CA1101695A - Torsional vibration damper - Google Patents
Torsional vibration damperInfo
- Publication number
- CA1101695A CA1101695A CA323,267A CA323267A CA1101695A CA 1101695 A CA1101695 A CA 1101695A CA 323267 A CA323267 A CA 323267A CA 1101695 A CA1101695 A CA 1101695A
- Authority
- CA
- Canada
- Prior art keywords
- housing
- disc
- hub
- damper
- ring
- 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
- 239000012530 fluid Substances 0.000 claims abstract description 11
- 238000013016 damping Methods 0.000 claims abstract description 7
- 150000001875 compounds Chemical class 0.000 claims description 5
- 229920001296 polysiloxane Polymers 0.000 description 8
- 230000007812 deficiency Effects 0.000 description 3
- 230000006866 deterioration Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000033001 locomotion Effects 0.000 description 2
- CWYNVVGOOAEACU-UHFFFAOYSA-N Fe2+ Chemical compound [Fe+2] CWYNVVGOOAEACU-UHFFFAOYSA-N 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000004075 alteration Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000002508 compound effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010348 incorporation Methods 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 238000010008 shearing Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000002277 temperature effect Effects 0.000 description 1
Landscapes
- Mechanical Operated Clutches (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
A viscous torsional vibration damper is provided for a rotatable shaft. A hub is attachabe to the shaft. A
housing is connected to the hub and has an internal cham-ber. An inertia disc is within the chamber and a fluid damping medium is placed between the inertia disc and the housing. A first set of springs for tuning the damper are connected between the housing and the hub and a second set of springs for tuning the damper are provided between the disc and the housing.
A viscous torsional vibration damper is provided for a rotatable shaft. A hub is attachabe to the shaft. A
housing is connected to the hub and has an internal cham-ber. An inertia disc is within the chamber and a fluid damping medium is placed between the inertia disc and the housing. A first set of springs for tuning the damper are connected between the housing and the hub and a second set of springs for tuning the damper are provided between the disc and the housing.
Description
This invention relates to torsional vibration dampers for rotatable shafts.
It is known to provide a tuned torsional vibration damper for attachment to a reciprocating engine crankshaft or any rotating part of a power transmission system sub-jected to torsional vibration. Prior art torsional dampers have, however, displayed certain deficiencies. For example~
non-metallic tuning elements have been known to be limited to a relatively short life due to their intrinsic ~ehaviour under high-cycle distortion and high temperatures; both common conditions in viscous dampersO Non-metallic tuning elements have also been known to undergo drastic changes in stiffness characteristics with age, vibration amplitude and temperature, causing significant deterioration of damper effectiveness.
Tuned dampers which rely on non-fixed leaf or spoke springs, such as disclosed in U.S. Patent 3~5777802 to Rumsey, display wear and abrasion at points of sliding contact, inderminate and variable interleaf friction7 non-20 linearity of stiffness, and adverse effects on the ease of ;}
analytical modelling, when laminated springs are used7 and large amounts of lost space which should be available for the interia disc.
Tuned dampers, such as disclosed in United States Patent 3,653,278 to Brinkman, utilizing the visco-elastic properties of silicone fluids7 are subject to alteration in tuning with the inevitable deterioration of the silicone fluid under the shearing end temperature effects found in torsional dampersO The gradual loss in damping capability 3o of a silicone ~luid can normally be tolerated to a limited ;
~ ~3~, , ex~ent by itself. When the silicone fluid is used or tuning, however, the deterioration of the fluid has the compound effect of loss in damping and tuning characteris-tics.
A form of torsional damper utilizing resilient tuning means is found is U.S. Patent 2,724,983 to O'Connor~
The use of a torsional shaft, as disclosed by o'Connor, requires additional bearing support for the damper and an overall damper length which is unacceptable for many appli-cations.
According to the invention, a compound tuned, viscous torsional vibration damper comprises a central hub for connecting the damper to a rotatable shaft; and a hollow cylindrical housing with an annular inner wall surrounding the hub, an annular outer wall and disc-shaped side walls.
