CA1105742A - Series spring torsional vibration damper - Google Patents
Series spring torsional vibration damperInfo
- Publication number
- CA1105742A CA1105742A CA303,485A CA303485A CA1105742A CA 1105742 A CA1105742 A CA 1105742A CA 303485 A CA303485 A CA 303485A CA 1105742 A CA1105742 A CA 1105742A
- Authority
- CA
- Canada
- Prior art keywords
- vibration damper
- set forth
- damper assembly
- arms
- spacers
- 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
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
- F16F15/1232—Wound springs characterised by the spring mounting
- F16F15/1234—Additional guiding means for springs, e.g. for support along the body of springs that extend circumferentially over a significant length
-
- 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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
- F16H2045/0231—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers arranged in series
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Arrangement Of Transmissions (AREA)
Abstract
ABSTRACT
A torsional vibration damper assembly for use in a torsion coupling or clutch arrangement to provide a low spring rate, high deflection amplitude characteristic. The assembly includes an input means having driving members secured thereto, a hub assembly adapted to be operatively connected to an output means and including a housing containing hub barrels and drive plates secured thereto, a plurality of floating spacers, and a plurality of compression spring sets which are arranged in two groups operating in parallel with the spring sets of each group operating in series.
A torsional vibration damper assembly for use in a torsion coupling or clutch arrangement to provide a low spring rate, high deflection amplitude characteristic. The assembly includes an input means having driving members secured thereto, a hub assembly adapted to be operatively connected to an output means and including a housing containing hub barrels and drive plates secured thereto, a plurality of floating spacers, and a plurality of compression spring sets which are arranged in two groups operating in parallel with the spring sets of each group operating in series.
Description
077~28-BB ~1~5 ~42 The present invention rela~es tO a torsional vibra~ion damper assembly for use in a torsion coupling between a pair of axially aligned shafts, in a clutch for a manual trans-mission or in a lock-up clutch for a torque converter of an automatic transmission.
Vibration in a vehicle drive train has been a long-standing problem due to the sudden shock of engagement o the clutch disc in a vehicle clutch for a ~anual trans-mission and to the torque fluctuations occurring in an internal combustion engine. The use of a vibration damper has been long accept~d as a way of counteracting these tor-sional vi.brations rom the vehicle engine which would other-wise cause undesirable characteristics, e.g., impact loads, pulsations, noises, etc., in the transmission and driveline during operation o~ the vehicle.
In an automatic transmission having a constant slipping device, torsional vibrations are not a problem unless a lock-up clutch is utilized to provide a direct drive in order to enhance fuel economy. Without the lock-up clut h, the vibrations axe absorbed hydraulically; but when a torque eonverter is locked in direct drive, a vibration d~mper is required to eIiminate any dis~urbance resulting from torsional vibration. Likewise, the vibra~ion damper`
assembly is convenient or use as a fle~ible co~pling between an input shaft and output shaft where flexibility is required. The present inven~ion provides a novel vibration damper assembly that will be use~ul in all of these various -~
applications.
The present invention comprehends a novel vibration damper assembly which provides a relatively low rate, high amplitude deflection between the torque input and output elements.
According to one aspec-t of the present invention, there is provided a vibration damper assembly for trans-mitting torque between driving and driven elements, the assembly including an input member operatively associated with torque input means, and a hub assembly operatively connected to torque output means. A housing encompasses the hub assembly and floating spacers are provided within the housing. Resilient means are provided in the housing between the spacers, and the hub assembly includes a pair of oppositely disposed arms adapted to engage the resilient means. A pair of drive members is secured to the input member and extend into the housing into the path of and engaging the resilient means.
The assembly of a specific embodiment o~ the invention includes mounting means operatively connected to a torque input, drive members on the mounting means, a hub barrel and drive plates connected together and operatively .
,, j , , cbr/cJ~; 2-~`
connected to the output, a plurality of floatiny spacers, and resilient spring means positioned in the path of the drive members, floating spacers and drive plates to provide a resilient connection between the mounting means and the hub.
A specific embodiment of the present invention also comprehends a novel vibration damper assembly providing an extended arc of deflection between the driving and driven members. The hub is secured to a dish-shaped cover plate which has a generally flat base and an annular depending flange or side. The interior surface of the flange provides a guiding surface for the floating spacers each of which contains a roller contacting the guiding surface. The resilient springs contact converging sides of the wedge-shaped spacers.
