WO2011160208A1 - Isolation pulley with overrunning and vibration damping capabilities - Google Patents
Isolation pulley with overrunning and vibration damping capabilities Download PDFInfo
- Publication number
- WO2011160208A1 WO2011160208A1 PCT/CA2011/000726 CA2011000726W WO2011160208A1 WO 2011160208 A1 WO2011160208 A1 WO 2011160208A1 CA 2011000726 W CA2011000726 W CA 2011000726W WO 2011160208 A1 WO2011160208 A1 WO 2011160208A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- decoupler
- spring
- input
- input hub
- Prior art date
Links
Classifications
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- 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
- F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
- F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
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- 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
- F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
- F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
- F02B67/06—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus driven by means of chains, belts, or like endless members
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- 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
- F16D13/00—Friction clutches
- F16D13/12—Friction clutches with an expansible band or coil co-operating with the inner surface of a drum or the like
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- 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
- F16D13/00—Friction clutches
- F16D13/76—Friction clutches specially adapted to incorporate with other transmission parts, i.e. at least one of the clutch parts also having another function, e.g. being the disc of a pulley
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- 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
- F16D41/00—Freewheels or freewheel clutches
- F16D41/20—Freewheels or freewheel clutches with expandable or contractable clamping ring or band
- F16D41/206—Freewheels or freewheel clutches with expandable or contractable clamping ring or band having axially adjacent coils, e.g. helical wrap-springs
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- 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
- F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
- F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
- F16D7/022—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with a helical band or equivalent member co-operating with a cylindrical torque limiting coupling surface
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- 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
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- 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
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- 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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49826—Assembling or joining
Definitions
- the present disclosure generally relates to an isolation pulley with over-running and vibration damping capabilities.
- Over-running decouplers are disclosed in U.S. Patent Application Publication Nos. 2010/0140044 and 2007/0037644. While such over-running decouplers are well suited for their intended purposes, there remains a need in the art for over-running decouplers that provide for torsional isolation.
- the present teachings provide a decoupler that includes an input hub, an output member and a clutch and isolation system having a one-way clutch and a torsional isolator.
- the one-way clutch has a clutch input structure, a clutch spring, a carrier, and a clutch output structure.
- the clutch input structure is fixedly coupled to the input hub for rotation therewith.
- the clutch spring is formed of wire and has a plurality of coils and a first end that is mounted to the carrier.
- the carrier is non-rotatably mounted to the input hub and orients an axial end face of the wire that forms the first end of the clutch spring against the clutch input structure.
- the clutch output structure has a clutch surface.
- the coils of the clutch spring are configured to expand against the clutch surface to transmit rotary power from the input hub to the clutch output structure in a first rotational direction.
- the coils of the clutch spring are configured to contract to permit the clutch output structure to overrun the input hub in the first rotational direction.
- the torsional isolator includes an input driver, an output driver and at least one spring that is configured to transmit torque in the first rotational direction between the input driver and the output driver.
- the input driver is coupled to the clutch output structure for rotation therewith.
- the output member is coupled to the output driver for rotation therewith.
- the at least one spring of the torsional isolator is disposed radially outwardly of the clutch spring.
- the teachings of the present disclosure provide a method for forming a decoupler.
- the method can include: mounting a torsional isolating spring concentrically about a clutch spring of a one-way clutch, the one-way clutch being drivingiy coupled to an input hub and configured to transmit rotary power between the input hub and the torsional isolating spring in a predetermined rotational direction; and balancing the decoupler to a predetermined rotational imbalance such that the decoupler is rotationally imbalanced when no torsional load is carried by the decoupler and the rotational imbalance of the decoupler decreases as a torsional load carried by the decoupler increases to a predetermined torsional load.
- the teachings of the present disclosure provide a decoupler having an input hub, an output member, a one-way clutch, and at least one isolation spring. Rotary power is transmitted in a predetermined rotational direction from the input hub, through the one-way clutch, through the isolation spring and to the output member.
- Construction of a decoupler in this manner can have several advantages, depending on the final configuration of the decoupler. For example, it may be possible to reduce the overall size of the one-way clutch relative to the prior art so that the one-way clutch is less costly. As another example, it may be possible to integrate a relatively larger spring into the decoupler, which can have cost advantages (as compared to a decoupler employing multiple springs) and/or provide a different spring rate that may not be easily attainable by other spring configurations. Other advantages not expressed herein may also be obtained.