An annular-shaped inertia disc is within the housingO There is a bearing between the inner wall of the housing and the inertia disc for rotation of the inertia disc within the housing. A viscous damping fluid is between the disc and the housing. Disc tuning means resiliently connects the disc and the housing~ Housing tuning means resilient connects the hub and the housing.
Viscous dampers with coil springs under compres-sion at all times, thus providing a constant stiffness or tuning effect~ reduce the damper hub vibratory amplitude, when compared with system employing untuned viscous dampers, by as much 35%-45%~ By the incorporation of housing tuning, for example~ when the hub comprises an inner part resi-liently connected to an outer part by spGke springs~ the invention allows for compound tuning of the damper and the vibratory amplitude can be reduced anokher 40% approxi-mately.
The use of coil springs or spoke springs fixedly attached to two ends overcomes the deficiencies in tuned dampers relying on non-fixed leaf or spoke springs. Addi-tionally, the dampers according to the present invention are considerably more compact than those using a torsional shaft as the resilient tuning means. Further, the deficiencies related to torsional vibration dampers, utilizing the visco-elastic properties of silicone fluids for tuning, areovercome by the resilient tuning employed in the present invention.
Aspects of the invention are illustrated b~ way of example, in the drawings, in which:
Figure 1 is a side elevational sectional view of a first embodiment of the invention;
Figure 2 is an end section view of the top half of the embodiment illustrated in Figure l;
Figure 3 is a side elevational view of a second embodiment of the invention, equivalent to Figure l;
Figure 4 is a side sectional view of part of a third embodiment of the invention showing a portion of the inertia disc, a portion of a coil spring and permanent magnet;
Figure 5 on the first sheet of drawings, is a portion of the embodiment illustrated in Figure 1 but showing non-integral spoke springs;
Figure 6 is a portion of the embodiment shown in Figure 3 but including nonintegral spoke springs;
Figure 7 shows an embodiment similar to the embodi-ment illustrated in Figure 1 but showing coil springs instead of spoke springs adjacent the hub;
-~3-6~5 Figure 8, on the fi.rst sheet of drawings, shows a portion of an embodiment similar to the embodiment shown in Figure 1 but including limit stop means for limiting move-ment of the hub relative to the housing;
Figure 9 shows an embodiment similar to that shown in Figure 1 but without spoke springs;
Figure 10 illustrates an embodiment of the in-vention similar to Figure 1, but excluding the coil springs connecting the disc to the housing; and Figure 11 t on the second sheet of the drawings, shows a portion of an embodiment of the invention similar to the embodiment illustrated in Figure 3 but wherein the resilient spoke springs connect the outer wall of the housing and the inertia disc.
A torsional vibration damper, according to a first embodiment of the invention, is shown in Figures 1 and 2.
The viscous damper comprises a hub 1 attachable to a shaft by means of bolt holes 2. The hub 1 is attached to ring 3 by means of eight spoke springs 4. A housing 5 comprises annular inner wall 6, annular outer wall 7 and disc-shaped side walls 8 and 9 connecting inner wall 6 to outer wall 7O
The inner wall 6 of the housing 5 is connected to the hub 1 by means of ring 3 and spoke springs 4. Dowels 10 are place~ between inner wall 6 and ring 3 to prevent movement between the hub 1 and the housing 5~
Inner wall 6; outer wall 7 and side walls 8 and 9 of housing 5 define an internal chamber 11~ Within chamber 11 is annular-shaped inertia disc 12~ A portion 13 of the disc 12 is lead filled to increase the inertia effect. A
space 14 between outer wall 7, and side walls 8 and 9 of s housing 5 and inertia disc 12 is filled with silicone fluid.
The silicone fluid comprises the damping medium of the viscous damper. The inertia disc 12 has two diametrically opposing slots 19 and 20 on opposite sides of the hub 1.