A specific embodiment of the present invention further comprehends a novel vibration damper assembly wherein the resilient springs are arranged into two groups acting in parallel, with each group comprising several spring sets of concentric springs acting in series.
Further objects of the present invention are to provide a construction of maximum simplicity, efficiency, economy ';
' -2a-cbr/~ J
and ease of assembly and operation, and such further objects, advantages and capabilities as will later more fully appear and are inherently possessed thereby.
In the accompanying drawings:
Figure 1 is a rear elevational view, partially in cross section, of ~he vibration damper assembly of the present invention.
Figure 2 is a vertical cross sectional view of the vibration damper assembly taken on th~ line 2-2 of Figure 1.
Figure 3 is a partial cross sectional view taken on the line 3-3 of Figure 1.
Figure 4 is a cross sectional view taken on the irregular line 4-4 of Figure 2.
Figure 5 is a cross sectional view taken on the line 5-5 of Figure 4.
Figure 6 is an exploded perspective view of the vibration damper without the springs and spacers.
Figure 7 is an enlarged exploded perspective view of a floating spacer.
Referring more particularly to the disclosure in the drawings wherein is shown an illustrative embodiment of the present in~ention, Figures 1 and 2 disclos~ a vibration damper assembly 10 for connection of driving and driven members (not shown) wherein the assembly can be utiliz d as a 1exible connection be~ween a pair of axially aligned shafts, as a lockup clutch in a torque converter for an automatic transmlssion, or as a clutch in a manual trans-mission. The present assembly includes a driving member 11, 077028-BB ~ 1~ 5 742 which m~y be a clutch friction plate or may be secured to a flywheel or driving flange of a shaft, having a central opening 12 defined by an annular flange 13.
Mounted on the member 11 by rivets 14 are a pair of oppositely disposed drive tangs 15; each tang having an arcuate base 16 with openings 17 for the rivets, an an-gularly offset portion 18 and a generally triangular end 19 projecting into a retaining cover plate 21. The cover plate 21 includes a generally flat base portion 22 having a central opening Z3 and a plurality of openings 24 surrounding open-ing 23, and a depending skirt or flange 25 joined to the flat portion 22 by a curved portion 26 and terminating in a radially extending rim 27. A pair of oppositely disposed elongated slots 28, 28 are o~med in the flange 25 to receive the drive tangs 15; each slot having a central enlarged portion 29 and a narrowed extension 30 at each end of portion 29.
Within the cover plat~ 21 are mounted a first an~ular barrel hub 31 having a central opening 32 Yplined at 33 and a plurality of circumferentially spaced openings 34 around the central opening, a second annular barrel hub 35 also ha~ing a central opening 36 splined at 37 and circumferen-tially spaced openings 38 therearound. A pair of substan-tially identical drive plates 39, 39' are located with one plate 39 located between the barrel hubs 31, 35 and the second plate 39' position~d behind the hub 35 away from the cover plate base portion 22. Each drive pla~e 39, 39' _~_ ~77028-BB
~ 7~ ~
includes an annular body 41, 41' having a central opening 42, 42', a plurality of circumferentially spaced openings 43, 43' therearound and a pair of oppositely disposed out-wardly extending arms 44, 44', each arm having outwardly diverging edges 45, 45'.
A plurality of rivets 46 extend through the aligned openings 24, 34, 43, 38 and 43' of the cover plate 21, barrel hub 31, drive plate 39, barrel hub 35 and dri~e plate 39', respectively, to retain the parts together and form a unitary cover plate assembly. An annular cpace 47 is ormed between ~he cover plate flange 25 and the barrel hubs 31, 35 to receive a plurality of damper spring spacers 48, each spacer being in the form of a generally triangular block having flat sides 49 converging away from a generally flat base 50, an inclined end 51 and a curved end surface 52 generally conformable with the curved portion 26 of the cover plate. A passage 53 extends through the block ad-jacent the base 50 and has a counterbored portion 54 opening into the end surface 51 and intersecting thP flat base 50 to provide an elongated slot 55, as se~n in Figure 7. A shaft 56 has an enlarged head 57 at one end and a reduced shank 5 at the opposite end adapted to be received in the passage 53. A bushing 5g is rotatably mounted on the sha~t 56 and is receiv~d in the counterbored portion 54 to partially extend through the slot 55.
