US20080099295A1 - Overrunning bi-directional clutch as gear synchronizer and coupler - Google Patents

Overrunning bi-directional clutch as gear synchronizer and coupler Download PDF

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Publication number
US20080099295A1
US20080099295A1 US11/924,030 US92403007A US2008099295A1 US 20080099295 A1 US20080099295 A1 US 20080099295A1 US 92403007 A US92403007 A US 92403007A US 2008099295 A1 US2008099295 A1 US 2008099295A1
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United States
Prior art keywords
outer shell
shell
grooves
depressions
needles
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.)
Abandoned
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US11/924,030
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English (en)
Inventor
Brian Lee
Jeffrey Hemphill
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IHO Holding GmbH and Co KG
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Schaeffler KG
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Filing date
Publication date
Application filed by Schaeffler KG filed Critical Schaeffler KG
Priority to US11/924,030 priority Critical patent/US20080099295A1/en
Assigned to SCHAEFFLER KG reassignment SCHAEFFLER KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HEMPHILL, JEFFREY, LEE, BRIAN
Publication of US20080099295A1 publication Critical patent/US20080099295A1/en
Priority to US13/271,114 priority patent/US8544625B2/en
Abandoned legal-status Critical Current

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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
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/08—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
    • F16D41/086—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action the intermediate members being of circular cross-section and wedging by rolling
    • F16D41/088—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action the intermediate members being of circular cross-section and wedging by rolling the intermediate members being of only one size and wedging by a movement not having an axial component, between inner and outer races, one of which is cylindrical

Definitions

  • the invention concerns an over-running bi-directional clutch (ORBDC) used as a gear synchronizer, or coupler or any applications between a relatively moveable internal shaft, or the like, and an external shaft, gear, or other couplable element that is external to the ORBDC.
  • ORBDC over-running bi-directional clutch
  • Applicant proposes use of the ORBDC hereof during a power shift in transmissions of the automated manual type or in active or passive transfers in four wheel drive or all wheel drive vehicle applications.
  • ORBDCs in general and the ORBDC hereof in particular are distinguishable from traditional manual transmissions and transfer case systems which utilize synchronizer components (forks, rings, cones, dog teeth, etc.) to match gear input/output speeds during gear selection and shifting, and to lock the selected gear for power transfer
  • synchronizer components forks, rings, cones, dog teeth, etc.
  • These components are expensive, heavy, and large. Therefore traditional systems are relatively more expensive, more massive, and require larger packaging volume than the proposed solution ORBDC of the present invention.
  • the invention therefore reduces system package size and mass as compared with traditional synchronizer component systems.
  • ORBDC is a known construction and examples of it appear U.S. Pat. Nos. 6,409,001, 6,097,206, and 6,974,400. It provides two operational modes in its position in a typical application, e.g., inside a speed gear and fixed to a power transmission shaft 1) as an over-running plain bearing for gear rotation when the clutch is unblocked, and 2) as a rigid coupling for transfer of torque from the gear to the shaft, or vice versa, when the clutch is blocked. Both functions are effective bi-directional, i.e. performed during either clockwise or counterclockwise rotation.
  • the ORBDC is basically comprised of three component sets. There is a drawn outer shell 1 of bearing quality steel, which is split to allow expansion of the outer diameter of the shell and the ORBDC. Ramped surfaces are formed on the inner diameter or surface of the outer shell.
  • the inner shell 2 of bearing quality steel with a solid inner diameter for being press-fit onto a shaft.
  • the inner shell has ramped surfaces on the outer diameter or surface thereof.
  • the ramps on the outer shell as well on the inner shell are produced by forming axial direction depressions or grooves in one or both of the shell surfaces in which the below described needles or rollers sit and the inclined walls of those depressions or grooves define the ramps on which the needles or rollers move during operation described below.
  • a plurality of needles or bearing rollers 3 are disposed between the inner and outer shells and are received in the axial direction grooves or recesses formed by the ramped surfaces of each shell.
  • the diameter of the needles or rollers allows them to move into the grooves or recesses.
  • the recesses or grooves in the ramped surfaces of the inner and outer shells are shaped and disposed so that in a neutral position, the inner and outer shell depressions or grooves may be radially aligned.
  • the ORBDC When the ORBDC is in its “neutral” position, that is, no tangential rotational loads are applied to the outer shell, the ramps in the outer and inner shell align, forming grooves or pockets which loosely contain the needles or rollers.
  • the outer shell in this position is in its unstressed, un-deformed state, which is at its smallest outer diameter.
  • the ORBDC functions as an over-running plain bearing and us state is unblocked.
  • the relative tangential load may be applied to the outer shell via an active force, such as a drag band, or a passive force, such as drag from oil shear of the speed gear.
  • an active force such as a drag band
  • a passive force such as drag from oil shear of the speed gear.
  • Design of the ORBDC is key to the present invention.
  • Previously known configurations of the ORBDC either utilize no inner shed (by forming ramps directly on the inner shaft) or utilize an inner shell with no hole for an actuation pin to pass through.
  • the outer shell is instead prevented from moving in relation to the inner shell by a key member which is rotatonially fixed to the shaft and thus to the inner shell. This key member is slid into engagement with a notch in the outer shell via movement along the shaft axis, very much like traditional synchronization components are used to lock gears in manual transmissions.
  • U.S. Pat. No. 6,409,001 details such an arrangement.
  • the invention concerns controlling the application of the relative tangential load. Control of the load application is accomplished via a movable actuation member positioned integral with the timer and outer shells.
  • the ORBDC When the actuation member is in a position to lock both the inner and outer shells in a selected relative angular position, the ORBDC is in neutral and cannot block relative rotation.
  • the actuation member When the actuation member is actuated to allow relative rotational motion of the outer shell with respect to the inner shell, the clutch will block and the gear will locked to the shaft by the clutch.
  • the desired odd or even gear would be blocked via actuation of the appropriate ORBDC. All other corresponding gears (odd or even) would be locked in their neutral position.
  • the opposite gear set (odd or even) would be pre-selected to the appropriate gear and its ORBDC would also be blocked awaiting application of the corresponding main clutch. The remaining gears in this set too would be locked in neutral.
  • Engine power would be transferred through the first selected gear via the first main clutch until the need to shift. At that time, the first and second main clutches would respectively release and clamp, thus transferring power to the second selected gear, which is already pre-selected and locked. At this time, the first gear set would pre-select another gear, and so on.
  • the movable actuation member used to lock and unlock the inner and outer shells in relative angular position can be designed in many configurations. In its simplest form, it is a pin which extends through the ORBDC radially from the inner shell outward through the outer shell. The pin could fit into a matching hole in both inner and outer shells. When the pin is in place, the shells are locked. When the pin is removed from at least one shell, the shells can rotate relative to each other, and the ORBDC will block. As is obvious, depending on the actuation member design, the inner and outer shell design will also need to be adjusted to accommodate.
  • the invention is designed to be used with an actuation member which is positioned within the inner power transmission shaft, as opposed to a member that sides along the axis of the shaft.
  • the ORBDC in one embodiment hereof includes a hole that passes through both the inner and outer shells.
  • the actuation member hereof passes through this hole and either prevents or allows the outer shell to rotate relative to the inner shell. Given that a gear will ride on the outer diameter of the outer shell, the actuation member cannot protrude above this outer diameter. For this reason the outer shell has a recessed step to bring it in closet proximity to the inner shell. This reduces the length of the pin, which protects the pin from interference with the gear and also lowers the forces on the pin.
  • FIG. 1 illustrates a power transmission system in which the present invention is embodied
  • FIG. 2 is a detail of one ORBDC from FIG. 1 ,
  • FIG. 3 is a perspective view of an ORBDC
  • FIG. 4 is a cross-section through the ORBDC of FIG. 3 ;
  • FIG. 5 is a cross-section through one embodiment of the ORBDC
  • FIG. 6 is a cross-section through a second embodiment of an ORBDC
  • FIG. 7 is a perspective view of the ORBDC in FIG. 6 .
  • FIG. 8 is a cross-section along the axis showing a third embodiment of the invention.
  • FIG. 9 is a cross-section of the third embodiment across the axis
  • FIG. 10 is an illustrative perspective view of a fourth embodiment of an ORBDC
  • FIG. 11 is an enlarged cross-sectional view showing the ORBDC of FIG. 10 in the live and locked states.
  • FIG. 12 is a perspective view showing a fifth embodiment of an ORBDC.
  • FIG. 13 shows then ORBDC of FIG. 12 in fee and locked states.
  • FIGS. 3 and 4 show basic elements of an ORBDC in which the invention may be embodied. It includes an outer shell 1 , inner shell 2 and needle rollers 3 between the shells. The outer shell is split at 4 . There may be a notch at the split as described with reference to the embodiment of FIG. 12 .
  • the actuation member is a radially movable pin 11 which is integrated in the inner power transmission shaft 12 .
  • An actuation tube 13 internal to the power shaft has a grooved or cammed surface 16 to actuate the pin 11 to either protrude through both of the inner 14 and outer 15 shells as shown by pin 18 , or to retract as shown by pin 19 and thus free the outer shell to rotate and block the ORBDC. While an inner shell on a shaft is shown, the surface with ramps winch cooperates with the needles may be formed in the shaft itself. Also, the grooves or depressions or ramps may be formed in only one of the shells.
  • the needles or rollers in all embodiments have a diameter so that they can enter a groove or depression and avoid riding a ramp.
  • the actuation member is a rotating pin 21 winch is integrated in the inner power transmission shaft 22 .
  • the pin 21 can be actuated, that is rotated by various arrangements.
  • the preferred design is a rotating drum 23 with cam lugs 24 thereon that contact the bottom 25 of the pin and rotate the pin.
  • the actuation member is a rocker pin 31 which is installed into the ORBDC at a circumferential location of and in place of one of the needle rollers 32 .
  • the rocker pin 31 has a pivot center 33 , a lock tab 34 , an interlock tab 35 , and an engagement tab 36 .
  • a selection drum 37 is rotated to transfer between the ORBDC being in its neutral or locking conditions. When the inner selection drum 37 is rotated so that the respective interlock cam 38 on the drum contacts the interlock tab 35 , the pin 31 pivots so that the lock tab 34 protrudes through the outer shell 39 of the ORBDC, thus allowing the gear to spin freely over the outer shell.
  • the outer shell is instead prevented from moving in relation to the inner shell by a key member (not shown) which is rotationally fixed to the shaft and thus to the inner shell.
  • This key member is slid into engagement with a notch 52 in the outer shell via movement along the shaft axis, very much like traditional synchronization components are used to lock gears in manual transmissions.
  • the actuation member is positioned within the inner power transmission shaft (not shown) and is not a member that slides along the axis of the shaft.
  • the ORBDC in this embodiment hereof includes a hole 6 that passes through both the inner and outer shells.
  • the actuation member hereof (not shown, but from one of the Figures above) passes through the hole 61 and either presents or allows the outer shell to rotate relative to the inner shell. Because a gear (not shown) will ride on the outer diameter of the outer shell, the actuation member cannot protrude above the outer diameter of the outer shell. For this reason, the outer shell has a recessed step 62 to bring it in closer proximity to the inner shell.
  • the ORBDC have both an inner and outer shell to make use of the recessed step outer shell in FIG. 10 .
  • This can also be used if the inner shell is eliminated via directly forming ramps as described above on the inner shaft. In such a case, the step would come in close proximity with the shaft and still allow actuation from within the shaft without interfering with the gear.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Retarders (AREA)
  • Structure Of Transmissions (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
US11/924,030 2006-10-26 2007-10-25 Overrunning bi-directional clutch as gear synchronizer and coupler Abandoned US20080099295A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US11/924,030 US20080099295A1 (en) 2006-10-26 2007-10-25 Overrunning bi-directional clutch as gear synchronizer and coupler
US13/271,114 US8544625B2 (en) 2006-10-26 2011-10-11 Overrunning bi-directional clutch as gear synchronizer and coupler

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US85452806P 2006-10-26 2006-10-26
US87166406P 2006-12-22 2006-12-22
US87665106P 2006-12-22 2006-12-22
US11/924,030 US20080099295A1 (en) 2006-10-26 2007-10-25 Overrunning bi-directional clutch as gear synchronizer and coupler

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US13/271,114 Continuation US8544625B2 (en) 2006-10-26 2011-10-11 Overrunning bi-directional clutch as gear synchronizer and coupler

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US20080099295A1 true US20080099295A1 (en) 2008-05-01

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US11/924,030 Abandoned US20080099295A1 (en) 2006-10-26 2007-10-25 Overrunning bi-directional clutch as gear synchronizer and coupler
US13/271,114 Expired - Fee Related US8544625B2 (en) 2006-10-26 2011-10-11 Overrunning bi-directional clutch as gear synchronizer and coupler

Family Applications After (1)

Application Number Title Priority Date Filing Date
US13/271,114 Expired - Fee Related US8544625B2 (en) 2006-10-26 2011-10-11 Overrunning bi-directional clutch as gear synchronizer and coupler

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US (2) US20080099295A1 (de)
DE (6) DE102007051735A1 (de)
WO (6) WO2008049893A1 (de)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008047685A1 (de) * 2008-09-18 2010-03-25 Schaeffler Kg Freilaufkupplung
DE112010004010A5 (de) 2009-10-12 2012-08-23 Schaeffler Technologies AG & Co. KG Freilaufanordnung, insbesondere für ein cvt -getriebe
DE102013108030A1 (de) 2013-07-26 2015-02-19 Bayram Özcan Lastschaltbare Freilaufkupplung
US20230110808A1 (en) * 2021-10-08 2023-04-13 Schaeffler Technologies AG & Co. KG Rotor disconnect clutch assembly
CN114151467B (zh) * 2021-12-03 2022-09-16 华星传动科技无锡有限公司 一种便于拆卸安装的双向离合器

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3393783A (en) * 1966-11-21 1968-07-23 Ford Motor Co Transversely engaged cam operated friction clutch
US20020029948A1 (en) * 2000-07-07 2002-03-14 Williams Randolph C. On-demand transfer case with integrated sprocket and bi-directional clutch assembly
US6409001B1 (en) * 1997-11-26 2002-06-25 Ker-Train Holdings Ltd Full-complement multi-directional coupling
US6652407B2 (en) * 2001-04-23 2003-11-25 New Venture Gear, Inc. Transfer case shift system for controllable bi-directional overrunning clutch
US20070029152A1 (en) * 2004-01-14 2007-02-08 Joki Mark A Four wheel drive system
US20080099294A1 (en) * 2006-10-26 2008-05-01 Schaeffler Kg Three-mode overrunning bi-directional clutch
US20080098843A1 (en) * 2006-10-26 2008-05-01 Schaeffler Kg Gear selection assembly with nested differentially rotatable tube
US7779978B2 (en) * 2004-11-05 2010-08-24 Koyo Bearings Usa Llc Selectable mode clutch
US7874414B2 (en) * 2006-10-26 2011-01-25 Schaeffler Kg Overrunning bi-directional clutch with controlled locking

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US2259473A (en) * 1939-11-15 1941-10-21 Weskenson Corp Roller clutch
US4987790A (en) * 1987-02-26 1991-01-29 Weismann Peter H Transmission
US5301565A (en) * 1987-02-26 1994-04-12 Weismann Peter H Transmission
US5689998A (en) * 1994-03-31 1997-11-25 The Anchored Corporation Continuous-torque variable-speed transmission
DE19536715C2 (de) * 1995-09-30 1999-11-11 Suhler Fahrzeugwerk Gmbh Schrittschalteinrichtung für ein Schaltgetriebe, insbesondere für Fahrzeuggetriebe
GB9918642D0 (en) * 1999-08-06 1999-10-13 Ricardo Mtc Limited Gearboxes
US6974400B2 (en) 2002-02-05 2005-12-13 American Axle & Manufacturing, Inc. Transfer case with a tri-mode bi-directional clutch assembly
CA2451899A1 (en) 2002-12-10 2004-06-10 Tesma International Inc. A gear coupler with a controllable roller clutch
DE10259931A1 (de) 2002-12-20 2004-07-01 Ina-Schaeffler Kg Kupplungsanordnung
FR2858031B1 (fr) * 2003-07-22 2005-10-14 Skf Ab Dispositif de roue libre, poulie et alternateur equipes d'une roue libre
US20060191763A1 (en) * 2003-10-20 2006-08-31 Joki Mark A Clutching device
US7004875B2 (en) 2004-03-29 2006-02-28 Magna Powertrain, Inc. Torque coupling with tri-mode overrunning clutch assembly
US20050236246A1 (en) * 2004-04-21 2005-10-27 Timken Us Corporation Secondary driven axle control
JP2007507677A (ja) * 2004-09-07 2007-03-29 ティムケン ユーエス コーポレーション モード選択可能クラッチ
US7415905B2 (en) * 2005-01-07 2008-08-26 Gm Global Technology Operations, Inc. Vehicular transmissions utilizing slipper ring clutch control
JP2006316984A (ja) * 2005-04-12 2006-11-24 Kanzaki Kokyukoki Mfg Co Ltd 双方向クラッチ

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3393783A (en) * 1966-11-21 1968-07-23 Ford Motor Co Transversely engaged cam operated friction clutch
US6409001B1 (en) * 1997-11-26 2002-06-25 Ker-Train Holdings Ltd Full-complement multi-directional coupling
US20020029948A1 (en) * 2000-07-07 2002-03-14 Williams Randolph C. On-demand transfer case with integrated sprocket and bi-directional clutch assembly
US6652407B2 (en) * 2001-04-23 2003-11-25 New Venture Gear, Inc. Transfer case shift system for controllable bi-directional overrunning clutch
US20070029152A1 (en) * 2004-01-14 2007-02-08 Joki Mark A Four wheel drive system
US7779978B2 (en) * 2004-11-05 2010-08-24 Koyo Bearings Usa Llc Selectable mode clutch
US20080099294A1 (en) * 2006-10-26 2008-05-01 Schaeffler Kg Three-mode overrunning bi-directional clutch
US20080098843A1 (en) * 2006-10-26 2008-05-01 Schaeffler Kg Gear selection assembly with nested differentially rotatable tube
US7874414B2 (en) * 2006-10-26 2011-01-25 Schaeffler Kg Overrunning bi-directional clutch with controlled locking

Also Published As

Publication number Publication date
DE102007051734A1 (de) 2008-04-30
WO2008049892A3 (de) 2008-07-10
WO2008049893A1 (de) 2008-05-02
WO2008049894A1 (de) 2008-05-02
DE102007051732A1 (de) 2008-04-30
DE102007051738A1 (de) 2008-11-06
DE102007051736A1 (de) 2008-04-30
WO2008049892A2 (de) 2008-05-02
US8544625B2 (en) 2013-10-01
US20120043174A1 (en) 2012-02-23
DE102007051733A1 (de) 2008-06-26
WO2008049896A1 (de) 2008-05-02
WO2008049895A1 (de) 2008-05-02
WO2008049891A1 (de) 2008-05-02
DE102007051735A1 (de) 2008-04-30

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Owner name: SCHAEFFLER KG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:LEE, BRIAN;HEMPHILL, JEFFREY;REEL/FRAME:020015/0787;SIGNING DATES FROM 20071015 TO 20071025

STCB Information on status: application discontinuation

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