The slot 19 is defined by an outside wall 21 and end walls
It is known to provide a tuned torsional vibration damper for attachment to a reciprocating engine crankshaft or any rotating part of a power transmission system sub-jected to torsional vibration. Prior art torsional dampers have, however, displayed certain deficiencies. For example~
non-metallic tuning elements have been known to be limited to a relatively short life due to their intrinsic ~ehaviour under high-cycle distortion and high temperatures; both common conditions in viscous dampersO Non-metallic tuning elements have also been known to undergo drastic changes in stiffness characteristics with age, vibration amplitude and temperature, causing significant deterioration of damper effectiveness.
Tuned dampers which rely on non-fixed leaf or spoke springs, such as disclosed in U.S. Patent 3~5777802 to Rumsey, display wear and abrasion at points of sliding contact, inderminate and variable interleaf friction7 non-20 linearity of stiffness, and adverse effects on the ease of ;}
analytical modelling, when laminated springs are used7 and large amounts of lost space which should be available for the interia disc.
Tuned dampers, such as disclosed in United States Patent 3,653,278 to Brinkman, utilizing the visco-elastic properties of silicone fluids7 are subject to alteration in tuning with the inevitable deterioration of the silicone fluid under the shearing end temperature effects found in torsional dampersO The gradual loss in damping capability 3o of a silicone ~luid can normally be tolerated to a limited ;
~ ~3~, , ex~ent by itself. When the silicone fluid is used or tuning, however, the deterioration of the fluid has the compound effect of loss in damping and tuning characteris-tics.
A form of torsional damper utilizing resilient tuning means is found is U.S. Patent 2,724,983 to O'Connor~
The use of a torsional shaft, as disclosed by o'Connor, requires additional bearing support for the damper and an overall damper length which is unacceptable for many appli-cations.
According to the invention, a compound tuned, viscous torsional vibration damper comprises a central hub for connecting the damper to a rotatable shaft; and a hollow cylindrical housing with an annular inner wall surrounding the hub, an annular outer wall and disc-shaped side walls.
An annular-shaped inertia disc is within the housingO There is a bearing between the inner wall of the housing and the inertia disc for rotation of the inertia disc within the housing. A viscous damping fluid is between the disc and the housing. Disc tuning means resiliently connects the disc and the housing~ Housing tuning means resilient connects the hub and the housing.
Viscous dampers with coil springs under compres-sion at all times, thus providing a constant stiffness or tuning effect~ reduce the damper hub vibratory amplitude, when compared with system employing untuned viscous dampers, by as much 35%-45%~ By the incorporation of housing tuning, for example~ when the hub comprises an inner part resi-liently connected to an outer part by spGke springs~ the invention allows for compound tuning of the damper and the vibratory amplitude can be reduced anokher 40% approxi-mately.
The use of coil springs or spoke springs fixedly attached to two ends overcomes the deficiencies in tuned dampers relying on non-fixed leaf or spoke springs. Addi-tionally, the dampers according to the present invention are considerably more compact than those using a torsional shaft as the resilient tuning means. Further, the deficiencies related to torsional vibration dampers, utilizing the visco-elastic properties of silicone fluids for tuning, areovercome by the resilient tuning employed in the present invention.
Aspects of the invention are illustrated b~ way of example, in the drawings, in which:
Figure 1 is a side elevational sectional view of a first embodiment of the invention;
Figure 2 is an end section view of the top half of the embodiment illustrated in Figure l;
Figure 3 is a side elevational view of a second embodiment of the invention, equivalent to Figure l;
Figure 4 is a side sectional view of part of a third embodiment of the invention showing a portion of the inertia disc, a portion of a coil spring and permanent magnet;
Figure 5 on the first sheet of drawings, is a portion of the embodiment illustrated in Figure 1 but showing non-integral spoke springs;
Figure 6 is a portion of the embodiment shown in Figure 3 but including nonintegral spoke springs;
Figure 7 shows an embodiment similar to the embodi-ment illustrated in Figure 1 but showing coil springs instead of spoke springs adjacent the hub;
-~3-6~5 Figure 8, on the fi.rst sheet of drawings, shows a portion of an embodiment similar to the embodiment shown in Figure 1 but including limit stop means for limiting move-ment of the hub relative to the housing;
Figure 9 shows an embodiment similar to that shown in Figure 1 but without spoke springs;
Figure 10 illustrates an embodiment of the in-vention similar to Figure 1, but excluding the coil springs connecting the disc to the housing; and Figure 11 t on the second sheet of the drawings, shows a portion of an embodiment of the invention similar to the embodiment illustrated in Figure 3 but wherein the resilient spoke springs connect the outer wall of the housing and the inertia disc.