Aq shown in Figures 1, 3 and 4, the bushing 59 extends beyond the base 50 of a spacer 48 to engage the interior _5_ ~574;~
surface 60 of the cover plate flange 25 and provide a roller bearing action for the spacer. As seen in Figure 1, two spacers 48, 48 are positioned between the opposite arms 44, 44' of the drive plates 39, 39' to form therewith three spring pockets to receive damper springs 61, 62, 61', 62', and 61", 62". The springs are concentric with a pair of springs in each pocket. All three pairs of springs seen in Figure l may be of the same rates or the rates of the pairs may vary depending on ~he desired characteristics of the damper. Although two springs are shown for each pocket, a single spring or three or more concentric springs may be utilized depending on the desired conditions of use.
Figure 1 discloses three pairs o~ springs on one side of the centerline d~noted as line 2-2 to form one group of springs, with a second gro~p of springs being loca~ed on the opposite side of the centerline 2-2. The two groups of springs act in parallel and have additive loads, with the sets of springs in each group acting in series with the loads not being additive. The rates of the various pairs o~
springs may either be equal or have varying rates, with springs 61, 62 having the lowes~ rate of compression, the 5prings 61', 62' having an intermediate ra~e, and the springs 61", 62" located between the spacers 48, 48 having the highest spring rate. Iden~ical springs are provided in the diametrically opposite pockets as shown in Figure 4.
Considering operation o~ the vibration damper assembly 10, the two drive tangs 15 transmi~ torque from the driving member 11 through the springs 61, 62, 61', 62' and 61", 62"
-6~
077028-B~
7~2 and spacers 48 to the drive plates 39, 39' and barrel hubs 31, 35; the splines 33 and 37 adapted to rereive the splined end of a driven shaft (not shown) leading to a transmission or other device. As shown in Figure 1, as the driving member 11 rotates in either direction, the tangs 15 move in the slots 28 to compress the lowest rate springs 61, 62 between the tangs 15 and the first spacers 48. The springs 61', 62' and 61", 62" will also be compressed but to a lesser degree as the spacers 48 move on the bushings 59 relativ~ to the cover plate 21. As the torque is increased, the springs 61, 62 will be compressed to their solid height, with the springs 61', 62' being compressed more and springs 61", 62" yieldably transmitting torque. If both springs 61, 62 and 61', 62' are compressed to their solid heights, springs 61't, 6~" having the highest spring rate will still yieldably transmit torque. If the spring rates of the spring sets are identical, the application of input torque will cau~e compression of all springs 61, 62, 61', 62' and 61" and 62" equally.
; This vibration damper assembly will provide a greater deflection angle than prior conventional d~mper assemblies.
The angled sides 49, 49 of the spacers 48 react to the spring orce causing the spacers to be urged outwardly and provide frictional contact between the bushings and the interior surface 60 of the cover plate. Although described with one arrangement of spring rates for each group, the deflection characteristic for the damper may be varied depending on the choice of springs. The damper assembly is ~7-~ 7~ 2 suitable for use in a variety of automotive or industrial torsional vibration damper applications requiring a low spring rate and high deflection amplitude characteristic.
Vibration in a vehicle drive train has been a long-standing problem due to the sudden shock of engagement o the clutch disc in a vehicle clutch for a ~anual trans-mission and to the torque fluctuations occurring in an internal combustion engine. The use of a vibration damper has been long accept~d as a way of counteracting these tor-sional vi.brations rom the vehicle engine which would other-wise cause undesirable characteristics, e.g., impact loads, pulsations, noises, etc., in the transmission and driveline during operation o~ the vehicle.
In an automatic transmission having a constant slipping device, torsional vibrations are not a problem unless a lock-up clutch is utilized to provide a direct drive in order to enhance fuel economy. Without the lock-up clut h, the vibrations axe absorbed hydraulically; but when a torque eonverter is locked in direct drive, a vibration d~mper is required to eIiminate any dis~urbance resulting from torsional vibration. Likewise, the vibra~ion damper`
assembly is convenient or use as a fle~ible co~pling between an input shaft and output shaft where flexibility is required. The present inven~ion provides a novel vibration damper assembly that will be use~ul in all of these various -~
applications.
The present invention comprehends a novel vibration damper assembly which provides a relatively low rate, high amplitude deflection between the torque input and output elements.
According to one aspec-t of the present invention, there is provided a vibration damper assembly for trans-mitting torque between driving and driven elements, the assembly including an input member operatively associated with torque input means, and a hub assembly operatively connected to torque output means. A housing encompasses the hub assembly and floating spacers are provided within the housing. Resilient means are provided in the housing between the spacers, and the hub assembly includes a pair of oppositely disposed arms adapted to engage the resilient means. A pair of drive members is secured to the input member and extend into the housing into the path of and engaging the resilient means.
