 2016-09-26 | 2019-04-17 | Rudolf Gehring | Slewing bearing on base of sliding bearing with drive structures |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE680988C (en) * | 1934-09-21 | 1939-09-13 | Getefo Ges Fuer Tech Fortschri | Elastic coupling |
| US3628352A (en) * | 1970-07-09 | 1971-12-21 | Gates Rubber Co | Flexible coupling |
| DE3012411A1 (en) * | 1980-03-29 | 1981-10-08 | Hackforth GmbH & Co KG, 4690 Herne | ELASTIC SHAFT COUPLING, IN PARTICULAR JOINT SHAFT ADJUSTMENT COUPLING |
| GB2120749B (en) * | 1982-05-21 | 1986-09-24 | Flexibox Ltd | Improvements in flexible couplings |
| ZA863782B (en) * | 1986-05-21 | 1988-01-27 | Ludwig Maier | Coupling |
| DE3834919A1 (en) * | 1988-10-13 | 1990-04-19 | Man Nutzfahrzeuge Ag | DRIVETRAIN WITH TURN-ELASTIC CLUTCH AND PTO SHAFT |
| DE8912387U1 (en) * | 1989-10-18 | 1990-01-04 | MAGNA INTERNATIONAL GmbH, 6460 Gelnhausen | Torsional vibration dampened pulley |
-
1990
- 1990-06-09 DE DE4018596A patent/DE4018596A1/en active Granted
-
1991
- 1991-02-01 EP EP91101333A patent/EP0462356B1/en not_active Expired - Lifetime
- 1991-02-01 DE DE91101333T patent/DE59100550D1/en not_active Expired - Fee Related
- 1991-06-07 CA CA002044094A patent/CA2044094C/en not_active Expired - Fee Related
- 1991-06-07 JP JP3136138A patent/JPH04231751A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101949423A (en) * | 2010-09-09 | 2011-01-19 | 东南大学 | Viscoelastic damping anti-torque vibration damper |
Also Published As
| Publication number | Publication date |
|---|---|
| DE59100550D1 (en) | 1993-12-09 |
| CA2044094A1 (en) | 1991-12-10 |
| DE4018596C2 (en) | 1992-09-03 |
| JPH04231751A (en) | 1992-08-20 |
| EP0462356A1 (en) | 1991-12-27 |
| EP0462356B1 (en) | 1993-11-03 |
| DE4018596A1 (en) | 1991-12-19 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| MKLA | Lapsed |