WO1993000520A1 - Roue libre amelioree pour reacteur de convertisseur de couple - Google Patents

Roue libre amelioree pour reacteur de convertisseur de couple Download PDF

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Publication number
WO1993000520A1
WO1993000520A1 PCT/US1992/005301 US9205301W WO9300520A1 WO 1993000520 A1 WO1993000520 A1 WO 1993000520A1 US 9205301 W US9205301 W US 9205301W WO 9300520 A1 WO9300520 A1 WO 9300520A1
Authority
WO
WIPO (PCT)
Prior art keywords
reactor
rollers
race
outer race
clutch
Prior art date
Application number
PCT/US1992/005301
Other languages
English (en)
Inventor
Rudolf Richard Castens
Original Assignee
Hybo Science, Inc.
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 Hybo Science, Inc. filed Critical Hybo Science, Inc.
Publication of WO1993000520A1 publication Critical patent/WO1993000520A1/fr

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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
    • 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
    • F16D41/061—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by movement having an axial component
    • 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
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F16H41/28—Details with respect to manufacture, e.g. blade attachment
    • 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
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F16H2041/246—Details relating to one way clutch of the stator

Definitions

  • the instant invention relates to freewheels and, i particular, relates to a novel unidirectional clutch/bearin assembly adapted to be used in connection with an automobile torqu converter and which accommodates loads in the axial, radial an circumferential directions.
  • the typical three-element single-stage converter i comprised of an impeller, driven by the output shaft of the engine fluidly coupled to a turbine.
  • the turbine in turn is mechanicall connected to the transmission input shaft.
  • the converter als employs a small, vaned, wheel known as the reactor or stator having its vanes positioned between the impeller and the turbine and adapted to direct hydraulic fluid deflected off of the turbin blades along a more favorable path back to the impeller blades thereby providing a more efficient energy transfer with respect t the fluid coupling generally.
  • FIG. 1A illustrates, in cross section, the genera diagram of a torque converter 10 which is comprised of a flywhee 12 connected to an impeller 14.
  • the impeller has connected to it curved outer shell a plurality of specially curved impeller vane 16 adapted to propel hydraulic fluid against turbine vanes 18 upo rotation of flywheel 12.
  • Turbine blades 18 are connected to turbin shell 18' which in turn is rigidly connected to transmission inpu shaft 19. Fluid striking turbine vanes 18, by natural physic forces, is deflected generally backwardly so that it proceeds circulate back into the path of impeller blades 16 whereupon it again propelled at turbine blades 18. This process is repeat while torque is being transferred between impeller 14 and turbi 18'.
  • a device known as a reactor or ⁇ tator 20 has come in widespread use and has for its purpose the efficient re-directi of the hydraulic fluid from the impeller blades 18 through preferred path via reactor vanes 22 into smooth re-engagement wi impeller blades 16.
  • Vanes 22 of the reactor are shaped in a fo which approximates an average ideal transmission fluid fl direction for the circulating fluid.
  • the reactor 20 wi perform its function only if it is permitted to rotate about t axis of shaft 19 ir. one direction but to lock up, or transm torque, in the opposite direction.
  • the freewheel 23, shown in Fig. IB, upon which t reactor rotates, must be a unidirectional clutch which transmi torque when acted upon by a force in one direction, as shown arrows F in Fig. 2A, yet which permits the reactor 20 to free whe in the opposite direction.
  • the inner race of freewheel 23 connected to a stationary member 30 disposed in concentr relationship about shaft 19 and fixed with respect to the automat transmission casing T.
  • the reactor vanes 22 on create a drag on the rotational motion of the hydraulic flu rotating with the impeller 16 and turbine 18. Therefore, it desirable for the reactor to be permitted to spin freely when act upon by forces directed opposite that of the arrows F shown in Fi 2A.
  • the reactor is of a non-streamline inefficient shape due to the oversized traditional freewheel 23. a result, the "floor" 21 of the reactor presents a sha obstruction in the flow path of fluid returning from turbine blad 18 to impeller blades 16 which diminishes performance of the torq converter substantially. Further, it has heretofore been necessa to make the actual diameter of the overall torque convert unnecessarily large to provide clearance for convention freewheels.
  • the ramp roller clutch does not resi force in the axial direction and hence requires the use of bul axial thrust elements 26. Reducing the size of the free wheel a related elements will permit a reduction in size of the torq converter, and hence transmission overall.
  • the freewhee presently in use do not act as a true bearing in the freewheeli mode because the rollers thereof are not permitted to spin relati to the outer race. It is desired, therefore, to provide a unidirectiona clutch member which acts as a free wheel and a bearing i association with a torque converter reactor which provides lockin action against one direction of rotation of the reactor and lo friction rotation thereof in the opposite direction while utilizin a minimum of space and material and providing resistance agains axial forces.
  • an improved unidirectiona clutch or freewheel adapted to rotatably support the reactor of torque converter so as to allow the reactor, in one direction, t spin freely yet prevent rotational movement thereof in the opposit direction, while also providing axial thrust resistance.
  • the nove clutch is comprised generally of four elements: an inner rac member rigidly connected to the transmission housing; an outer rac surrounding the inner race and defining therewith confronting rac surfaces and an volume therebetween, the outer race being rigidl connected to the reactor; a plurality of cylindrical thrus transmitting rollers disposed in said annular volume and incline with respect to radial planes; and annular bearing means associate with one end of the clutch to permit slidable rotation of sai rollers relative to an annular shoulder connected to one of th races.
  • the clutch has a first, larger diameter, end and second, smaller diameter end, between which the inner and oute race surfaces curve according to a special relationship, creatin a ramp surface against which the rollers jam in the locki direction.
  • the floor of the reactor may be contoured allow the torque transmitting fluid within the converter to trav smoothly from the turbine side to the impeller side of t converter without interruption.
  • Previous free wheel technology i limited to impeded flow of fluid within the converter from t turbine to the impeller due to the non- uniformity of the floor o the reactor caused by the relatively large free wheels used in th prior art.
  • my invention by occupying far less space permits the reactor floor to be contoured to coincide with th overall interior of the torque converter and to thereby improve th performance thereof.
  • the traditional (prior art freewheel such as the ramp roller shown in Fig.
  • IB does not resi axial loading, additional axial thrust bearing elements must incorporated into the torque converter presently used, increasi the weight thereof and space utilized.
  • the instant invention employing a freewheel of the hyperboloidal type which has slopi race surfaces, resists axial loading without the use of seconda axial thrust components.
  • the needle rollers 32 us in the traditional ramp roller freewheel DO NOT spin in place the freewheel mode but actually slide along the inner race.
  • the needle rollers are not constrained wi respect to either the inner or outer race during the freewheel mo and hence the tendency of the races to wear is distributed even about both inner and outer race surfaces.
  • It is a principal object of the instant invention provide an extremely compact and reliable unidirectional axi thrust bearing and freewheel which combines a one-way clutch wi axial thrust bearing features required of a torque converter fr wheel. It is another object of the instant invention to enhan the free wheeling capacity of a torque converter reactor replacing the ramp roller type free wheel with a hyperboloid unidirectional clutch. It is a still further object of the instant invention increase the efficiency of a torque converter by utilizing hyperboloidal-type freewheel which occupies less space than prio art technology yet which transfers the same magnitude of torq thereof.
  • Fig. 1A shows a cross sectional view of a standard torq converter utilizing a typical ramp roller clutch known in the ar
  • Fig. IB shows a plan view of a typical ramp roller clut as shown in Fig. 1A.
  • Fig. 1C is a plan view of a hyperboloidal-type clutc used with the present invention shown side by side for compariso purposes with the traditional ramp roller freewheel known in t prior art.
  • Fig. 2 is a partial cut away perspective view of typical torque converter and transmission casing arrangemen employing a prior art freewheel.
  • Fig. 2B is a partial cut away perspective view of typical torque converter and transmission casing arrangemen employing my uni-directional freewheel/bearing.
  • Fig. 2C is an enlarged view of a portion of Fig. 2B.
  • Fig. 3 is an exploded perspective view of the pair o clutches used in the preferred embodiment of the present invention
  • Fig. 4 is an elevational view of the uni-directiona clutch used in the present invention with the outer race remove for illustration purposes.
  • Fig. 5 is a cross section of a torque converter employi a simplified embodiment of the unidirectional clutch in associati with a torque converter reactor.
  • Fig. 6 shows a cross sectional elevation of t embodiment of my invention shown in Figs. 2B, and 3 wherein a pa of my unidirectional clutches of the hyperboloidal-type a employed in association with a torque converter reactor.
  • Fig. 1A a shows a typic torque converter in cross sectional elevation comprised of a f wheel 12 mechanically connected to an impeller 14 via interconnect member such as member 13.
  • Integrally connected impeller 14 are a plurality of vanes 16 spaced equally about t dish-shaped body of impeller 14 adapted to transfer kinetic ener from the rotational movement of the output shaft 11 of a moti source (not shown) such as an automobile internal combustion engi to the input shaft 19 of an automatic transmission.
  • Fly wheel together with interconnecting member 13 and impeller member 14 fo a fluid tight partial housing for hydraulic fluid.
  • Turbine vanes are connected to turbine member 18' and are impacted upon hydraulic fluid propelled by motion of impeller vanes 16, causi turbine 18' to move and to consequently cause torque convert output shaft 19, to which it is rigidly affixed, to rotate.
  • React or stator 20 has specially curved vanes 22 spaced thereabout and positioned generally in the fluid return path between vanes 18 a 16.
  • Reactor 20 is supported, in Figs. 1A and 2A, by a ramp roll freewheel 23 commonly used in the art. Such a freewheel is shown i Fig. IB.
  • Ramp roller freewheel 23 has an outer race member 2 rigidly affixed to reactor 20 and an inner race member 28 rigidl affixed via splines 29 to stationary member 30, which is fixe relative to transmission casing T.
  • ramp roller 2 transmits torque from outer race member 26 to inner race member 2 when the outer race member 26 is acted upon by a force tending t rotate it in the direction of arrow J in Fig. IB relative t stationary inner race member 28.
  • outer race member 2 freewheels with respect to inner race member 28 when outer rac member 26 is acted upon by a force tending to rotate it in th direction of arrow S.
  • the floor 21 o reactor 20 be manufactured generally flat to provide clearance fo the bulky ramp roller clutch 24, hence decreasing performance of the torque converter by presenting a flow obstruction in the hydraulic fluid return path between vanes 18 and 16.
  • the instant invention the preferred embodiment of which is shown in Figs. 2B, 3, 4 and 6, overcomes the disadvantages inherent in traditional free wheel technology such as that shown in Figs. 1A, IB and 2A by providing a pair of extremely compact and efficient unidirectional clutches 38 each comprised of an inner race member 40 defining an inner race surface 42 and an outer race member 60 defining an outer race surface 62.
  • Said outer race member 60 is integrally connected to reactor 20 by any expedient known in the art, such as by splines, molding, welding, casting and the like.
  • a plurality of thrust transmitting rollers 50 are disposed the annular volume 49 formed by and between the confronti surfaces 42 and 62 of the inner and outer race members 40 and 6 respectively.
  • Said rollers 50 of which there must be at lea three to obtain static and dynamic deter inance, are all similar inclined with respect to radial planes.
  • the confronting inner and outer race surfaces 42 and are surfaces of revolution about the axis of rotation of t clutch.
  • the inner race surface or surface of revolution 42 contac each of said rollers along a first line of contact, said first li of contact being the generating line for said first surface revolution.
  • Said outer race or second surface of revolution 6 contacts each of said rollers along a second line of contact, sai second line of contact being the generating line of said secon surface of revolution.
  • the clutch has a first end 44 and a secon end 46, said first end having a larger diameter than said secon end.
  • Said rollers 50 each have a first end 54 and second end 5 corresponding to the first end 44 and the second end 46 of th clutch 38, said first end 54 of said rollers 50 and said first en 44 of said clutch meeting at an interface.
  • bearin means such as annular ring 70 is disposed at the interface of sai rollers 50 with said first end 44 to permit slidable movemen therebetween in a first direction while supporting the rollers 5 axially thereof.
  • the rolling axes of rollers 5 constitute generators of true hyperboloids. Therefore, th generating lines of the inner and outer race surfaces approac generators of a true hyperboloid as the radius of the roller approaches zero.
  • the bearing mean at the interface between the rollers and at least one of the firs and second members is an annular support ring 70 positioned on an supported by an annular shoulder 72 integrally connected to a least one of the members 40 or 60 beneath the rollers at th position of contact, or interface, between the rollers 50 and rac surfaces corresponding to the larger diameter end 44 of eac member.
  • the annular support member 70 may be fabricated of self-lubricating material and is thereby capable of slidabl rotation relative to at least one of the members so as to freel support the rollers rotatably relative to said at least one member.
  • the supported end portions of the rollers 58 are arcuately or spherically shaped and the annular ring member 70 configured to define a plurality of correspondingly shaped depressions or cavities 64 on the roller supporting surface so as to receive the end portions of the rollers in nestled relation and thereby maintain the rollers in predetermined spaced relation corresponding to the distance between the cavities 64.
  • the race surfaces 42 and 62 are capable of thrust transmitting contact with the rollers 50 so as to transmit torque between the members 40 and 60 in dependence upon the number and diameter of the rollers 50, the length of the rollers and the angle of inclination between the rollers with respect to radial planes. It has been found that the use of a pair of hyperboloid unidirectional clutches disclosed herein, the first referred to the State I or first stage and the second referred as the Stage or second stage, would provide enhanced performance over a sing such clutch as twice the torque transmitting capacity is ma available.
  • the clutches 38 transmit axial loading a hence perform the critical function of acting as axial thru bearings, in addition to the capacity of the hyperboloidal clut to act as a true roller bearing in the freewheeling stat Therefore, using two hyperboloidal clutches between the reactor and stationary shaft 30 provides a unidirectional clutch which ac as a true roller bearing when freewheeling, acts as an axial thru bearing to withstand loading along the axis of rotation R of t clutch, and which occupies a minimum of space and is extreme lightweight when compared to prior art technology.
  • Biasing means such as coil spring 65 or Bellevil spring or wave washer 90, shown in Figure 6, or the like disposed between Stage I and Stage II of clutches 38 so as to bi the respective inner race members 40 thereof away from each othe
  • the inner and outer ra members are maintained in proper alignment should wear occu Retaining means such as C-clips 92, 94 may be used to limit t positions of the Stage I and Stage II inner race members where t inner race members are axially movable on shaft 30.
  • the ra members may be machined out of solid material or may be stamped o of thin sheet material as shown for outer race member 60.
  • reactor 20 is rigidly connected to outer race membe 60 in any convenient manner.
  • Figs. 4 and 5 show a simplified version of the inventio shown in Figs. 2B and 2C using only one unidirectional clutch, where inner race member 40 is rigidly connected to splined inne race element 30, which in turn is rigidly connected to transmissio casing T.
  • Outer race member 60 is located in surroundin relationship to inner race member 40 so as to position outer rac surface 62 as detailed in Figure 3, confronting relationship with inner race surface 42 and thus define an annular volume therebetween.
  • a plurality of thrust transmitting cylindrical rollers 50 are disposed within said annular volume, all being inclined at an angle with respect to radial planes.
  • Annular thrust ring 70 is slidably positioned between first ends 54 of said rollers and an annular shoulder member 72 connected to inner race member 40.
  • An additional or secondary axial thrust bearing means may be employed when only one hyperboloidal unidirectional clutch is utilized with reactor 20.
  • Such secondary axial thrust bearing means may be comprised of a plurality of roller bearings 98 disposed about the periphery of inner ball bearing race member 96 and within outer ball bearing race member 100.
  • a secondary or auxiliary axial thrust bearing may be desired f certain applications.
  • the secondary axial thrust bearing mea disclosed herein is exemplary. However, it is contemplated th alternative forms of apparatus to resist axial loading are with the scope of the invention.
  • a biasing means such as wave washer 90 may also employed in association with a retaining clip 92 to maintain inn race member 40 in proper alignment with respect to outer ra member 60.
  • a second retaining means such as C-clip 94 may be us to limit the distance to which inner race member 40 may move shaft 30.
  • Annular thrust ri 70 may be solid, in which case the needle rollers actually sli over the top surface thereof, or, alternatively, the annular thru ring 70 used with the first embodiment of this invention may used having cavities 64, Figure 3, into which ends 54 of rollers are inserted.
  • the clutch transmits torq in one direction while in the other there is simply a free-wheeli action, which direction is determined by whether the rollers a located with right hand or left hand skew.
  • the rollers 50 Figure 4 are oriented with a right hand skew. Engagement in the jamming direction is instantaneous direct, and virtually soundless, and is positive, i.e.
  • FIG. 6 Depicted in Figure 6 is a second embodiment of th instant invention wherein a pair of my unidirectional clutches ar used as a freewheel, roller and axial bearing for a torqu converter reactor but wherein a first stage clutch resists axia loading from left to right and second stage clutch resists fro right to left.
  • FIG. 7 Depicted in Figure 7 is a third embodiment of the instan invention wherein a pair of my unidirectional clutches are used a a freewheel, roller and axial bearing for a torque converte reactor but wherein the diameter of the stage 1 clutch about th axis of rotation R of the reactor, torque converter and clutches i greater than the diameter of the stage 2 clutch about axis R Because the oil flow direction in a torque converter chan ⁇ e frequently, to resist severe transmission fluid thrust forces which may at times be in the nature of shock waves, increasing th diameter of the stage 1 clutch, or alternatively, the stage clutch if desired, provides additional axial thrust bear capacity as well as additional torque transmission capacity in lock up mode.
  • Increasing the diameter of one of my clutc permits the use of additional rollers 50, which increases amount of surface area contact between the rollers 50 and the in and outer race surfaces 42 and 62. It is contemplated that more than two such clutches be used in heavy duty applications such as trucks, buses, e Further, the size of the clutches used is only limited by the s of the transmission components involved. Additionally, the in race member 40 may be machined directly out of stationary shaft and hence be integrally connected thereto. If desired, clutches may be used in such an embodiment where both the in races of the stage 1 and stage 2 clutches are machined direc from stationary member 30.
  • Patent Application Serial No 07/418,795 which is incorporated by reference herein as thoug fully set forth herein, the axial thrust resisting feature thereo is used to the greatest benefit.
  • a first stage clutch 38 resist axial loading from left toward right in Fig. 6, while second stag clutch 38' resists axial loading from right to left in that Figure.
  • the instant invention has been shown and described herei in what is considered to be the most practical and preferre embodiment. It is recognized, however, that departures may be mad therefrom within the scope of the invention and that obviou modifications will occur to a person skilled in the art.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

Un embrayage unidirectionnel ou roue libre améliorée est adapté pour être utilisé dans un convertisseur de couple aux fins de support rotatif du réacteur (20) dans celui-ci. La présente invention concerne un embrayage unidirectionnel du type hyperboloïde ayant des surfaces (40, 60) de voie de roulement dans lesquelles se trouvent des rouleaux de transmission de poussée (50) inclinés par rapport aux plans radiaux afin de permettre la rotation dans un seul sens. Des surfaces multiples de voie de roulement ou étages (I, II) resistent à la charge axiale et des moyens (90) sont prévus pour solliciter l'élément de voie de roulement interne vers l'élément de voie de roulement externe afin de maintenir un bon alignement.
PCT/US1992/005301 1991-06-20 1992-06-22 Roue libre amelioree pour reacteur de convertisseur de couple WO1993000520A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US71821891A 1991-06-20 1991-06-20
US718,218 1991-06-20

Publications (1)

Publication Number Publication Date
WO1993000520A1 true WO1993000520A1 (fr) 1993-01-07

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PCT/US1992/005301 WO1993000520A1 (fr) 1991-06-20 1992-06-22 Roue libre amelioree pour reacteur de convertisseur de couple

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WO (1) WO1993000520A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0748946A1 (fr) * 1995-06-12 1996-12-18 Ebara Corporation Appareil de transmission de puissance

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1670197A (en) * 1924-03-24 1928-05-15 Humfrey Sandberg Co Ltd Free-wheel ratchet device
US1929782A (en) * 1931-12-09 1933-10-10 New Departure Mfg Co Clutch
US2710504A (en) * 1952-06-06 1955-06-14 Adiel Y Dodge Toroidal chamber type hydraulic torque converter
US3147595A (en) * 1964-03-16 1964-09-08 Ford Motor Co Hydrokinetic power transmission mechanism with stator speed sensitive pressure signal
US3163988A (en) * 1963-06-13 1965-01-05 Ford Motor Co Multiple element hydrokinetic torque converter
US3557921A (en) * 1968-03-29 1971-01-26 Koyo Seiko Co One-way clutch
US4441315A (en) * 1981-01-27 1984-04-10 Valeo Reaction assembly for a torque converter and a torque converter comprising such a reaction assembly

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1670197A (en) * 1924-03-24 1928-05-15 Humfrey Sandberg Co Ltd Free-wheel ratchet device
US1929782A (en) * 1931-12-09 1933-10-10 New Departure Mfg Co Clutch
US2710504A (en) * 1952-06-06 1955-06-14 Adiel Y Dodge Toroidal chamber type hydraulic torque converter
US3163988A (en) * 1963-06-13 1965-01-05 Ford Motor Co Multiple element hydrokinetic torque converter
US3147595A (en) * 1964-03-16 1964-09-08 Ford Motor Co Hydrokinetic power transmission mechanism with stator speed sensitive pressure signal
US3557921A (en) * 1968-03-29 1971-01-26 Koyo Seiko Co One-way clutch
US4441315A (en) * 1981-01-27 1984-04-10 Valeo Reaction assembly for a torque converter and a torque converter comprising such a reaction assembly

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0748946A1 (fr) * 1995-06-12 1996-12-18 Ebara Corporation Appareil de transmission de puissance
US5850897A (en) * 1995-06-12 1998-12-22 Ebara Corporation Power transmitting apparatus
EP0893614A3 (fr) * 1995-06-12 1999-03-10 Ebara Corporation Appareil de transmission de puissance

Also Published As

Publication number Publication date
TW221045B (fr) 1994-02-11

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