The assembly of a specific embodiment o~ the invention includes mounting means operatively connected to a torque input, drive members on the mounting means, a hub barrel and drive plates connected together and operatively .
,, j , , cbr/cJ~; 2-~`
connected to the output, a plurality of floatiny spacers, and resilient spring means positioned in the path of the drive members, floating spacers and drive plates to provide a resilient connection between the mounting means and the hub.
A specific embodiment of the present invention also comprehends a novel vibration damper assembly providing an extended arc of deflection between the driving and driven members. The hub is secured to a dish-shaped cover plate which has a generally flat base and an annular depending flange or side. The interior surface of the flange provides a guiding surface for the floating spacers each of which contains a roller contacting the guiding surface. The resilient springs contact converging sides of the wedge-shaped spacers.
A specific embodiment of the present invention further comprehends a novel vibration damper assembly wherein the resilient springs are arranged into two groups acting in parallel, with each group comprising several spring sets of concentric springs acting in series.
Further objects of the present invention are to provide a construction of maximum simplicity, efficiency, economy ';
' -2a-cbr/~ J
and ease of assembly and operation, and such further objects, advantages and capabilities as will later more fully appear and are inherently possessed thereby.
In the accompanying drawings:
Figure 1 is a rear elevational view, partially in cross section, of ~he vibration damper assembly of the present invention.
Figure 2 is a vertical cross sectional view of the vibration damper assembly taken on th~ line 2-2 of Figure 1.
Figure 3 is a partial cross sectional view taken on the line 3-3 of Figure 1.
Figure 4 is a cross sectional view taken on the irregular line 4-4 of Figure 2.
Figure 5 is a cross sectional view taken on the line 5-5 of Figure 4.
Figure 6 is an exploded perspective view of the vibration damper without the springs and spacers.
Figure 7 is an enlarged exploded perspective view of a floating spacer.
Referring more particularly to the disclosure in the drawings wherein is shown an illustrative embodiment of the present in~ention, Figures 1 and 2 disclos~ a vibration damper assembly 10 for connection of driving and driven members (not shown) wherein the assembly can be utiliz d as a 1exible connection be~ween a pair of axially aligned shafts, as a lockup clutch in a torque converter for an automatic transmlssion, or as a clutch in a manual trans-mission. The present assembly includes a driving member 11, 077028-BB ~ 1~ 5 742 which m~y be a clutch friction plate or may be secured to a flywheel or driving flange of a shaft, having a central opening 12 defined by an annular flange 13.
Mounted on the member 11 by rivets 14 are a pair of oppositely disposed drive tangs 15; each tang having an arcuate base 16 with openings 17 for the rivets, an an-gularly offset portion 18 and a generally triangular end 19 projecting into a retaining cover plate 21. The cover plate 21 includes a generally flat base portion 22 having a central opening Z3 and a plurality of openings 24 surrounding open-ing 23, and a depending skirt or flange 25 joined to the flat portion 22 by a curved portion 26 and terminating in a radially extending rim 27. A pair of oppositely disposed elongated slots 28, 28 are o~med in the flange 25 to receive the drive tangs 15; each slot having a central enlarged portion 29 and a narrowed extension 30 at each end of portion 29.
Within the cover plat~ 21 are mounted a first an~ular barrel hub 31 having a central opening 32 Yplined at 33 and a plurality of circumferentially spaced openings 34 around the central opening, a second annular barrel hub 35 also ha~ing a central opening 36 splined at 37 and circumferen-tially spaced openings 38 therearound. A pair of substan-tially identical drive plates 39, 39' are located with one plate 39 located between the barrel hubs 31, 35 and the second plate 39' position~d behind the hub 35 away from the cover plate base portion 22. Each drive pla~e 39, 39' _~_ ~77028-BB
~ 7~ ~
includes an annular body 41, 41' having a central opening 42, 42', a plurality of circumferentially spaced openings 43, 43' therearound and a pair of oppositely disposed out-wardly extending arms 44, 44', each arm having outwardly diverging edges 45, 45'.
A plurality of rivets 46 extend through the aligned openings 24, 34, 43, 38 and 43' of the cover plate 21, barrel hub 31, drive plate 39, barrel hub 35 and dri~e plate 39', respectively, to retain the parts together and form a unitary cover plate assembly. An annular cpace 47 is ormed between ~he cover plate flange 25 and the barrel hubs 31, 35 to receive a plurality of damper spring spacers 48, each spacer being in the form of a generally triangular block having flat sides 49 converging away from a generally flat base 50, an inclined end 51 and a curved end surface 52 generally conformable with the curved portion 26 of the cover plate. A passage 53 extends through the block ad-jacent the base 50 and has a counterbored portion 54 opening into the end surface 51 and intersecting thP flat base 50 to provide an elongated slot 55, as se~n in Figure 7. A shaft 56 has an enlarged head 57 at one end and a reduced shank 5 at the opposite end adapted to be received in the passage 53. A bushing 5g is rotatably mounted on the sha~t 56 and is receiv~d in the counterbored portion 54 to partially extend through the slot 55.
Aq shown in Figures 1, 3 and 4, the bushing 59 extends beyond the base 50 of a spacer 48 to engage the interior _5_ ~574;~
surface 60 of the cover plate flange 25 and provide a roller bearing action for the spacer. As seen in Figure 1, two spacers 48, 48 are positioned between the opposite arms 44, 44' of the drive plates 39, 39' to form therewith three spring pockets to receive damper springs 61, 62, 61', 62', and 61", 62". The springs are concentric with a pair of springs in each pocket. All three pairs of springs seen in Figure l may be of the same rates or the rates of the pairs may vary depending on ~he desired characteristics of the damper. Although two springs are shown for each pocket, a single spring or three or more concentric springs may be utilized depending on the desired conditions of use.
Figure 1 discloses three pairs o~ springs on one side of the centerline d~noted as line 2-2 to form one group of springs, with a second gro~p of springs being loca~ed on the opposite side of the centerline 2-2. The two groups of springs act in parallel and have additive loads, with the sets of springs in each group acting in series with the loads not being additive. The rates of the various pairs o~
springs may either be equal or have varying rates, with springs 61, 62 having the lowes~ rate of compression, the 5prings 61', 62' having an intermediate ra~e, and the springs 61", 62" located between the spacers 48, 48 having the highest spring rate. Iden~ical springs are provided in the diametrically opposite pockets as shown in Figure 4.
Considering operation o~ the vibration damper assembly 10, the two drive tangs 15 transmi~ torque from the driving member 11 through the springs 61, 62, 61', 62' and 61", 62"
-6~
077028-B~
7~2 and spacers 48 to the drive plates 39, 39' and barrel hubs 31, 35; the splines 33 and 37 adapted to rereive the splined end of a driven shaft (not shown) leading to a transmission or other device. As shown in Figure 1, as the driving member 11 rotates in either direction, the tangs 15 move in the slots 28 to compress the lowest rate springs 61, 62 between the tangs 15 and the first spacers 48. The springs 61', 62' and 61", 62" will also be compressed but to a lesser degree as the spacers 48 move on the bushings 59 relativ~ to the cover plate 21. As the torque is increased, the springs 61, 62 will be compressed to their solid height, with the springs 61', 62' being compressed more and springs 61", 62" yieldably transmitting torque. If both springs 61, 62 and 61', 62' are compressed to their solid heights, springs 61't, 6~" having the highest spring rate will still yieldably transmit torque. If the spring rates of the spring sets are identical, the application of input torque will cau~e compression of all springs 61, 62, 61', 62' and 61" and 62" equally.
; This vibration damper assembly will provide a greater deflection angle than prior conventional d~mper assemblies.
The angled sides 49, 49 of the spacers 48 react to the spring orce causing the spacers to be urged outwardly and provide frictional contact between the bushings and the interior surface 60 of the cover plate. Although described with one arrangement of spring rates for each group, the deflection characteristic for the damper may be varied depending on the choice of springs. The damper assembly is ~7-~ 7~ 2 suitable for use in a variety of automotive or industrial torsional vibration damper applications requiring a low spring rate and high deflection amplitude characteristic.
Claims (20)
OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A vibration damper assembly to transmit torque between driving and driven elements, comprising an input member operatively associated with torque input means, a hub assembly operatively connected to torque output means, a housing encompassing said hub assembly, floating spacers within said housing, resilient means in said housing between said spacers, said hub assembly including a pair of oppositely disposed arms adapted to engage said resilient means, and a pair of drive members secured to said input member and extending into said housing into the path of and engaging said resilient means.
2. A vibration damper assembly as set forth in Claim 1 , in which said floating spacers comprise generally wedge-shaped blocks with inwardly converging sides engaged by said resilient means.
3. A vibration damper assembly as set forth in Claim 1, in which said housing comprises a cover plate with a generally flat base portion and a depending skirt having a pair of elongated slots in the outer radial periphery there-of, said driving members extending through said slots into the cover plate.
4. A vibration damper assembly as set forth in Claim 3, wherein said elongated slots are oppositely disposed in said cover plate, each slot having an enlarged central portion with elongated narrow end portions.
5. A vibration damper assembly as set forth in Claim 3, in which said hub assembly includes at least one barrel hub and at least one drive plate secured in the cover plate, said barrel hub being splined to be operatively connected to said torque output means.
6. A vibration damper assembly as set forth in Claim 5, in which said drive plate includes an annular body and a pair of oppositely extending arms, said arms extending into and secured in the elongated slots.
7. vibration damper assembly as set forth in Claim 6, in which each arm has outwardly diverging edges, and each drive member has outwardly diverging edges generally aligned with the edges on an arm, said drive members and drive plate arms being aligned when there is no torque input.
8. A vibration damper assembly as set forth in Claim 3, in which said spacers comprise generally wedge-shaped blocks with inwardly converging sides, and roller means in the base of each block adapted to engage the cover plate to allow circumferential movement of said wedges.
9. A vibration damper assembly as set forth in Claim 8, in which said roller means includes a shaft mounted in said block, and a bushing mounted on the shaft and partially exposed in the base of the spacer to engage said cover plate.
10. A vibration damper assembly as set forth in Claim 6, in which said resilient means includes a plurality of sets of two or more concentric compression springs, said springs engaging the arms of said drive plate and said spacers, and said drive members extending through said elongated slots and adapted to engage one end of a spring set upon the exertion of torque by said input member.
11. A vibration damper assembly as set forth in Claim 10, in which said springs are arranged in two groups acting in parallel, each group including three spring sets and two spacers interposed around the hub and between the oppositely extending drive plate arms.
12. A vibration damper assembly as set forth in Claim 10, in which each spacer has inwardly converging sides engaged by the ends of adjacent spring sets, and said arms having inwardly converging edges engaged by said spring sets, said spring sets cooperating with said spacer sides to urge the spacers outwardly toward said cover plate skirt.
13. A vibration damper assembly as set forth in Claim 12, including roller means in the base surface of each spacer adapted to engage said cover plate skirt.
14. A vibration damper assembly as set forth in Claim 1, in which said housing includes a cover plate having a flat base portion and a depending skirt, said hub assembly including a pair of drive plates in said cover plate, a first hub barrel separating said drive plates, a second barrel hub separating said drive plates from said flat base portion, securing means retaining the drive plates and barrel hubs onto said cover plate, said cover plate, drive plates and barrel hubs having aligned central openings to receive the torque output means, said drive plates each having an annular body and a pair of oppositely disposed outwardly extending arms, said annular bodies and said barrel hubs being radially spaced from said skirt to provide an annular chamber divided by said arms into two sub-stantially semi-circular chambers, said skirt having a pair of oppositely disposed elongated narrow slots, each slot having an enlarged portion receiving the ends of the arms therein, and said driving members are secured to said input member and extend into the slots between said arms.
15. A vibration damper assembly as set forth in Claim 14, in which a pair of spacers are located in each semi-circular chamber, and said resilient means includes three sets of springs in each semi-circular chamber extending between said drive plate arms and said spacers, said three sets of springs forming a group.
16. A vibration damper assembly as set forth in Claim 15, in which said spring groups in the semi-circular chambers act in parallel, with the springs in each group acting in series.
17. A vibration damper assembly as set forth in Claim 15, in which said driving plate arms have outwardly diverging edges, and said spacers have outwardly diverging side walls terminating in a generally flat base portion, the ends of the spring sets engaging the edges of the arms and the diverging sides of said spacers to urge said spacers outwardly toward the cover plate skirt.
18. A vibration damper assembly as set forth in Claim 17, in which each spacer has a roller partially exposed in the base portion and adapted to engage the skirt.
19. A vibration damper assembly as set forth in Claim 18, in which said roller includes a shaft mounted in said spacer and a bushing journalled on said shaft, said spacer having a recess receiving said shaft and bushing and partially opening into said base portion to expose a portion of said bushing.
20. A vibration damper assembly as set forth in Claim 17, in which said drive members have outwardly diverging edges adapted to be generally aligned with the edges of the driving plate arms when there is no torque input.
21, A vibration damper assembly as set forth in
20. A vibration damper assembly as set forth in Claim 17, in which said drive members have outwardly diverging edges adapted to be generally aligned with the edges of the driving plate arms when there is no torque input.
21, A vibration damper assembly as set forth in
Claim 20, in which an edge of each drive member engages the end of a spring set and urges it away from the adjacent drive plate arm when input torque is applied by said input member.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US80199077A | 1977-05-31 | 1977-05-31 | |
| US801,990 | 1977-05-31 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1105742A true CA1105742A (en) | 1981-07-28 |
Family
ID=25182552
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA303,485A Expired CA1105742A (en) | 1977-05-31 | 1978-05-16 | Series spring torsional vibration damper |
Country Status (11)
| Country | Link |
|---|---|
| JP (1) | JPS6024336B2 (en) |
| AR (1) | AR222151A1 (en) |
| AU (1) | AU522690B2 (en) |
| BR (1) | BR7803497A (en) |
| CA (1) | CA1105742A (en) |
| DE (1) | DE2823894C2 (en) |
| ES (1) | ES470154A1 (en) |
| FR (1) | FR2393200A1 (en) |
| GB (1) | GB1594788A (en) |
| IT (1) | IT1094940B (en) |
| SE (1) | SE435088B (en) |
Families Citing this family (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4304107A (en) * | 1977-05-31 | 1981-12-08 | Borg-Warner Corporation | Series spring torsional vibration damper |
| US4302951A (en) * | 1979-12-26 | 1981-12-01 | Borg-Warner Corporation | Torsional vibration damper |
| CA1157398A (en) * | 1979-12-26 | 1983-11-22 | Paul E. Lamarche | Two-stage torsional vibration damper |
| US4413711A (en) * | 1981-03-30 | 1983-11-08 | Borg-Warner Corporation | Extended travel damper in a lock-up clutch for a torque converter |
| US4790792A (en) * | 1983-12-22 | 1988-12-13 | Eaton Corporation | Torsion damping assembly |
| US4555009A (en) * | 1983-12-22 | 1985-11-26 | Borg-Warner Corporation | Minimum complexity vibration damper |
| JPS60136623A (en) * | 1983-12-22 | 1985-07-20 | Daikin Mfg Co Ltd | Widely swinging square type damper disk |
| JPS60112727U (en) * | 1984-01-05 | 1985-07-30 | 株式会社 大金製作所 | damper disc |
| US4585427A (en) * | 1985-03-26 | 1986-04-29 | Borg-Warner Automotive, Inc. | Long travel series damper for continuously variable transmission |
| DE3606707C2 (en) * | 1986-03-01 | 1999-07-01 | Luk Lamellen & Kupplungsbau | Motor vehicle with a torque converter between the internal combustion engine and the transmission |
| AU6923987A (en) * | 1986-03-18 | 1987-09-24 | Borg-Warner Automotive, Inc. | Long travel damper with dynamic spring dividers |
| FR2620501A1 (en) * | 1987-09-10 | 1989-03-17 | Valeo | TORSION DAMPER DEVICE |
| FR2620502B1 (en) * | 1987-09-10 | 1989-12-08 | Valeo | TORSION DAMPING DEVICE |
| FR2756031B1 (en) * | 1996-11-21 | 1999-01-29 | Valeo | DOUBLE SHOCK ABSORBER FOR MOTOR VEHICLE |
| DE19825249B4 (en) * | 1998-06-05 | 2007-05-03 | Zf Sachs Ag | torsional vibration damper |
| DE102004024739A1 (en) * | 2004-05-19 | 2005-12-15 | Zf Friedrichshafen Ag | supporting |
| US8376653B2 (en) † | 2007-04-23 | 2013-02-19 | Wirtgen Gmbh | Self-propelled road construction machine |
| JP4941191B2 (en) * | 2007-09-13 | 2012-05-30 | アイシン・エィ・ダブリュ株式会社 | Damper device |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB166939A (en) * | 1920-04-16 | 1921-07-18 | B S A Cycles Ltd | Improvements in spring drives for motor cycles and the like |
| DE307086C (en) * | 1920-09-04 | |||
| DE429536C (en) * | 1923-04-12 | 1926-05-29 | Rolls Royce | Friction-acting damping device for clutches with resilient intermediate members, especially for motor vehicles |
| US1861251A (en) * | 1928-05-14 | 1932-05-31 | Ernest E Wemp | Clutch |
| US2149887A (en) * | 1937-04-15 | 1939-03-07 | Hickman Pneumatic Seat Co Inc | Device for providing torsional resistance |
| US2284278A (en) * | 1938-02-07 | 1942-05-26 | George I Goodwin | Clutch plate |
| US2574573A (en) * | 1949-12-09 | 1951-11-13 | Kaiser Frazer Corp | Vibration dampener |
| DE838973C (en) * | 1950-03-31 | 1952-05-15 | Kloeckner Humboldt Deutz Ag | Friction clutch |
| IL28649A (en) * | 1966-09-29 | 1972-04-27 | Prephar | Glycopeptides and their preparation from animal organs |
| DE2315946C3 (en) * | 1973-03-30 | 1984-03-22 | LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl | Clutch disc |
| FR2361577A1 (en) * | 1976-08-12 | 1978-03-10 | Ferodo Sa | Friction clutch for automobile - has friction, washer, spring washer and friction pads to damp out torsional oscillations by hysteresis |
-
1978
- 1978-05-16 CA CA303,485A patent/CA1105742A/en not_active Expired
- 1978-05-19 GB GB20874/78A patent/GB1594788A/en not_active Expired
- 1978-05-24 ES ES470154A patent/ES470154A1/en not_active Expired
- 1978-05-24 AU AU36409/78A patent/AU522690B2/en not_active Expired
- 1978-05-26 SE SE7806096A patent/SE435088B/en not_active IP Right Cessation
- 1978-05-30 FR FR7816118A patent/FR2393200A1/en active Granted
- 1978-05-30 JP JP53064858A patent/JPS6024336B2/en not_active Expired
- 1978-05-30 IT IT23998/78A patent/IT1094940B/en active
- 1978-05-31 BR BR7803497A patent/BR7803497A/en unknown
- 1978-05-31 DE DE2823894A patent/DE2823894C2/en not_active Expired
- 1978-05-31 AR AR272416A patent/AR222151A1/en active
Also Published As
| Publication number | Publication date |
|---|---|
| FR2393200A1 (en) | 1978-12-29 |
| AU3640978A (en) | 1979-11-29 |
| AR222151A1 (en) | 1981-04-30 |
| DE2823894A1 (en) | 1978-12-14 |
| FR2393200B1 (en) | 1984-06-08 |
| JPS6024336B2 (en) | 1985-06-12 |
| AU522690B2 (en) | 1982-06-24 |
| IT1094940B (en) | 1985-08-10 |
| SE7806096L (en) | 1978-12-01 |
| SE435088B (en) | 1984-09-03 |
| DE2823894C2 (en) | 1987-05-27 |
| ES470154A1 (en) | 1979-02-01 |
| GB1594788A (en) | 1981-08-05 |
| BR7803497A (en) | 1978-12-26 |
| IT7823998A0 (en) | 1978-05-30 |
| JPS53148670A (en) | 1978-12-25 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4304107A (en) | Series spring torsional vibration damper | |
| CA1105742A (en) | Series spring torsional vibration damper | |
| US4530673A (en) | Series spring vibration dampers | |
| CA1157398A (en) | Two-stage torsional vibration damper | |
| US4279132A (en) | Vibration damper assembly | |
| CA1040970A (en) | Compact vibration damper | |
| US4347717A (en) | Two-stage torsional vibration damper | |
| CA1111286A (en) | High deflection amplitude torsional vibration damper | |
| US4360352A (en) | Extended travel vibration damper assembly | |
| CA1094474A (en) | Torsional vibration damper | |
| US4188806A (en) | Torsional vibration damper assembly | |
| EP0240166B1 (en) | Long travel damper with low lag dynamic spring retainers | |
| CA1264450A (en) | Long travel series damper for continuously variable transmission | |
| CA1141567A (en) | Torsional vibration damper | |
| EP0061827B1 (en) | Extended travel damper in a lock-up clutch for a torque converter | |
| US4471863A (en) | Multi-stage torsional damping device | |
| US4252227A (en) | Torsional vibration damper and clutch assembly | |
| EP0147136B1 (en) | Minimum complexity vibration damper | |
| US4257510A (en) | Non-linear spring rate clutch damper | |
| GB2027847A (en) | Extended travel vibration damper assembly | |
| US5401213A (en) | Clutch and damper assembly | |
| US4679678A (en) | Minimum complexity vibration damper | |
| EP0238231A2 (en) | Long travel damper with dynamic spring dividers | |
| US9447857B2 (en) | Torque converter assembly for a vehicle | |
| EP0085242A2 (en) | Long travel damper with friction lag device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |