EP1208316A1 - Freilaufkupplungsriemenscheibe mit geschlossenem kupplungshohlraum - Google Patents

Freilaufkupplungsriemenscheibe mit geschlossenem kupplungshohlraum

Info

Publication number
EP1208316A1
EP1208316A1 EP01950264A EP01950264A EP1208316A1 EP 1208316 A1 EP1208316 A1 EP 1208316A1 EP 01950264 A EP01950264 A EP 01950264A EP 01950264 A EP01950264 A EP 01950264A EP 1208316 A1 EP1208316 A1 EP 1208316A1
Authority
EP
European Patent Office
Prior art keywords
sheave
clutch
hub
over
section
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.)
Withdrawn
Application number
EP01950264A
Other languages
English (en)
French (fr)
Inventor
Russell Monahan
Randall King
John Miller
Robert Frayer
Bryce Babcock
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BABCOCK, BRYCE
Frayer Robert
KING, RANDALL
MILLER, JOHN
MONAHAN, RUSSELL
NTN Corp
Original Assignee
Frayer Robert
Monahan Russell
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Frayer Robert, Monahan Russell filed Critical Frayer Robert
Publication of EP1208316A1 publication Critical patent/EP1208316A1/de
Withdrawn legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H55/00Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32Friction members
    • F16H55/36Pulleys
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00Freewheels or freewheel clutches
    • F16D41/20Freewheels or freewheel clutches with expandable or contractable clamping ring or band
    • F16D41/206Freewheels or freewheel clutches with expandable or contractable clamping ring or band having axially adjacent coils, e.g. helical wrap-springs

Definitions

  • This invention relates generally to devices in the over-running clutch field, and more specifically to an improved over-running clutch pulley for use with an accessory device driven by an automotive engine with a belt drive.
  • a drive belt is typically used to power and operate various accessory devices.
  • One of these accessory devices is typically an automotive alternator, which provides electrical power to the automobile.
  • the serpentine arrangement which drives several accessory devices, is currently most favored.
  • Serpentine arrangements typically include a drive pulley connected to the crankshaft of the engine (the “output device") and a drive belt trained about the drive pulley.
  • the drive belt is also trained about one or more conventional driven pulleys, which are connected to the input shafts of various accessories devices (the "input device").
  • the drive belt may experience many instances of sudden deceleration relative to the input shaft. This situation may occur, for example, during a typical shift from first gear to second gear under wide open throttle acceleration. This situation is worsened if the throttle is closed or "back off immediately after the shift. In these situations, the drive belt decelerates very quickly while the driven pulley, with the high inertia from the accessory device, maintains a high rotational speed, despite the friction between the drive belt and the driven pulley.
  • the drive belt may experiences other situations that cause audible vibration and undue wear.
  • a serpentine arrangement with conventional driven pulleys may be used with an automobile engine that has an extremely low idle engine speed (which may increase fuel economy).
  • the arrangement typically experiences "belt flap" of the drive belt as the periodic cylinder firing of the automotive engine causes the arrangement to resonate within a natural frequency and cause an audible vibration and an undue wear on the drive belt.
  • the disadvantage of the conventional driven pulleys namely the audible squeal, the undue wear, and the vibration of the drive belt, may be avoided by the use of an over-running clutch pulley instead of the conventional driven pulley.
  • An over-running clutch pulley allows the pulley to continue to rotate at the same rotational speed and in a same rotational direction after a sudden deceleration of the drive belt.
  • the over-running clutch pulley functions like the rear hub of a typical bicycle; the rear hub and rear wheel of a conventional bicycle continue to rotate at the same rotational speed and in the same rotational direction even after a sudden deceleration of the pedals and crankshaft of the bicycle.
  • An example of an over-running clutch pulley is described in U.S. Patent No. 5,598,913 issued to the same assignee of this invention and hereby incorporated in its entirety by this reference.
  • This invention provides an over-running clutch pulley with a closed clutch cavity, which is intended to increase wear resistance while minimizing the costs and weight.
  • FIG. 1 is a perspective view of an over-running clutch pulley of the invention, shown with a drive belt as the input device and a cylindrical shaft as the output device;
  • FIG. 2 is a partial cross-section view, taken along the line 2-2 of FIG. 1 , of the overrunning clutch pulley of a first preferred embodiment
  • FIG. 3 is a partial cross-section view, similar to FIG. 2, of the over-running clutch pulley of a second preferred embodiment
  • FIG. 4 is a partial cross-section view, similar to FIG. 2, of the over-running clutch pulley of a third preferred embodiment
  • FIG. 5 is a partial cross-section view, similar to FIG. 2, of the over-running clutch pulley of a fourth preferred embodiment.
  • FIG. 6 is a partial cross-section view, similar to FIG. 2, of the over-running clutch pulley of a fifth preferred embodiment.
  • the invention includes an over-running clutch pulley 10 for rotationally engaging an input device 12 and an output device 14.
  • the over-running clutch pulley 10 has been designed for use with a drive belt 16 as the input device 12, and with a cylindrical shaft 18 as the output device 14. More specifically, the over-running clutch pulley 10 has been particularly designed for use with a drive belt 16 with a grooved surface and a cylindrical shaft 18 of an automotive alternator.
  • the over-running clutch pulley 10 may be used, however, in other environments, with other suitable input devices, such as smooth belt, a toothed belt, a V- shaped belt, or even a toothed gear, and with other suitable output devices, such as a polygonal shaft.
  • the over-running clutch pulley 10 may be used in an environment with two devices that alternate their rotational input responsibilities, and in an environment with an "output device” that actually provides rotational input and with an "input device” that actually receives rotational input.
  • the terms “input device” and “output device” are interchangeable.
  • the over-running clutch pulley 10 of the preferred embodiment includes a sheave member 20, a hub member 22 located substantially concentrically within the sheave member 20, a bearing member 24, a sealing member 26, and a clutch member 28, which cooperate to rotationally engage the drive belt and the cylindrical shaft.
  • the sheave member 20 preferably includes a sheave input section 30 adapted to the engage the input device, and a sheave clutch section 32 defining a sheave clutch surface 34.
  • the hub member 22 preferably includes a hub output section 36 adapted to engage the output device, and a hub clutch section 38 defining a hub clutch surface 40.
  • the bearing member 24 preferably positions the sheave member 20 and the hub member 22 such that the sheave member 20 and the hub member 22 define a radial gap 42.
  • the sheave input section 30 of the sheave member 20 of the preferred embodiment functions to engage the drive belt.
  • the sheave input section 30 preferably defines a sheave input surface 46 with two sheave input shoulders 48 and at least one sheave input groove 50.
  • the sheave input section 30 may alternatively define other suitable surfaces, such as toothed surfaces or ribbed surfaces, to engage the input device.
  • the sheave input surface 46 is preferably outwardly directed (away from the rotational axis of the over-running clutch pulley 10) and is preferably substantially cylindrically shaped.
  • the sheave input section 30 is preferably made from conventional structural materials, such as steel, and with conventional methods, but may alternatively be made from other suitable materials (as described below) and from other suitable methods.
  • the hub output section 36 of the hub member 22 of the preferred embodiment functions to engage the cylindrical shaft.
  • the hub output section 36 preferably defines a hub output surface 52 with a smooth section 54 (which functions to ease and center the assembly of the over-running clutch pulley 10 onto the cylindrical shaft), a threaded section 56 (which functions to substantially prevent rotation and to axially retain the hub member 22 to the cylindrical shaft), and a hexagonal section 58 (which functions to mate with an alien wrench for easy tightening and loosening of the over-running clutch pulley 10 onto and off of the cylindrical shaft).
  • the hub output section 36 may include other suitable devices or define other surfaces to prevent rotational and axial slippage, to engage the cylindrical shaft, and to engage a tool for tightening or loosening the over-running clutch pulley 10 onto and off of the cylindrical shaft.
  • the hub output surface 52 is preferably inwardly directed (toward the rotational axis of the overrunning clutch pulley 10) and is preferably substantially cylindrically shaped.
  • the hub output section 36 is preferably made from conventional structural materials, such as steel, and with conventional methods, but may alternatively be made from other suitable materials (as described below) and from other suitable methods.
  • the sheave clutch section 32 and the hub clutch section 38 of the preferred embodiment function to provide the sheave clutch surface 34 and the hub clutch surface 40, respectively, for the engagement with the clutch member 28.
  • the sheave clutch section 32 preferably extends radially inward from the sheave member 20. In this manner, the sheave clutch section 32 is preferably made from the same material and with the same methods as the sheave input section 30, but may alternatively be made from other suitable materials and with other suitable methods.
  • the hub clutch section 38 preferably extends radially outward from and axially over the hub output section 36. In this manner, the hub clutch section 38 is preferably made from the same material and with the same methods as the hub output section 36, but may alternatively be made from other suitable materials and with other suitable methods.
  • the sheave clutch surface 34 and the hub clutch surface 40 are located substantially adjacent with an axial gap 60 between each other.
  • the sheave clutch surface 34 and the hub clutch surface 40 are preferably inwardly directed (toward the rotational axis of the over-running clutch pulley 10) and are preferably substantially cylindrically shaped.
  • the sheave clutch surface 34 and the hub clutch surface 40 preferably have a similar radial diameter, a similar axial length, and a similar smooth finish. These features allow optimum performance of the clutch member 28.
  • the sheave clutch surface 34 and the hub clutch surface 40 may alternatively have differences with each other on these, or other, design specifications.
  • the bearing member 24 In addition to positioning the sheave member 20 and the hub member 22 such that the sheave member 20 and the hub member 22 define the radial gap 42 and the axial gap 60, the bearing member 24 also functions to allow relative rotational movement of the sheave member 20 and the hub member 22.
  • the bearing member 24, which is preferably a rolling element type, preferably includes an outer race element 62 preferably press-fit mounted on the sheave member 20, an inner race element 64 preferably press-fit mounted on the hub member 22, ball bearing elements 66 preferably located between the outer race element 62 and the inner race element 64, and bearing seals 68 preferably extending between the outer race element 62 and the inner race element 64 on either side of the ball bearing elements 66.
  • the bearing member 24 may alternatively omit the bearing seal 68 facing the clutch member 28 if the over-running clutch pulley 10 uses a grease material compatible with the bearing member 24 and the clutch member 28.
  • the bearing member 24 may alternatively be of other suitable types, such as a journal bearing or a roller bearing, may alternatively include other suitable elements, such as a so-called "slinger" shield 69 to prevent direct impingement of water or contaminants, and may alternatively be mounted in other suitable manners.
  • the bearing member 24 is a conventional device and, as such, is preferably made from conventional materials and with conventional methods, but may alternatively be made from other suitable materials and with other suitable methods.
  • the axial gap 60 and the radial gap 42 are interconnected, which function to substantially prevent contact between the sheave member 20 and the hub member 22.
  • the sealing member 26, which is preferably located within the radial gap 42, preferably functions to substantially prevent passage through the radial gap 42 of any fluid, namely a grease material (not shown) located in the closed clutch cavity 44 and subjected to centrifugal forces during the operation of the over-running clutch pulley 10.
  • the sealing member 26 also functions to allow relative rotational movement of the sheave member 20 and the hub member 22.
  • the sealing member 26 is a four-lobed O-ring 70 made from a conventional material and with conventional methods.
  • the sealing member 26 is any suitable device made from any suitable material and with any suitable method that substantially prevents leakage of a fluid from the closed clutch cavity 44 while simultaneously allowing relative rotational movement of the sheave member 20 and the hub member 22.
  • the hub clutch section 38 defines a hub outboard cavity 72 that functions to substantially contain the sealing member 26. Because of the nature of the hub outboard cavity 72, centrifugal forces on the sealing member 26 tend to further increase the ability of the sealing member 26 to substantially prevent passage of any fluid through the radial gap 42.
  • both the sheave member 20 and the hub member 22 may define portions of a gland that functions to substantially contain the sealing member 26.
  • the clutch member 28 of the preferred embodiment functions to engage the sheave clutch surface 34 and the hub clutch surface 40 upon the acceleration of the sheave member 20 in a first rotational direction relative to the hub member 22, and to disengage the sheave clutch surface 34 and the hub clutch surface 40 upon the deceleration of the sheave member 20 in the first rotational direction relative to the hub member 22.
  • the clutch member 28 is a coil spring 74.
  • the coil spring 74 which is made from conventional materials and with conventional methods, accomplishes the above features by the particular size and orientation of the coil spring 74 within the closed clutch cavity 44.
  • the clutch member 28 may include other suitable devices that accomplish the above features.
  • the coil spring 74 is preferably designed with a relaxed spring radial diameter that is sized slightly greater than an inner diameter of the sheave clutch surface 34 and the hub clutch surface 40.
  • the coil spring 74 frictionally engages with and exerts an outward force on both the sheave clutch surface 34 and the hub clutch surface 40.
  • the coil spring 74 is preferably oriented within the closed clutch cavity 44 such that the coils extend axially in the first rotational direction from the sheave clutch surface 34 to the hub clutch surface 40. With this orientation, relative rotational movement of the sheave member 20 and the hub member 22 will result in an unwinding or winding of the clutch member 28.
  • acceleration of the sheave member 20 in the first rotational direction relative to the hub member 22 will bias an unwinding of the coil spring 74 and deceleration of the sheave member 20 in the first rotational direction relative to the hub member 22 will bias a winding of the coil spring 74.
  • the unwinding of the coil spring 74 tends to increase the outward force of the coil spring 74 on the sheave clutch surface 34 and the hub clutch surface 40, thereby providing engagement, or "lock", of the sheave member 20 and the hub member 22.
  • This engagement condition preferably occurs upon the acceleration of the sheave member 20 in the first rotational direction relative to the hub member 22.
  • the winding of the coil spring 74 tends to decrease the outward force of the coil spring 74 on the sheave clutch surface 34 and the hub clutch surface 40, thereby allowing disengagement, or "slip", of the sheave member 20 and the hub member 22.
  • This disengagement condition preferably occurs upon the deceleration of the sheave member 20 in the first rotational direction relative to the hub member 22.
  • the coil spring 74 will lightly rub across the sheave clutch surface 34 or the hub clutch surface 40, which may cause wear of these surfaces.
  • the coil spring 74 will forcefully engage with the sheave clutch surface 34 and the hub clutch surface 40, which may also cause wear of these surfaces.
  • the sheave clutch surface 34 and the hub clutch surface 40 are preferably formed or treated to have a sufficient surface hardness value.
  • the sheave member 20 includes a sheave collar section 76 defining a sheave collar surface 78, and the hub clutch section 38 defines a hub flange surface 80.
  • the sheave collar section 76 preferably extends radially inward from the sheave input section 30 and adjacent the sheave clutch section 32.
  • the sheave collar section 76 preferably extends partially into the closed clutch cavity 44.
  • the inboard seal 68 preferably prevents the passage of debris and impurities between the grease material (not shown) for the bearing member 24 and the grease material (not shown) for the clutch member 28.
  • the second preferred embodiment as shown in FIG.
  • the sheave collar section 76' preferably substantially abuts the hub output section 36 and preferably prevents the passage of debris and impurities between the grease material (not shown) for the bearing member 24 and the grease material (not shown) for the clutch member 28, which allows for the absence of the inboard bearing seal (appropriately not shown).
  • the sheave collar surface 78 and the hub flange surface 80 are preferably located on opposite ends of the clutch member 28. In this manner, the sheave collar surface 78 and the hub flange surface 80 cooperate to insure the proper placement of the clutch member 28 within the closed clutch cavity 44.
  • the over-running clutch pulley 10 may, of course, use other suitable devices to insure the proper placement of the clutch member 28 within the closed clutch cavity 44. These devices may be surfaces defined by other sections of the sheave member 20 or the hub member 22, or surfaces defined by other suitable elements.
  • the sheave collar section 76 and 76' is integrally formed with the sheave input section 30.
  • the sheave clutch section 32 is preferably made from the same material and with the same methods as the sheave input section 30.
  • the sheave collar section 76" may be separately formed and later connected to the sheave input section 30, as shown in FIG. 4.
  • the sheave collar section 76" is preferably provided as a conventional washer 82 made from conventional materials and with conventional methods, but may alternatively be provided as any suitable device made from any suitable material and with any suitable method.
  • the coil spring 74 is preferably positioned over the axial gap 60.
  • the axial gap 60 is preferably less than 0.75 of a spring coil thickness of an individual spring coil. Further, because the contact between the sheave member 20 and the hub member 22 could cause undue wear, the axial gap 60 is preferably greater than 0.25 of the spring coil thickness to allow for normal flexing and dimensional variations of the over-running clutch pulley 10.
  • the axial gap 60 may be greater than 0.75 or less than 0.25 of the spring coil thickness if other suitable devices or methods are used to substantially prevent undue wear caused by contact between the sheave member 20 and the hub member 22 and to substantially prevent jams and wear caused by an individual spring coil into the axial gap 60.
  • the sheave input section 30 in the fourth preferred embodiment defines a sheave inboard gland 84 adapted to substantially collect and contain fluid from the axial gap 60.
  • the fluid namely the grease material (not shown) for the clutch member 28, may be contaminated with debris particles created from wear between the clutch member 28 and sheave clutch surface 34 and the hub clutch surface 40. Since the debris particles are typically heavier than the grease material, providing the sheave inboard gland 84 allows centrifugal forces on the over-running clutch pulley 10 to pull the debris particles away from the clutch member 28, thereby reducing undue wear of the clutch member 28, the sheave clutch surface 34, and the hub clutch surface 40.
  • the hub clutch section 38' in the fifth preferred embodiment defines a hub inboard gland 86, which functions like the sheave outboard gland of the fourth preferred embodiment.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pulleys (AREA)
  • Mechanical Operated Clutches (AREA)
  • Transmission Devices (AREA)
  • Transmissions By Endless Flexible Members (AREA)
  • Sealing Devices (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Lubricants (AREA)
EP01950264A 2000-05-31 2001-05-31 Freilaufkupplungsriemenscheibe mit geschlossenem kupplungshohlraum Withdrawn EP1208316A1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US20824400P 2000-05-31 2000-05-31
US208244P 2000-05-31
PCT/US2001/017640 WO2001092746A1 (en) 2000-05-31 2001-05-31 Over-running clutch pulley with closed clutch cavity

Publications (1)

Publication Number Publication Date
EP1208316A1 true EP1208316A1 (de) 2002-05-29

Family

ID=22773841

Family Applications (10)

Application Number Title Priority Date Filing Date
EP01939729A Withdrawn EP1208314A1 (de) 2000-05-31 2001-05-28 Freilaufkupplungsriemenscheibe mit schwimmender feder
EP01944187A Withdrawn EP1284832A1 (de) 2000-05-31 2001-05-31 Verfahren zur herstellung einer freilaufkupplungsriemenscheibe mit verformbarer oberfläche
EP01946024A Withdrawn EP1208315A4 (de) 2000-05-31 2001-05-31 Freilaufkupplungsriemenscheibe mit erhöhter oberflächenmikrohärte
EP01950264A Withdrawn EP1208316A1 (de) 2000-05-31 2001-05-31 Freilaufkupplungsriemenscheibe mit geschlossenem kupplungshohlraum
EP01939788A Withdrawn EP1284831A1 (de) 2000-05-31 2001-05-31 Verfahren zur herstellung einer freilaufkupplungsriemenscheibe mit halterungsteil
EP01939683A Withdrawn EP1208310A4 (de) 2000-05-31 2001-05-31 Freilaufkupplungsriemenscheibe mit einem kupplungs- und lagerschmiermittel
EP01950263A Withdrawn EP1285177A1 (de) 2000-05-31 2001-05-31 Freilaufkupplungsriemenscheibe mit schlupfbeeinflussung
EP01941715A Withdrawn EP1208312A1 (de) 2000-05-31 2001-05-31 Freilaufkupplungsriemenscheibe mit einem offenen hohlraum
EP01939732A Withdrawn EP1208311A1 (de) 2000-05-31 2001-05-31 Freilaufkupplungsriemenscheibe mit einem dichtelelemt
EP01941714A Withdrawn EP1208318A4 (de) 2000-05-31 2001-05-31 Freilaufkupplungsriemenscheibe mit einem beschichtungsmaterial

Family Applications Before (3)

Application Number Title Priority Date Filing Date
EP01939729A Withdrawn EP1208314A1 (de) 2000-05-31 2001-05-28 Freilaufkupplungsriemenscheibe mit schwimmender feder
EP01944187A Withdrawn EP1284832A1 (de) 2000-05-31 2001-05-31 Verfahren zur herstellung einer freilaufkupplungsriemenscheibe mit verformbarer oberfläche
EP01946024A Withdrawn EP1208315A4 (de) 2000-05-31 2001-05-31 Freilaufkupplungsriemenscheibe mit erhöhter oberflächenmikrohärte

Family Applications After (6)

Application Number Title Priority Date Filing Date
EP01939788A Withdrawn EP1284831A1 (de) 2000-05-31 2001-05-31 Verfahren zur herstellung einer freilaufkupplungsriemenscheibe mit halterungsteil
EP01939683A Withdrawn EP1208310A4 (de) 2000-05-31 2001-05-31 Freilaufkupplungsriemenscheibe mit einem kupplungs- und lagerschmiermittel
EP01950263A Withdrawn EP1285177A1 (de) 2000-05-31 2001-05-31 Freilaufkupplungsriemenscheibe mit schlupfbeeinflussung
EP01941715A Withdrawn EP1208312A1 (de) 2000-05-31 2001-05-31 Freilaufkupplungsriemenscheibe mit einem offenen hohlraum
EP01939732A Withdrawn EP1208311A1 (de) 2000-05-31 2001-05-31 Freilaufkupplungsriemenscheibe mit einem dichtelelemt
EP01941714A Withdrawn EP1208318A4 (de) 2000-05-31 2001-05-31 Freilaufkupplungsriemenscheibe mit einem beschichtungsmaterial

Country Status (3)

Country Link
EP (10) EP1208314A1 (de)
JP (10) JP2003535281A (de)
WO (10) WO2001092745A1 (de)

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20120099786A (ko) * 2002-07-26 2012-09-11 리텐스 오토모티브 파트너쉽 디커플러 조립체
KR101068335B1 (ko) 2003-02-04 2011-09-28 리텐스 오토모티브 파트너쉽 크랭크축 토크 변조기
JP4380234B2 (ja) * 2003-06-19 2009-12-09 Nok株式会社 パワーステアリング用密封装置
PL2273144T3 (pl) * 2003-09-22 2013-04-30 Litens Automotive Inc Odprzęgacz wału korbowego
CA2547383C (en) 2003-12-09 2013-08-13 Litens Automotive Partnership Spring travel limiter for overrunning alternator decoupler
JP5008928B2 (ja) * 2005-10-31 2012-08-22 三ツ星ベルト株式会社 プーリ構造体
JP5507608B2 (ja) * 2005-10-31 2014-05-28 三ツ星ベルト株式会社 プーリ構造体
JP2007139029A (ja) * 2005-11-16 2007-06-07 Ntn Corp 電動アクチュエータ
DE102007038209B3 (de) * 2007-08-13 2009-01-15 Carl Freudenberg Kg Vorrichtung zur Verwendung im Antrieb einer Lichtmaschine
CN102906441B (zh) * 2010-05-25 2016-11-09 利滕斯汽车合伙公司 在毂与带轮之间具有滑动界面的解耦器组件
GB201107466D0 (en) 2011-05-05 2011-06-15 Loktionov Alexandre Device and method for non-invasive collection of colorectal mucocellular layer and disease detection
FR2995056B1 (fr) * 2012-09-04 2015-07-03 Skf Ab Systeme mecanique a embrayage unidirectionnel, alternateur et procede de fabrication d'un tel systeme
BR102012022803B1 (pt) * 2012-09-10 2017-05-02 Zen S/A Indústria Metalúrgica desacoplador com sistema de roda livre e amortecimento de vibrações
JP6020029B2 (ja) * 2012-10-19 2016-11-02 株式会社豊田自動織機 ベーン型圧縮機
US9140319B2 (en) 2012-11-20 2015-09-22 Litens Automotive Partnership Decoupler with concentric clutching members
US9033832B1 (en) 2014-01-23 2015-05-19 Gates Corporation Isolating decoupler
CN104373552B (zh) * 2014-11-28 2017-02-01 中国石油天然气股份有限公司 具有皮带断折保护装置的皮带轮
US9291253B1 (en) 2015-03-24 2016-03-22 Gates Corporation Isolating decoupler
CN107467252B (zh) * 2017-09-08 2020-11-13 勐海悦朋轩茶业有限公司 一种智能化红茶发酵设备
CN112091534A (zh) * 2020-08-12 2020-12-18 芜湖亿联旋压科技有限公司 一种离合器毂的旋压制造方法

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2101130A (en) * 1935-06-29 1937-12-07 Packard Motor Car Co Motor vehicle
US2794524A (en) * 1954-09-01 1957-06-04 Curtiss Wright Corp Spring clutch mechanisms
US2906005A (en) * 1956-03-19 1959-09-29 Racine Ind Plant Inc Method of securing needle bearings in nylon gears
US3047300A (en) * 1959-07-01 1962-07-31 Lockheed Aircraft Corp Metal sealing assembly
US3926286A (en) * 1973-02-05 1975-12-16 Reell Precision Mfg Spring grip clutch
US3831723A (en) * 1973-04-18 1974-08-27 Gen Motors Corp Electromagnetic spring-wound clutch
US4725260A (en) * 1987-03-24 1988-02-16 Litens Automotive Inc. Belt tensioner with spring actuated band brake damping
JPH01279117A (ja) * 1988-04-28 1989-11-09 Matsushita Electric Ind Co Ltd 流体軸受装置
US5061090A (en) * 1990-05-31 1991-10-29 Porter-Cable Corporation Shaft and bearing assembly
US5288683A (en) * 1990-10-30 1994-02-22 Chuetsu Metal Works Co., Ltd. Wear-resistant copper alloys and synchronizer rings for automobiles comprising the same
US5156573A (en) * 1991-06-05 1992-10-20 Litens Automotive Partnership Serpentine drive with coil spring-one-way clutch alternator connection
CA2074637C (en) * 1991-07-31 1998-11-10 Kazuki Kawashima Belt tension adjusting device
JPH0560144A (ja) * 1991-08-29 1993-03-09 Ntn Corp グリース封入転がり軸受
JP3114378B2 (ja) * 1991-09-20 2000-12-04 日本精工株式会社 転がり軸受
US5325950A (en) * 1992-08-31 1994-07-05 Ingersoll-Rand Company Lubricant remover for a wrap spring clutch
DE9417045U1 (de) * 1994-10-22 1994-12-15 Schaeffler Waelzlager Kg Vorrichtung zur Dämpfung von Drehschwingungen in einem Antriebsstrang
JPH08317599A (ja) * 1995-05-22 1996-11-29 Mitsubishi Electric Corp 車両用発電機
US5598913A (en) 1995-06-07 1997-02-04 Ntn Corporation One-way over-running clutch pulley
DE19535889A1 (de) * 1995-09-27 1997-04-03 Schaeffler Waelzlager Kg Freilaufkupplung für einen Lichtmaschinenantrieb
SE9602257L (sv) * 1996-06-07 1997-12-08 Plannja Hardtech Ab Sätt att framställa ståldetalj
US5822859A (en) * 1996-10-07 1998-10-20 General Motors Corporation Bearing with integrally retained separable race
JPH11218144A (ja) * 1997-11-17 1999-08-10 Nippon Seiko Kk ワンウェイクラッチ内蔵転がり軸受
JP4327929B2 (ja) * 1999-03-03 2009-09-09 協同油脂株式会社 低騒音性に優れたウレアグリースの製造方法

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0192746A1 *

Also Published As

Publication number Publication date
JP2003535273A (ja) 2003-11-25
JP2003535283A (ja) 2003-11-25
EP1208315A4 (de) 2006-01-18
WO2001091938A1 (en) 2001-12-06
WO2001092746A1 (en) 2001-12-06
JP2004514092A (ja) 2004-05-13
EP1208314A1 (de) 2002-05-29
WO2001092740A1 (en) 2001-12-06
EP1208311A1 (de) 2002-05-29
JP2003535280A (ja) 2003-11-25
EP1284832A1 (de) 2003-02-26
WO2001092743A1 (en) 2001-12-06
EP1284831A1 (de) 2003-02-26
JP2003535279A (ja) 2003-11-25
EP1285177A1 (de) 2003-02-26
WO2001092742A1 (en) 2001-12-06
JP2003535281A (ja) 2003-11-25
WO2001092745A1 (en) 2001-12-06
EP1208310A4 (de) 2006-01-18
JP2003535278A (ja) 2003-11-25
WO2001092747A1 (en) 2001-12-06
JP2003535287A (ja) 2003-11-25
WO2001092741A1 (en) 2001-12-06
EP1208318A1 (de) 2002-05-29
WO2001092760A1 (en) 2001-12-06
JP2003535282A (ja) 2003-11-25
EP1208310A1 (de) 2002-05-29
JP2004501326A (ja) 2004-01-15
EP1208315A1 (de) 2002-05-29
EP1208318A4 (de) 2006-01-18
WO2001091939A1 (en) 2001-12-06
EP1208312A1 (de) 2002-05-29

Similar Documents

Publication Publication Date Title
EP1367282B1 (de) Freilaufkupplungsriemenscheibe mit einem Kupplungssteckmodul
US7052420B2 (en) Over-running clutch pulley with coating material
EP1208316A1 (de) Freilaufkupplungsriemenscheibe mit geschlossenem kupplungshohlraum
US6637570B2 (en) Over-running clutch pulley with composite sealing member
US6691846B2 (en) Over-running clutch pulley with shortened depth
US7191880B2 (en) Over-running clutch pulley with increased surface microhardness
KR101167472B1 (ko) 오버러닝 교류 발전기 디커플러용 스프링 활주 리미터
JPH09119509A (ja) 一方向オーバーランニングクラッチプーリー装置
US6237736B1 (en) One-way clutch built-in type pulley apparatus for alternator and method for preventing squeal of endless belt for driving alternator
US6923303B2 (en) Over-running clutch pulley with clutch and bearing lubricant
WO2002052162A2 (en) Over-running clutch pulley with tool bores

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: BABCOCK, BRYCE

Owner name: MILLER, JOHN

Owner name: FRAYER, ROBERT

Owner name: NTN CORPORATION

Owner name: MONAHAN, RUSSELL

Owner name: KING, RANDALL

RIN1 Information on inventor provided before grant (corrected)

Inventor name: MONAHAN, RUSSELL

Inventor name: BABCOCK, BRYCE

Inventor name: FRAYER, ROBERT

Inventor name: NTN CORPORATION

Inventor name: KING, RANDALL

Inventor name: MILLER, JOHN

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: NTN CORPORATION

Owner name: FRAYER, ROBERT

Owner name: MILLER, JOHN

Owner name: KING, RANDALL

Owner name: BABCOCK, BRYCE

Owner name: MONAHAN, RUSSELL

RIN1 Information on inventor provided before grant (corrected)

Inventor name: MONAHAN, RUSSELL

Inventor name: NTN CORPORATION

Inventor name: KING, RANDALL

Inventor name: FRAYER, ROBERT

Inventor name: BABCOCK, BRYCE

Inventor name: MILLER, JOHN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20030103