A torsional vibration damper, according to a first embodiment of the invention, is shown in Figures 1 and 2.
The viscous damper comprises a hub 1 attachable to a shaft by means of bolt holes 2. The hub 1 is attached to ring 3 by means of eight spoke springs 4. A housing 5 comprises annular inner wall 6, annular outer wall 7 and disc-shaped side walls 8 and 9 connecting inner wall 6 to outer wall 7O
The inner wall 6 of the housing 5 is connected to the hub 1 by means of ring 3 and spoke springs 4. Dowels 10 are place~ between inner wall 6 and ring 3 to prevent movement between the hub 1 and the housing 5~
Inner wall 6; outer wall 7 and side walls 8 and 9 of housing 5 define an internal chamber 11~ Within chamber 11 is annular-shaped inertia disc 12~ A portion 13 of the disc 12 is lead filled to increase the inertia effect. A
space 14 between outer wall 7, and side walls 8 and 9 of s housing 5 and inertia disc 12 is filled with silicone fluid.
The silicone fluid comprises the damping medium of the viscous damper. The inertia disc 12 has two diametrically opposing slots 19 and 20 on opposite sides of the hub 1.
The slot 19 is defined by an outside wall 21 and end walls
2~ and 23. Slot 20 is defined by outside wall 24 and end walls 25 and 26. Retaining plates 27, 28, 29 and 30 are connected to end walls 22, 237 25 and 26 respectively.
Abutment plates 31 and 32 are connected to inner wall 6 of housing 5~ Abutment plate 31 projects into slot 19 halfway between end wall 22 and end wall 23. Abutment plate 32 projects into slot 20 half way between end wall 25 and end wall 26. Coil spring 15 is compressed between abutment plate 31 and retaining plate 27 and coil spring 16 is com-pressed between abutment plate 31 and retaining plate 28.
Likewise, coil spring 17 is compressed between abutment plate 32 and retaining plate 29 and coil ~pring 18 is compressed between abutment plate 32 and retaining plate 30. Because inertia disc 12 is connected to inner wall 6 of housing 5 through coil springs 15, 16, 17, and 18, inertia disc 12 is rotatably movable with respect to inner wall 60 For this reason, bearing 33 is provided on housing 3.
Eight spoke springs 4 are formed integrally with the hub 1 and the ring 3. Compound tuning of the damper according to the first embodiment oE the invention is possible since two means of tuning are providedO Firstly~
the housing 5 may be tuned with respect to the hub 1 by altering the size and configuration of spoke springs 4.
Secondly7 the inertia disc 12 may be tuned with respect to the housing 5 by altering the size and configuration of coil springs 15, 16, 17, and 18.
A torsional vibration damper according to a second embodiment of the invention i5 shown in Figure 3. The second embodiment of the invention will be described only with respect to the differences between it and the first embodiment. Hub 34 is connectable to a shaft by means of bolt holes 35. Housing 36 has an annular outer wall 37 and an annular inner wall 38. The housing 36 has side walls similar to side walls 8 and 9 in Figure 2~ Inner wall 38 is fixedly connected to hub 34 and rotatable therewith~ Ring 40 is connected to the inner wall 38 of the housing 36 and rotatable therewith. Spoke springs 43 are fixedly connected to inertia disc 39 at one end within radially oriented slots 42 and fixedly connected to ring 40 at the other end, spoke springs 43, ring 40, and disc 39 being integral in the present embodiment. Space 41 between inertia disc 39 and outer wall 37 is filled with silicone damping fluid. It should be noted that no bearings are required in the second embodiment of the invention.
In a third embodiment of the invention, shown in Figure 4, permanent magnets 44 (only one of which is shown) are provided in cavities 45 at each end of each coil spring 46, (only one of which is shown) to pick up ferrous par-ticles resulting from wear of the components. The magnets 44 are the full width of the disc 46.
A fourth embodiment of the invention, shown in Figure 5, is similar to the first embodiment of the in-vention shown in Figure 1 but spokes springs 4 are non-integral with the hub 1 and the ring 3~ Instead~ spokes 4 are press fitted into ~lots 5C in ring 3 and slots 52 in hub 1.
6~5 Figure 6 illustrates a fifth embodiment of the invention similar to the embodiment shown in Figure 3 but including non-integral spoke springs. Spoke springs 43 are press fitted into slots 54 in disc 38 and into slots 56 in in ring 40.
Figure 7 illustrates an embodiment of the in-vention similar to that shown in Figure l but including coil springs 58 resiliently connecting the hub 1 to the ring 3O
Only the central portion of the embodiment adjacent the hub is shown. Coil springs 58 are each compressed between projections 60 on ring 3 and projections 61 on hub 1.
Projections 61 have an end 64 providing a bearing surface for ring 3. Also, projections 60 have an end 66 providing bearing surfaces for hub 1.
Figure 8 illustrates a sixth embodiment of the invention similar to Figure l but including limit stops between hub 1 and ring 3. Only a portion of the hub and ring are shown and one limit stop, though a plurality of stops may be employed. The limit stop includes projection 68 on hub l and engaging element 70 attached to ring 3 having a recess 72. The rotation of hub 1 relative to ring
Abutment plates 31 and 32 are connected to inner wall 6 of housing 5~ Abutment plate 31 projects into slot 19 halfway between end wall 22 and end wall 23. Abutment plate 32 projects into slot 20 half way between end wall 25 and end wall 26. Coil spring 15 is compressed between abutment plate 31 and retaining plate 27 and coil spring 16 is com-pressed between abutment plate 31 and retaining plate 28.
Likewise, coil spring 17 is compressed between abutment plate 32 and retaining plate 29 and coil ~pring 18 is compressed between abutment plate 32 and retaining plate 30. Because inertia disc 12 is connected to inner wall 6 of housing 5 through coil springs 15, 16, 17, and 18, inertia disc 12 is rotatably movable with respect to inner wall 60 For this reason, bearing 33 is provided on housing 3.
Eight spoke springs 4 are formed integrally with the hub 1 and the ring 3. Compound tuning of the damper according to the first embodiment oE the invention is possible since two means of tuning are providedO Firstly~
the housing 5 may be tuned with respect to the hub 1 by altering the size and configuration of spoke springs 4.
Secondly7 the inertia disc 12 may be tuned with respect to the housing 5 by altering the size and configuration of coil springs 15, 16, 17, and 18.
A torsional vibration damper according to a second embodiment of the invention i5 shown in Figure 3. The second embodiment of the invention will be described only with respect to the differences between it and the first embodiment. Hub 34 is connectable to a shaft by means of bolt holes 35. Housing 36 has an annular outer wall 37 and an annular inner wall 38. The housing 36 has side walls similar to side walls 8 and 9 in Figure 2~ Inner wall 38 is fixedly connected to hub 34 and rotatable therewith~ Ring 40 is connected to the inner wall 38 of the housing 36 and rotatable therewith. Spoke springs 43 are fixedly connected to inertia disc 39 at one end within radially oriented slots 42 and fixedly connected to ring 40 at the other end, spoke springs 43, ring 40, and disc 39 being integral in the present embodiment. Space 41 between inertia disc 39 and outer wall 37 is filled with silicone damping fluid. It should be noted that no bearings are required in the second embodiment of the invention.
In a third embodiment of the invention, shown in Figure 4, permanent magnets 44 (only one of which is shown) are provided in cavities 45 at each end of each coil spring 46, (only one of which is shown) to pick up ferrous par-ticles resulting from wear of the components. The magnets 44 are the full width of the disc 46.
A fourth embodiment of the invention, shown in Figure 5, is similar to the first embodiment of the in-vention shown in Figure 1 but spokes springs 4 are non-integral with the hub 1 and the ring 3~ Instead~ spokes 4 are press fitted into ~lots 5C in ring 3 and slots 52 in hub 1.
6~5 Figure 6 illustrates a fifth embodiment of the invention similar to the embodiment shown in Figure 3 but including non-integral spoke springs. Spoke springs 43 are press fitted into slots 54 in disc 38 and into slots 56 in in ring 40.
Figure 7 illustrates an embodiment of the in-vention similar to that shown in Figure l but including coil springs 58 resiliently connecting the hub 1 to the ring 3O
Only the central portion of the embodiment adjacent the hub is shown. Coil springs 58 are each compressed between projections 60 on ring 3 and projections 61 on hub 1.
Projections 61 have an end 64 providing a bearing surface for ring 3. Also, projections 60 have an end 66 providing bearing surfaces for hub 1.
Figure 8 illustrates a sixth embodiment of the invention similar to Figure l but including limit stops between hub 1 and ring 3. Only a portion of the hub and ring are shown and one limit stop, though a plurality of stops may be employed. The limit stop includes projection 68 on hub l and engaging element 70 attached to ring 3 having a recess 72. The rotation of hub 1 relative to ring
3 is limited by the coaction of projection 68 with the recess 72.
An eighth embodiment of the invention illustrated in Figure 9 which is similar to the embodiment sh3wn in Figure 1 and like paxts are numbered the same~ In this embodiment, however~ spoke springs 4 have been removed and replaced with a solid hub 1~ This embodiment does not provide for compound tuniny but resilient tuning between the disc 12 and housing 5 is possible by means of the four coil ~6~ S
springs 15, 16, 17, and 18.
Figure 10 illustrates a ninth embodlment of the invention generally the same as the embodiment shown in Figure 1 and like parts are numbered the same. In this embodiment, however, the coil springs are omitted and the disc 12 is not connected to the hub 1. This damper is tuned by means of spoke springs 4 between the ring 3 and hub 1.
A tenth embodiment of the invention is illustrated in Figure 11. This embodiment is similar to that shown in Figure 3 but including a ring 76 fixedly attached to outer wall 37 of housing 36 and rotatable therewith. Spoke springs 78 (only one of which is shown) are fixedly attached at one end to ring 76 and at the other end to inertia disc 74, the inertia disc 74, spoke springs 78, the ring 76 being integral in the present embodiment. A gap 80 for viscous fluid is provided between disc 72 and inner wall 38.
In a further embodimen'c of the invention, the ring 40, in the embodiment shown in Figure 6~ is integral with the inner wall 38.
In another embodiment of the invention7 ring 3~ in the embodiment shown in Figur~ 5, is integral with the inner wall 6 of the housing 5 shown in Figure 1.
In another embodiment of the invention~ the bearing 33, shown in Figure 1, is provided on inertia disc 12 instead of on housing 3O
In another embodiment of the invention, the embodiment of the invention illustrated in Figure 3 could have spoke springs similar to spokes springs 4 between hub 1 and ring 3 as shown in Figure lo 6~
While each of the above embodiment~ includes only one inertia disc, alternative embodiments of the invention include more than one inertia disc in one damperO
An eighth embodiment of the invention illustrated in Figure 9 which is similar to the embodiment sh3wn in Figure 1 and like paxts are numbered the same~ In this embodiment, however~ spoke springs 4 have been removed and replaced with a solid hub 1~ This embodiment does not provide for compound tuniny but resilient tuning between the disc 12 and housing 5 is possible by means of the four coil ~6~ S
springs 15, 16, 17, and 18.
Figure 10 illustrates a ninth embodlment of the invention generally the same as the embodiment shown in Figure 1 and like parts are numbered the same. In this embodiment, however, the coil springs are omitted and the disc 12 is not connected to the hub 1. This damper is tuned by means of spoke springs 4 between the ring 3 and hub 1.