- Figure 1 is rear perspective view of an exemplary decoupler constructed in accordance with the teachings of the present disclosure
- Figure 2 is an exploded perspective view of the decoupler of Figure 1 ;
- Figure 3 is a longitudinal section view of the decoupler of Figure 1 ;
- Figure 4 is a rear view of a portion of the decoupler of Figure 1 , illustrating a carrier, a clutch spring and a clutch input structure coupled to an input hub;
- Figure 5 is a perspective view of a portion of the decoupler of Figure 1 , illustrating a second end of the clutch spring mounted to a spring support;
- a decoupler constructed in accordance with the teachings of the present disclosure is generally indicated by reference numeral 10.
- the decoupler 10 can comprise an input member 12, a clutch and isolation system 14, an output member 16 and a torsional vibration damper 16.
- the fit between a bore 38 in the hub member 30 and a guide portion 40 of the driving shaft DS is configured to position the centerline relative to the rotational axis to a desired degree.
- the annular shoulder 32 can comprise a circumferentially-extending surface 44 and a radially-extending surface 46.
- the torsional vibration damper 18 which is not shown to scale, can comprise any type of torsional vibration damping means, including damping means that employ viscous shear force, tangential spring farce and/or friction force to dampen torsional vibrations.
- the torsional vibration damper 18 employs tangential spring force and comprises a damper input member 22, a resilient member Rl and an inertia member IM.
- the damper input member 22 can be a discrete component that can be coupled to the input hub 20 in any suitable manner.
- the resilient member Rl can comprise an elastomer that can be coupled to (e.g., bonded, frictionally engaged) to the damper input member 22 and the inertia member IM.
- the inertia member IM can be an annular structure that can be sized in a manner that is well known in the art to at lest partly cancel torsional vibration at a predetermined frequency.
- the clutch and isolation system 14 can comprise a one-way clutch 54 and a torsional isolator 56.
- the one-way clutch 54 comprises a clutch input structure 60, a carrier 62, a clutch spring 64, a clutch output member 66 and a spring support 68
- the torsional isolator 56 comprises an input driver 70, at least one isolating spring 72, and an output driver 74.
- the clutch input structure 60 can be coupled to the annular shoulder 32 such that the clutch input structure 60 will co-rotate with the input member 12.
- the clutch input structure 60 can have an abutting face ⁇ 0 that can extend from the radially- extending surface 46 of the annular shoulder 32.
- the clutch spring 64 can be formed of spring wire of an appropriate cross-sectional shape and can comprise a plurality of helical coils 86 that are disposed between a first end 88 and a second end 90.
- the first end 88 can extend radially inwardly from an adjacent one of the helical coils 86 and can comprise first and second linear segments 94 and 96, respectively, a first transition zone 98, and a second transition zone 100-
- the first linear segment 94 can extend radially inwardly from the adjacent one of the helical coils 86 at a first angle
- the second linear segment 96 can extend radially inwardly from the adjacent one of the helical coils ⁇ 6 at a second, larger angle.
- the first transition zone 98 can couple the first linear segment 94 to the adjacent one of the helical coils 86, while the second transition zone 100 can couple the second linear segment 96 to the first linear segment 94.
- the second end 90 can comprise a tang 104 that can extend parallel to a central axis about which the helical coils 86 are formed.
- the carrier 62 can be received around the annular shoulder 32 and can be configured to support the clutch spring 64 as rotary power is transmitted from the clutch input structure 60 to the clutch spring 64.
- the carrier 62 can be formed of a suitable material, such as steel or plastic, and can comprise a flange portion 110, a sleeve portion 112, a groove 114 and a carrier abutment wall 116.
- the flange portion 110 can be an annular structure having a front surface 118, which can abut the radially-extending surface 46 of the annular shoulder 32, and a rear surface 120 that can abut the adjacent one of the helical coils 86 of the clutch spring 64.
- portion of the rear surface 120 that abuts the clutch spring 64 is helically shaped to match the contour of the helical coils 86 of the clutch spring 64.
- the sleeve portion 112 can be an annular structure that can extend axially from the flange portion 110.
- the sleeve portion 112 can be sized to be received in the helical coils ⁇ 6 of the clutch spring 64 to support one or more of the helical coils 86 and/or to maintain the carrier 62 and the first end 88 of the clutch spring 64 about a common rotational axis.
- the groove 114 can be configured to receive the first end 88 of the clutch spring 64 and can extend through the circumference of the sleeve portion 12 and optionally through the carrier abutment wall 116.
- the carrier abutment wall 116 can abut the clutch input structure 60 and if the groove 14 extends through the carrier abutment wall 116, an axial end face 126 of the wire that forms the clutch spring 64 can also abut the abutting face 80 of the clutch input structure 60.
- the clutch input structure 60 is a cylindrical pin (so that the abutting face 80 is cylindrically shaped) and is located relative to the axial end face 126 such that a centeriine CLC of the clutch input structure 60 (i.e., taken perpendicular to the axial end face 126) is spaced radially outwardly of a longitudinal centeriine CLD of the wire that forms the clutch spring 64 at a point where the centeriine CLD intersects the axial end face 126. Construction in this manner can locate the centeriine CLD between the centeriine CLD and the rotational axis of the decoupler 10, which may help to trap the wire that forms the clutch spring 64 in some situations.
- the carrier 62 can be configured to be non-rotatably coupled to the input member 12.
- the flange portion 110 of the carrier 62 is notched as shown in Figure 4 to receive the clutch input structure 60 to maintain the carrier 62 (and therefore the first end 88 of the clutch spring 64) in a predetermined orientation relative to the clutch input structure 60.
- the carrier 62 has been described as having a flange portion 110 that is formed as a continuous annular structure, it will be appreciated that the carrier 62 could be formed in the alternative as a discontinuous annular structure.
- the flange portion 110 could be formed with a radial slit (not shown) to provide the carrier 62 with a greater degree of circumferential compliance.
- the carrier 62 could be press-fit to the annular shoulder 32 to couple the carrier to the input member 12 for rotation therewith.
- a backing member 130 can be coupled to the input hub 20 to inhibit withdrawal of the first end 88 of the clutch spring 64 from the groove 114.
- the backing member 130 is formed of steel and is press-fit to the input hub 20, but it will be appreciated that other coupling methods could be employed.
- the backing member 130 could comprise an external snap-ring or thrust washer (not shown) that could be coupled to the input hub 20 in an appropriate manner, such as being received in a correspondingly shaped ring groove (not shown).
- the clutch output member 66 can comprise a circumferentially extending structure that can be disposed about the helical coils 86 of the clutch spring 64.
- the clutch output member 66 can comprise a dutch surface 140 that can be engaged by the helical coils 86 of the clutch spring 64 as will be discussed in detail, below.
- the spring support 68 can comprise a tubular body portion 146 and an end flange 148.
- the tubular body portion 146 can be configured to be received between the hub member 30 and the helical coils 86 of the clutch spring 64.
- the end flange 148 can be configured to abut an axial end of the clutch spring 64 opposite the carrier 62.
- the end flange 148 has a helically contoured surface that directly abuts an axial end of the clutch spring 64.
- a tang slot 150 can be formed in the spring support 68 and can be sized to receive the tang 104 to couple the spring support 68 to the second end 90 of the clutch spring 64 for rotation therewith.
- the at least one isolating spring 72 can be received between the input driver 70 and the output driver 74 to transmit rotary power therebetween.
- the at least one isolating spring 72 comprises a single helical torsion spring 154, which opens (i.e., expands in a radial direction) with the transmission of increasing amounts of torque there through, while each of the input and output drivers 70 and 74 includes a helical spring groove 160 and a driver lug 162.
- the at least one isolating spring 72 could comprise one or more springs that are disposed circumferentially about the input hub 20.
- the helical torsion spring 154 can be axially compressed between the input driver 70 and the output driver 74.
- the helical torsion spring 154 is wound in a direction that is opposite the direction in which the clutch spring 64 is wound, but it will be appreciated that other configurations are within the scope of the present disclosure.
- the input driver 70 can be coupled to the clutch output member 66 for rotation therewith.
- the input driver 70 is integrally formed with the clutch output member 66 such that the clutch output member 66 is disposed axially along the length of the helical torsion spring 154. It will be appreciated that construction in this manner positions the at least a portion of the helical coils 86 of the clutch spring 64 in an axially overlapping manner with at least a portion of the coils of the helical torsion spring 154.
- One or more seals may be incorporated into the decoupler 10 to inhibit ingress of water and/or debris into the interior of the decoupler 10, and/or to maintain a lubricant in a portion of the decoupler 10.
- a first seal 170 is disposed between the annular shoulder 32 and the clutch output member 66
- a second seal 172 is disposed between the output driver 74 and the clutch output member 66
- a third seat is disposed between the input hub 20 and the output driver 74.
- the first, second and third seals 170, 172 and 174 cooperate to seal an internal cavity in which the clutch spring 64 is disposed.
- a suitable lubricant such as a grease, an oil or a traction fluid, could be employed to lubricate the helical coils 66 and the clutch surface 140.
- a suitable lubricant such as a grease, an oil or a traction fluid
- the second and third seals 172 and 174 are illustrated as being face seals, it will be appreciated that any type of seal could be employed.
- the third seal 174 can comprise a retaining member, such as a retaining ring 180, that can be received in a groove 162 formed in the input hub 20.
- the retaining member e.g., retaining ring 180
- the retaining member can limit axial movement of the output driver 74 away from the input driver 70.
- One or more bearings can be employed to support the input and output drivers 70 and 74 relative to the input hub 20.
- a first bearing 190 is disposed between the input driver 70 and the damper input member 22, while a second bearing 192 is disposed between the hub member 30 and the output driver 74.
- the first and second bearings 1 0 and 192 can be any type of bearing, but in the particular example provided, are thrust bushings.
- the first bearing 190 can comprise an annular portion 200, which can be configured to support the input driver 70 relative to a rotational axis of the input hub 20, and a radially extending portion 202 that can be configured to limit movement of the input driver 70 axially along the rotational axis of the input hub 20 in a direction toward the damper input member 22.
- the second bearing 192 can comprise an annular portion 206, which can be received between the hub member 30 and an annular collar 208 on the output driver 74 and configured to support the output driver 74 relative to the rotational axis of the input hub 20, and a radially extending portion 210 that can be configured to limit axial movement of the output driver 74 axiaily along the rotational axis of the input hub 20 in a direction away from the damper input member 22.
- the radially extending portion 210 is depicted as abutting the third seal 174, but it will be appreciated that the radially extending portion 210 could contact another structure, such as a rib (not shown) formed on the hub member 30 or a retaining ring (not shown) received in a groove (not shown) in the hub member 30.
- the output member 16 can be any type of structure that is configured to provide a rotary output, such as a pulley, a gear, a sprocket or a roller.
- the output member 16 comprises a pulley sheave 230 that is configured to engage a poly-V belt.
- the output member 16 can be rotatably coupled to the output driver 74 in any desired manner, such as a plurality of bolts, and/or one or more welds.
- the output member 16 includes an annular mounting hub 232 that is received over an annular, axially-extending rib 240 on the output driver 74.
- the circumferentially outer side of the rib 240 can align the output member 16 to the rotational axis of the output driver 74. while a seal lip 246 of the third seal 174 can sealingly engage the circumferentially inner side of the rib 240.
- the at least one isolating spring 72 will unload.
- a means can be provided to permit a relatively small torsional load to be transmitted from the output driver 74 to the input driver 70.
- the output driver 74 and the input driver 70 could have, for example, two or more mating lugs (not shown) that facilitate the transmission of rotary power from the output driver 74 to the input driver 70.
- the axial compression on the helical torsion spring 154 is sufficiently large so as to permit friction forces (i.e., between the ends of the helical torsion spring 54 and the input and output drivers 70 and 74) to carry a modest level of torque so that the output driver 74 can effectively back drive the input driver 70 (and the clutch output member 66 therewith).
- the back driving of the clutch output member 66 tends to cause the helical coils 66 of the clutch spring 64 to contract in a circumferential direction so that the clutch spring 64 at least partly disengages the dutch surface 140 of the clutch output member 66 to an extent where the clutch output member 66, the input driver 70, the output driver 74 and the output member 16 can over-run the input hub 20 in the predetermined rotational direction.
- the at least one isolating spring 72 comprises a torsion spring that is wrapped coaxially about the rotational axis of the decoupler 0
- the decoupler 10 could be formed so as to be rotationaliy imbalanced when no rotary load is transmitted through the decoupler 10, and the rotational imbalance can lessen as the rotary load transmitted through the decoupler 10 increases to a predetermined magnitude.
- the decoupler 10 can be configured to be rotationally balanced when a rotary load of a predetermined magnitude is transmitted through the decoupler 10.
- Rotation of the output driver 74 relative to the input hub 20 can be limited to a predetermined range having end points corresponding to a predetermined minimum loading of the at least one isolating spring 72 and a predetermined maximum loading of the at least one isolating spring 72.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Operated Clutches (AREA)
- Pulleys (AREA)
Abstract
Description
Claims
Priority Applications (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020127033630A KR20130108516A (en) | 2010-06-25 | 2011-06-22 | Isolation pulley with overrunning and vibration damping capabilities |
CN201180031578.8A CN102959262B (en) | 2010-06-25 | 2011-06-22 | There is the isolation belt wheel of the ability of surmounting and vibration damping ability |
CA2829076A CA2829076A1 (en) | 2010-06-25 | 2011-06-22 | Isolation pulley with overrunning and vibration damping capabilities |
BR112012029750A BR112012029750A2 (en) | 2010-06-25 | 2011-06-22 | uncoupler, and method for forming a decoupler |
EP11797419.6A EP2585727A4 (en) | 2010-06-25 | 2011-06-22 | Isolation pulley with overrunning and vibration damping capabilities |
US13/805,085 US9989103B2 (en) | 2010-06-25 | 2011-06-22 | Isolation pulley with overrunning and vibration damping capabilities |
JP2013515644A JP2013533439A (en) | 2010-06-25 | 2011-06-22 | Isolation pulley with overrunning and vibration damping capability |
US15/873,807 US10663008B2 (en) | 2010-06-25 | 2018-01-17 | Isolation pulley with overrunning and vibration damping capabilities |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US35854010P | 2010-06-25 | 2010-06-25 | |
US61/358,540 | 2010-06-25 |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/805,085 A-371-Of-International US9989103B2 (en) | 2010-06-25 | 2011-06-22 | Isolation pulley with overrunning and vibration damping capabilities |
US15/873,807 Continuation US10663008B2 (en) | 2010-06-25 | 2018-01-17 | Isolation pulley with overrunning and vibration damping capabilities |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011160208A1 true WO2011160208A1 (en) | 2011-12-29 |
Family
ID=45370782
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/CA2011/000726 WO2011160208A1 (en) | 2010-06-25 | 2011-06-22 | Isolation pulley with overrunning and vibration damping capabilities |
Country Status (8)
Country | Link |
---|---|
US (2) | US9989103B2 (en) |
EP (1) | EP2585727A4 (en) |
JP (1) | JP2013533439A (en) |
KR (1) | KR20130108516A (en) |
CN (1) | CN102959262B (en) |
BR (1) | BR112012029750A2 (en) |
CA (1) | CA2829076A1 (en) |
WO (1) | WO2011160208A1 (en) |
Cited By (14)
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WO2012079155A1 (en) * | 2010-12-16 | 2012-06-21 | Litens Automotive Partnership | Clutched driven device |
WO2012102946A1 (en) * | 2011-01-24 | 2012-08-02 | The Gates Corporation (A Delaware Corporation) | Isolating decoupler |
CN102817936A (en) * | 2012-09-05 | 2012-12-12 | 李志敏 | Spring friction clutch mechanism for belt pulley and one-way coupling damping belt pulley |
WO2013131166A1 (en) * | 2011-08-08 | 2013-09-12 | Litens Automotive Partnership | Decoupler assembly |
WO2013184241A1 (en) * | 2012-06-04 | 2013-12-12 | The Gates Corporation | Isolator decoupler |
WO2014036625A3 (en) * | 2012-09-10 | 2014-05-15 | Zen S/A Indústria Metalúrgica | Decoupler with free wheel system and vibration dampening |
WO2016039903A1 (en) * | 2014-09-10 | 2016-03-17 | Gates Corporation | Crankshaft isolating pulley |
US9291253B1 (en) | 2015-03-24 | 2016-03-22 | Gates Corporation | Isolating decoupler |
US9638270B2 (en) | 2012-08-07 | 2017-05-02 | Litens Automotive Partnership | Decoupler carrier with balanced forces |
US9651099B2 (en) | 2013-01-25 | 2017-05-16 | Litens Automotive Partnership | Clutched device with wrap spring clutch with overrun locking member |
CN110273932A (en) * | 2013-08-27 | 2019-09-24 | 利滕斯汽车合伙公司 | Isolator used in the engine for being assisted or being started by endless drive component as motor generator unit or motor |
US11236812B2 (en) | 2012-09-10 | 2022-02-01 | Zen S/A Industria Metalurgica | Decoupler with one-way clutch and fail-safe system |
DE102013206444B4 (en) | 2012-04-24 | 2022-05-25 | Schaeffler Technologies AG & Co. KG | drive wheel |
US11549558B2 (en) | 2018-08-01 | 2023-01-10 | Gates Corporation | Isolator decoupler |
Families Citing this family (14)
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CN106687717B (en) * | 2014-09-10 | 2019-03-08 | 盖茨公司 | Belt pulley is isolated in crankshaft |
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Also Published As
Publication number | Publication date |
---|---|
BR112012029750A2 (en) | 2016-08-09 |
US10663008B2 (en) | 2020-05-26 |
JP2013533439A (en) | 2013-08-22 |
CN102959262A (en) | 2013-03-06 |
US9989103B2 (en) | 2018-06-05 |
US20130087428A1 (en) | 2013-04-11 |
CN102959262B (en) | 2016-01-20 |
US20180142738A1 (en) | 2018-05-24 |
KR20130108516A (en) | 2013-10-04 |
EP2585727A1 (en) | 2013-05-01 |
CA2829076A1 (en) | 2011-12-29 |
EP2585727A4 (en) | 2018-03-28 |
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