WO1981003366A1 - Corps de transmission de couple pour des transmissions de traction et procede de developpement de force de friction normale - Google Patents

Corps de transmission de couple pour des transmissions de traction et procede de developpement de force de friction normale Download PDF

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Publication number
WO1981003366A1
WO1981003366A1 PCT/US1980/000583 US8000583W WO8103366A1 WO 1981003366 A1 WO1981003366 A1 WO 1981003366A1 US 8000583 W US8000583 W US 8000583W WO 8103366 A1 WO8103366 A1 WO 8103366A1
Authority
WO
WIPO (PCT)
Prior art keywords
axis
beta
axes
alpha
rolling surfaces
Prior art date
Application number
PCT/US1980/000583
Other languages
English (en)
Inventor
Y Kemper
Original Assignee
Vadetec Corp
Y Kemper
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
Priority to AU67075/81A priority Critical patent/AU537135B2/en
Application filed by Vadetec Corp, Y Kemper filed Critical Vadetec Corp
Priority to GB8138446A priority patent/GB2087009B/en
Priority to EP19810900275 priority patent/EP0052603A4/fr
Priority to JP81500493A priority patent/JPS57500892A/ja
Priority to DE803050385T priority patent/DE3050385A1/de
Priority to PCT/US1980/000583 priority patent/WO1981003366A1/fr
Priority to CA000377736A priority patent/CA1149642A/fr
Priority to IT67663/81A priority patent/IT1144717B/it
Publication of WO1981003366A1 publication Critical patent/WO1981003366A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
    • F16H15/50—Gearings providing a continuous range of gear ratios
    • 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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/16—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a conical friction surface

Definitions

  • This invention relates to continuously variable traction drive transmissions and more particularly, it concerns improvements in torque transmitting bodies for such transmissions as well as in a method and structure for forcing complementary rolling surfaces incorporated in such transmissions into frictional torque transmitting engagement with each other.
  • alpha body identifies one of the three working bodies which is concentric with the primary or first transmission axis
  • the .term “beta body” identifies another of the three working bodies which is supported by or from the alpha body to be concentric with a second transmission axis which is inclined with respect to and intersects the first or primary axis
  • the term “omega body” identifies the last of the three working bodies which is concentric with the first axis and which is rotatable or not rotatable independently in relation to the alpha body.
  • the biconical body in continuously variable transmissions of the general class represented by the aforementioned U.S. patents is an integral or one-piece member supported at opposite ends by radial bearings.
  • the bearings do not restrict axial movement of the biconical body and preferably provide also for freedom of pivotal motion spherically about the respecti centers of bearing support.
  • the biconical body is used as the nutatable beta body in transmissions of the class described, normal force components by which the rolling or traction surfaces on the biconical body are pressed into engagement with complementing rolling or traction surfaces of revolution of the omega body, which complementing surfaces are concentric with an axis inclined with respect to and intersecting the axis of the biconical body, one of the two bearings in which the biconical body is journalled is carried from the alpha body by an eccentric mechanism which operates to convert torque acting between the alpha body and the biconical beta body into a thrusting force in a radial plane perpendicular to the axis of the beta body.
  • the thrusting force is oppose by a reaction at the traction surfaces of the omega body (or rings) .
  • the reaction force results in an axial force component at one point of rolling friction contact which is opposed by an equal axial force at a second point of rolling friction contact between the biconical beta body and the omega body.
  • the traction surfaces on the respective beta and omega bodies are urged together at two points of contact under equal normal force loading even though the original thrusting force is applied only at one end of the beta body.
  • the arrangement of the normal force developing means enables the traction surfaces on the respective beta and omega bodies to be withdrawn from contact with each other.
  • a primary object of the present invention is, therefore, the provision of an unique one-piece biconical body for transmissions of the class described together with an unique normal force developing mechanism and method by which traction surfaces on the biconical body are retained in rolling friction engagement with a complementing body at two diametrically opposite points of rolling friction contact.
  • FIG. 1 is a longitudinal cross-sectional view through a transmission embodiment incorporating the present invention
  • Fig. 2 is an enlarged fragmentary cross-section on line 2-2 of Fig. 1;
  • Fig. 3 is a schematic side elevation illustrating force components developed in accordance with the present invention
  • Figs. 4 and 5 are schematic diagrams depicting an operational characteristic of the invention.
  • a biconical torque transmitting or beta body is shown incorporated in a continuously variable transmission unit having a frame 12, an input shaft 14 and an output shaft 16.
  • a continuously variable transmission unit having a frame 12, an input shaft 14 and an output shaft 16.
  • the input shaft 14 is connected as an integral shaft extension with an alpha body 18 supported in the frame 12 by bearings 20 and 22 for rotation about a first axis 24.
  • the beta body 10 in turn, is supported from the alpha body 18 by bearings 26 and 28 to be rotatable on a second axis 30 inclined with respect to and intersecting the first axis 24 at a point S of axes intersection.
  • Supported by and coupled against rotation with respect to the frame 12 are a pair of omega rings 32 and 34 which are capable of axial adjustment toward and away • from the point S of axes intersection.
  • the rings 32 and 34 are coupled through the frame 12 as a single torque body and as such, constitute the omega body of the transmission shown.
  • axial adjustment of the omega rings.32 and.34 is effected by one or more opposit pitched screws 36 rotatable by an external control (not shown) through gears 38 and 40 which are rotatable on axes fixed with respect to the frame 12.
  • An additional control gear 42 rotatable with respect to the frame 12, is shown and in practice is used to synchronize rotation of the gear 40 with corresponding gears for additional sets of double pitched screws (not shown) .
  • a pinion gear 44 connected 0 directly to the biconical beta body 10, meshes with a ring gear ⁇ 6 coupled directly with the output shaft 16. .. , - Consistent with the several transmission embodimen
  • the biconical beta body 10 in the illustrated embodiment defines a pair of 5 external conical surfaces 48 and 50 to engage complementing internal traction surfaces 51 and 52 on the omega rings 32 and 34 at two diametrically opposite points of contact Pi and P2.
  • the rotational 0 speed of the output shaft 16 is the product of both rotation of the alpha body 18 on the first axis 24, causing orbital or planetary movement of the pinion gear 44, and rotation of the pinion gear with the biconical beta body 10 on the axis o
  • the biconical member 10 undergoes a nutational movement as a result of its being supported' on the second axis 30 by the alpha body 18.
  • the biconical body 10 may be concentric with the first axis 24 as the omega body and coupled directly with an output shaft whereas the rings 32 and 34 are concentric with the second axis 30 as the beta body and, as such, carried in nutation by the equivalent of the alpha body 18.
  • the structure and function of the biconical body 10 is equally applicable to either form of transmission in this general class.
  • the biconical body 10 is an integral or one-piece structure shaped externally to provide the frusto-conical traction surfaces 48 and 50 and having axially extending hub formations 54 and 56 at opposite ends.
  • the body 10 is hollow for reduced weight and to facilitate cooling.
  • both hubs 54 and 56 are also hollow to provide fluid communication throughout the length of the body 10.
  • the bearings 26 and 28 by which the body 10 is supported from the alpha body 18 are preferably hydrodynamic bearings supplied with lubrication by porting 58 and 60 within the .alpha body 18.
  • Each of the bearings 26 and 28 includes an internal bushing or sleeve 62 on the interior of a spherical bearing pad 64.
  • Each of the hubs 54 and 56 is, moreover, of a length greater than the length of the bushings 62 so that in the absence of any other restraint, the body 10 will be permitted sliding motion to a limited extent along the second axis 30.
  • the spherical bearing pads 64 will, moreover, provide- a similar freedom from restraint against universal pivotal movement of either hub 54 or 56 about the spherical center of the pads 64. It will be appreciated, therefore, that while the bearings 26 and 28 support the beta body 10 for rotation relative to the alpha body 18, the body 10 is supported with freedom from axial restraint by the bearings along the second axis.30.
  • the bearing 26 at one end of the beta body 10 is carried from the alpha body 18 by an eccentric member 66 having a flanged ring portion 68 to receive the spherical bearing pad 64 and a semicylindrical lobe-like portion 70.
  • the eccentric member 66 fits within the a recess 72 in the alpha body which is shaped to define a semicylindrical bearing surface 74 which complements the circular peripheral portion 76 of the lobe-like formation 70.
  • Both of the surfaces 74 and 76 are concentric with a point or axis 78 which is eccentric with respect to the first or primary transmission axis 24 on which the alpha body 18 is rotatable.
  • the point or axis 78 is offset from a plane 80 containing both the first axis 24 and the second axis 30 by a distance d and in a direction from which torque is transmitted between the alpha body 18 and the. beta body 10.
  • the point 78 is oriented with respect to the first axis 24 as if the alpha body 18 were driven in a clockwise direction of rotation in Fig. 2 or in a direction tending to move the point 78 toward the plane 80.
  • the eccentric member 66 is positioned in the alpha body recess 72 to be located diametrically between a yieldable preload plunger 82 and a hydraulic retraction plunger 84.
  • the preload plunger 82 is retained in engagement with the member 66 under the bias of a compression spring 86 whereas the plunger 84 is received in a chamber 88 to which hydraulic fluid may be introduced under pressure through porting 90.
  • the thrusting force between the alpha body 18 and the beta body 10 is through only the bearing 26 or at one end of the beta body, this initial thrusting force is resolved into substantially equal normal foce loading components at the points Pi and P2 of rolling friction contact.
  • the resolution of forces acting to retain the beta body rolling surfaces in engagement with those of the omega rings 32 and 34 may be appreciated by reference to Fig. 3 of the drawings.
  • the initial thrusting force F is in the direction of the arrow so designated and, as such, is perpendicular to the second axis 30.
  • the thrusting force is opposed by a reaction force

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

Entrainement de traction par nutation dans lequel des surfaces exterieures de roulement dans un corps monobloc biconique (10) sont retenues contre des surfaces (51, 52) interieures d'anneaux espacees axialement a des points de contact diametralement opposes par un mecanisme agissant entre un corps (18) pouvant tourner autour de l'axe des surfaces d'anneaux ou d'un premier axe (24) et portant le corps biconique (10) sur un deuxieme axe (30) incline par rapport au premier axe et coupant celui-ci en un point (S) d'intersection des axes situe a mi-chemin entre les surfaces d'anneaux (51, 52) et les points de contact. Le mecanisme comprend un organe pivotant (66) possedant un point d'appui (78) excentrique par rapport au premier axe (24) ou deplace par rapport a un plan contenant le premier (24) et le deuxieme (30) axes de maniere telle qu'une reaction de couple a la rotation du corps de transport (18) par le corps biconique (10) se traduise par une force qui tend a augmenter l'angle entre le premier (24) et le deuxieme (30) axes. Un dispositif de chargement prealable (82) servant a faire osciller l'organe pivotant (66) dans une direction produit un decentrage de charge prealable des surfaces de roulement l'une contre l'autre alors qu'un dispositif de decharge (84) servant a faire osciller l'organe pivotant dans la direction opposee produit une annulation de la force de friction normale entre les surfaces de roulement engagees.
PCT/US1980/000583 1980-05-19 1980-05-19 Corps de transmission de couple pour des transmissions de traction et procede de developpement de force de friction normale WO1981003366A1 (fr)

Priority Applications (8)

Application Number Priority Date Filing Date Title
AU67075/81A AU537135B2 (en) 1980-05-19 1980-05-10 Torque transmitting body for traction drive transmissions andnormal friction force developing method
GB8138446A GB2087009B (en) 1980-05-19 1980-05-19 Torque transmitting body for traction drive transmissions and normal friction force developing method
EP19810900275 EP0052603A4 (fr) 1980-05-19 1980-05-19 Corps de transmission de couple pour des transmission de traction et procede de developpement de force de friction normale.
JP81500493A JPS57500892A (fr) 1980-05-19 1980-05-19
DE803050385T DE3050385A1 (de) 1980-05-19 1980-05-19 Torque transmitting body for traction drive transmissions and normal friction force developing method
PCT/US1980/000583 WO1981003366A1 (fr) 1980-05-19 1980-05-19 Corps de transmission de couple pour des transmissions de traction et procede de developpement de force de friction normale
CA000377736A CA1149642A (fr) 1980-05-19 1981-05-15 Organe transmetteur de couple pour transmission motrices, et methode pour engendrer un effort de friction normal
IT67663/81A IT1144717B (it) 1980-05-19 1981-05-18 Trasmissione a variazione continua di velocita

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
WOUS80/00583 1980-05-19
PCT/US1980/000583 WO1981003366A1 (fr) 1980-05-19 1980-05-19 Corps de transmission de couple pour des transmissions de traction et procede de developpement de force de friction normale

Publications (1)

Publication Number Publication Date
WO1981003366A1 true WO1981003366A1 (fr) 1981-11-26

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ID=22154352

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1980/000583 WO1981003366A1 (fr) 1980-05-19 1980-05-19 Corps de transmission de couple pour des transmissions de traction et procede de developpement de force de friction normale

Country Status (7)

Country Link
EP (1) EP0052603A4 (fr)
JP (1) JPS57500892A (fr)
CA (1) CA1149642A (fr)
DE (1) DE3050385A1 (fr)
GB (1) GB2087009B (fr)
IT (1) IT1144717B (fr)
WO (1) WO1981003366A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4170200A1 (fr) * 2021-10-20 2023-04-26 Suzuki Motor Corporation Transmission à variation continue

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB839844A (en) * 1955-05-12 1960-06-29 Max Weber Variable speed friction drive
US3224300A (en) * 1959-09-03 1965-12-21 Walter V Chery Automatic transmission
US3420122A (en) * 1965-11-11 1969-01-07 Kenzo Okabe Infinitely variable friction drive
US4112779A (en) * 1976-11-03 1978-09-12 Vadetec Corporation Variable speed transmission device
US4152946A (en) * 1975-07-22 1979-05-08 Vadetec Corporation Transmission devices
US4183253A (en) * 1977-02-07 1980-01-15 Domenic Borello Dual surface angular power transfer wheel traction nipping device
GB2033034A (en) * 1978-10-27 1980-05-14 Vadetec Corp Infinitely-variable planetary friction gearing
US4208926A (en) * 1978-11-08 1980-06-24 Caterpillar Tractor Co. Nutating drive
US4233851A (en) * 1979-05-04 1980-11-18 Vadetec Corporation Infinitely variable transmission unit and method
US4238976A (en) * 1978-10-19 1980-12-16 Vadetec Corporation Infinitely variable power transmission and system

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US839844A (en) * 1906-01-16 1907-01-01 Hilliard Clutch & Machinery Company Clutch.
US4112780A (en) * 1977-04-01 1978-09-12 Vadetec Corporation Variable speed transmission device
US4277982A (en) * 1979-09-21 1981-07-14 Vadetec Corporation Torque transmitting body for traction drive transmissions and normal friction force developing method

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB839844A (en) * 1955-05-12 1960-06-29 Max Weber Variable speed friction drive
US3224300A (en) * 1959-09-03 1965-12-21 Walter V Chery Automatic transmission
US3420122A (en) * 1965-11-11 1969-01-07 Kenzo Okabe Infinitely variable friction drive
US4152946A (en) * 1975-07-22 1979-05-08 Vadetec Corporation Transmission devices
US4112779A (en) * 1976-11-03 1978-09-12 Vadetec Corporation Variable speed transmission device
US4183253A (en) * 1977-02-07 1980-01-15 Domenic Borello Dual surface angular power transfer wheel traction nipping device
US4238976A (en) * 1978-10-19 1980-12-16 Vadetec Corporation Infinitely variable power transmission and system
GB2033034A (en) * 1978-10-27 1980-05-14 Vadetec Corp Infinitely-variable planetary friction gearing
US4208926A (en) * 1978-11-08 1980-06-24 Caterpillar Tractor Co. Nutating drive
US4233851A (en) * 1979-05-04 1980-11-18 Vadetec Corporation Infinitely variable transmission unit and method

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP0052603A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4170200A1 (fr) * 2021-10-20 2023-04-26 Suzuki Motor Corporation Transmission à variation continue

Also Published As

Publication number Publication date
EP0052603A4 (fr) 1984-04-27
IT1144717B (it) 1986-10-29
CA1149642A (fr) 1983-07-12
GB2087009A (en) 1982-05-19
GB2087009B (en) 1984-05-02
JPS57500892A (fr) 1982-05-20
DE3050385A1 (de) 1982-06-16
EP0052603A1 (fr) 1982-06-02

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