A tenth embodiment of the invention is illustrated in Figure 11. This embodiment is similar to that shown in Figure 3 but including a ring 76 fixedly attached to outer wall 37 of housing 36 and rotatable therewith. Spoke springs 78 (only one of which is shown) are fixedly attached at one end to ring 76 and at the other end to inertia disc 74, the inertia disc 74, spoke springs 78, the ring 76 being integral in the present embodiment. A gap 80 for viscous fluid is provided between disc 72 and inner wall 38.
In a further embodimen'c of the invention, the ring 40, in the embodiment shown in Figure 6~ is integral with the inner wall 38.
In another embodiment of the invention7 ring 3~ in the embodiment shown in Figur~ 5, is integral with the inner wall 6 of the housing 5 shown in Figure 1.
In another embodiment of the invention~ the bearing 33, shown in Figure 1, is provided on inertia disc 12 instead of on housing 3O
In another embodiment of the invention, the embodiment of the invention illustrated in Figure 3 could have spoke springs similar to spokes springs 4 between hub 1 and ring 3 as shown in Figure lo 6~
While each of the above embodiment~ includes only one inertia disc, alternative embodiments of the invention include more than one inertia disc in one damperO
Claims (7)
1. A compound tuned, viscous, torsional vibra-tion damper comprising:
a central hub for connecting the damper to a rotatable shaft, a hollow cylindrical housing with an annular inner wall surrounding the hub, an annular outer wall and disc-shaped side walls;
an annular-shaped inertia disc within the housing;
a bearing between the inner wall of the housing and the inertia disc for rotation of the inertia disc within the housing;
viscous damping fluid between the disc and the housing;
disc tuning means resiliently connecting the disc and the housing; and housing tuning means resiliently connecting the hub and housing.
a central hub for connecting the damper to a rotatable shaft, a hollow cylindrical housing with an annular inner wall surrounding the hub, an annular outer wall and disc-shaped side walls;
an annular-shaped inertia disc within the housing;
a bearing between the inner wall of the housing and the inertia disc for rotation of the inertia disc within the housing;
viscous damping fluid between the disc and the housing;
disc tuning means resiliently connecting the disc and the housing; and housing tuning means resiliently connecting the hub and housing.
2. A damper as claimed in claim 1 comprising a ring surrounding the hub and radially spaced-apart therefrom the housing being mounted on the ring and the housing tuning means connecting the hub and the ring.
3. A damper as claimed in claim 2, the disc tuning means comprising a plurality of coil springs.
4. A damper as claimed in claim 2, the housing tuning means comprising spoke springs fixedly connected to the hub at a first end, extending radially outwards between the hub and the ring and fixedly connected to the ring at a second end.
5. A damper as claimed in claim 4, the inertia disc having two slots extending outwardly from the inner wall of the housing, the damper comprising two abutment plates connected to the inner wall of the housing and extending radially outwards into the slots, the disc tuning means comprising four said coil springs, each coil spring extending between the disc and one of the abutment plates perpendicularly to the one abutment plate.
6. A damper as claimed in claim 5, the hub, the ring and the spoke springs being integral.
7. A damper as claimed in claim 5, comprising two diametrically opposing said slots on the disc, each of the abutment plates having two sides and extending into the center of one said slot, each of the coil springs being compressed between one side of one said abutment plate and the disc.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA323,267A CA1101695A (en) | 1979-03-09 | 1979-03-09 | Torsional vibration damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA323,267A CA1101695A (en) | 1979-03-09 | 1979-03-09 | Torsional vibration damper |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1101695A true CA1101695A (en) | 1981-05-26 |
Family
ID=4113724
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA323,267A Expired CA1101695A (en) | 1979-03-09 | 1979-03-09 | Torsional vibration damper |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1101695A (en) |
-
1979
- 1979-03-09 CA CA323,267A patent/CA1101695A/en not_active Expired
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |