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WO1998020269A1 - Transmission a variation continue equipee d'un appareil de lubrification - Google Patents

Transmission a variation continue equipee d'un appareil de lubrification Download PDF

Info

Publication number
WO1998020269A1
WO1998020269A1 PCT/JP1997/003952 JP9703952W WO9820269A1 WO 1998020269 A1 WO1998020269 A1 WO 1998020269A1 JP 9703952 W JP9703952 W JP 9703952W WO 9820269 A1 WO9820269 A1 WO 9820269A1
Authority
WO
WIPO (PCT)
Prior art keywords
pulley half
driven pulley
drive pulley
moveable
belt
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.)
Ceased
Application number
PCT/JP1997/003952
Other languages
English (en)
Inventor
Daisuke Kobayashi
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.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co Ltd
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 Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Priority to EP97909695A priority Critical patent/EP0866929A1/fr
Publication of WO1998020269A1 publication Critical patent/WO1998020269A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0456—Lubrication by injection; Injection nozzles or tubes therefor
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0487—Friction gearings
    • F16H57/0489—Friction gearings with endless flexible members, e.g. belt CVTs
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/05—Features relating to lubrication or cooling or heating of chains
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members

Definitions

  • the present invention relates to a continuously variable transmission (CVT) for a vehicle and, more specifically, to a CVT of a V-belt type which includes a lubricating apparatus .
  • CVT continuously variable transmission
  • Application First Publication No. 8-254260 discloses a CVT of such a V-belt type which has a lubricating apparatus .
  • the apparatus includes a set of injector nozzles provided for injecting lubricating oil toward belt portions of a V-belt which are engaged with drive and driven pulleys, respectively.
  • the belt portions are influenced by frictional heat caused by a relative slide movement of a ring and an element constituting the V-belt , on the drive and driven pulleys .
  • the belt portions are cooled and lubricated by the lubricating oil injected from the corresponding injector nozzles.
  • the injector nozzles have outlets open to substantially a common hypothetical plane perpendicular to mutually parallel axes of rotation of the drive and driven pulleys .
  • a continuously variable transmission comprising: a drive pulley rotatable about a first axis, the drive pulley including a fixed drive pulley half and a moveable drive pulley half axially moveable relative to the fixed drive pulley half to vary a first axial distance therebetween; a driven pulley rotatable about a second axis parallel to the first axis, the driven pulley including a fixed driven pulley half and a moveable driven pulley half axially moveable relative to the fixed driven pulley half to vary a second axial distance therebetween; the moveable drive pulley half and said moveable driven pulley half cooperating to vary the first and second axial distances in inverse proportion; a V-belt drivingly connecting the drive pulley to the driven pulley; and a first injector nozzle and a second injector nozzle adapted to inject lubricating oil to the V- belt, respectively; the first injector
  • a continuously variable transmission including a drive pulley rotatable about a first axis, the drive pulley including a fixed drive pulley half and a moveable drive pulley half axially moveable relative to the fixed drive pulley half to vary a first axial distance therebetween, a driven pulley rotatable about a second axis parallel to the first axis, the driven pulley including a fixed driven pulley half and a moveable driven pulley half axially moveable relative to the fixed driven pulley half to vary a second axial distance therebetween, the moveable drive pulley half and the moveable driven pulley half cooperating to vary the first and second axial distances in inverse proportion, a V-belt drivingly connecting the drive pulley to the driven pulley, first and second injector nozzles adapted to inject lubricating oil to the V-belt through outlets thereof, respectively, a hydraulic pump supplying a pressure of
  • a lubricating apparatus for use in a continuously variable transmission including a drive pulley rotatable about a first axis, the drive pulley including a fixed drive pulley half and a moveable drive pulley half axially moveable relative to the fixed drive pulley half to vary a first axial distance therebetween, a driven pulley rotatable about a second axis parallel to the first axis, the driven pulley including a fixed driven pulley half and a moveable driven pulley half axially moveable relative to the fixed driven pulley half to vary a second axial distance therebetween, the moveable drive pulley half and the moveable driven pulley half cooperating to vary the first and second axial distances in inverse proportion, and a V-belt drivingly connecting the drive pulley to the driven pulley, comprising: a hydraulic pump feeding lubricating oil; a pressure regulator fluidly connected to the hydraulic pump to adjust a
  • Fig. 1 is a schematic diagram showing a continuously variable transmission (CVT) of a V-belt type, of a first embodiment according to the present invention, which is incorporated in a transaxle drivingly connected to an engine;
  • CVT continuously variable transmission
  • Fig. 2 is an enlarged section of a V-belt, taken in a radial direction thereof;
  • Fig. 3 is a fragmentary enlarged side view of the V-belt, as viewed in a circumferential direction thereof ;
  • Fig. 4 is a fragmentary enlarged longitudinal section of a main part of the CVT, taken in a longitudinal direction of the V-belt, showing a lubricating condition in a case where a speed ratio is maximum;
  • Fig. 5 is a fragmentary enlarged cross section as viewed in a direction perpendicular to the direction of Fig. 4;
  • Fig. 6 is a section similar to Fig. 4, but showing a lubricating condition in a case where the speed ratio is minimum;
  • Fig. 7A is a fragmentary schematic side view of the V-belt tensioned on drive and driven pulleys, showing conditions of contact between a ring and an element in the case of the maximum speed ratio;
  • Fig. 7B is a fragmentary schematic side view similar to Fig. 7A, but showing conditions of contact between the ring and the element in the case of the minimum speed ratio;
  • Fig. 8 is a graph illustrating a relationship between the speed ratio and difference in speed between the ring and the element ;
  • Fig. 9 is a section similar to Fig. 4, but showing a main part of the CVT of a second embodiment according to the present invention.
  • Fig. 10 is a section similar to Fig. 5, but showing the main part of the CVT of the second embodiment .
  • CVT continuously variable transmission
  • the CVT includes a drive pulley 1 as input pulley, a driven pulley 2 as output pulley, and a V-belt 3 drivingly connecting the drive pulley 1 and the driven pulley 2.
  • the drive pulley 1 includes a driver shaft la as input shaft, which is connected via a torque converter 4 and a clutch 5 to an output shaft 6a of an engine 6 to be rotatable about an axis .
  • the drive pulley 1 is rotatable about the axis of rotation of the driver shaft la.
  • the driver shaft la extends in one direction, i.e., left as viewed in Fig. 1, along the axis X.
  • the drive pulley 1 includes a fixed drive pulley half lb securely connected to the driver shaft la and an axially moveable drive pulley half lc mounted to the driver shaft la in opposed spaced relation to the fixed drive pulley half lb to define therewith a drive pulley groove.
  • the drive pulley halves lb and lc are of a generally frustoconical shape.
  • the moveable drive pulley half lc is axially moveable relative to the fixed drive pulley half lb to vary an axial distance therebetween, i.e., a width of the drive pulley groove.
  • the driven pulley 2 includes a follower shaft 2a rotatable about an axis parallel to the axis of the driver shaft la.
  • the follower shaft 2a extends in an opposite direction, namely, right as viewed in Fig. 1, along the axis.
  • the driven pulley 2 includes a fixed driven pulley half 2b securely connected to the follower shaft 2a and an axially moveable driven pulley half 2c mounted to the follower shaft 2a in opposed spaced relation to the fixed drive pulley half lb to define therewith a driven pulley groove.
  • the driven pulley halves 2b and 2c are of a generally frustoconical shape.
  • the moveable driven pulley half 2c is axially moveable relative to the fixed driven pulley half 2b to vary an axial distance therebetween, i.e., a width of the driven pulley groove.
  • the fixed driven pulley half 2b is axially displaced by a predetermined distance from the fixed drive pulley half lb.
  • the moveable drive pulley half lc and the moveable driven pulley half 2c are operatively coupled to a pressure regulator 8 fluidly connected with a hydraulic pump 7.
  • the pressure regulator 8 is operatively coupled with a controller 9 which develops a control signal for achieving a predetermined speed ratio corresponding to a predetermined shift pattern depending on operating condition of the vehicle.
  • speed ratio is defined as a ratio of rotation speed of input shaft, i.e., the driver shaft la, of the CVT to rotation speed of output shaft, i.e., the follower shaft 2a, thereof.
  • the pressure regulator 8 is operative in response to the control signal to apply fluid pressures to the moveable drive pulley half lc and the moveable driven pulley half 2c .
  • the moveable pulley halves lc and 2c are hydraulically operated to move to the respective axial positions corresponding to the fluid pressures.
  • the respective axial distances between the drive pulley halves lb and lc and between the driven pulley halves 2b and 2c are variable by the axial positions of the moveable drive pulley half lc and the moveable driven pulley half 2c.
  • the moveable drive pulley half lc and the moveable driven pulley half 2c cooperate to vary the respective axial distances from the fixed drive pulley half lb and the fixed driven pulley half 2b, in inverse proportion.
  • the inversely proportional change of the axial distances between the drive pulley halves lb and lc and between the driven pulley halves 2b and 2c, alters a radius of curvature over which the V-belt 3 frictionally contacts with the pulley groove walls of the drive pulley 1 and the driven pulley 2. This causes change of the speed ratio of the CVT.
  • the moveable drive pulley half lc siidably moves leftward as viewed in Fig. 1, away from the fixed drive pulley half lb to increase the axial distance therebetween, while the moveable driven pulley half 2c siidably moves leftward as viewed in Fig. 1, closer to the fixed driven pulley half 2b to reduce the axial distance therebetween.
  • the radius of curvature over which the V- belt 3 frictionally contacts with the pulley groove walls of the drive pulley 1 decreases
  • the radius of curvature over which the V-belt 3 frictionally contacts with the pulley groove walls of the driven pulley 2 increases. Therefore, the speed ratio becomes larger corresponding to a LOW shift range.
  • the speed ratio is maximum corresponding to the most LOW shift position.
  • the moveable drive pulley half lc siidably moves toward the fixed drive pulley half lb to reduce the axial distance therebetween
  • the moveable driven pulley half 2c siidably moves apart from the fixed driven pulley half 2b to increase the axial distance therebetween.
  • the radius of curvature over which the V-belt 3 frictionally contacts with the pulley groove walls of the drive pulley 1 increases , while the radius of curvature over which the V-belt 3 frictionally contacts with the pulley groove walls of the driven pulley 2 decreases.
  • the speed ratio becomes smaller corresponding to a HIGH shift range.
  • the V-belt 3 has a structure as explained hereinafter.
  • the V-belt is made of a suitable metal.
  • the V-belt 3 includes an endless ring 3a having a multi-layered structure, and a plurality of elements 3b mounted to the ring 3a.
  • the elements 3b are continuously disposed in a circumferential direction of the ring 3a.
  • Each of the elements 3b includes a protrudent portion having a generally triangular flat surface as shown in Fig. 2.
  • the protrudent portion is connected with a leg-like portion tapered radially inward the ring 3a as shown in Fig. 3, through a central post portion interposed therebetween as shown in Fig. 2.
  • Opposed slots are disposed adjacent the central post portion and extend parallel to each other in the circumferential direction of the ring 3a to be engaged with the ring 3a.
  • the leg-like portion has a vertical surface flush with the triangular flat surface of the protrudent portion, and a slant surface 3c inclined relative to the vertical surface.
  • a boundary between the flat surface and the slant surface 3c is indicated by A in Fig. 3.
  • Each element 3b is rotatable on the boundary A relative to the adjacent element 3b.
  • the boundary A is arranged so as to be spaced radially inward by a distance r from a bearing surface B contacting a radial inner side of the ring 3a.
  • the radial distance r may be approximately 1 mm.
  • the provision of the slant surface 3c allows a row of the elements 3b to curve along the ring 3a on the radial inner side, causing the V-belt 3 to be wound on the drive pulley 1 and driven pulley 2.
  • the leglike portion of the element 3b also has opposed side faces adjacent the slant surface 3c which are frictionally contacted with the respective pulley groove walls of the drive pulley 1 and the driven pulley 2 when the V-belt is mounted to the drive and driven pulleys 1 and 2.
  • the V-belt 3 tensioned between the drive pulley 1 and the driven pulley 2 transmits a torque by the friction contact of the element 3b with the respective pulley groove walls of the drive and driven pulleys 1 and 2.
  • two separate injector nozzles 10 and 11 adapted to inject lubricating oil to the V-belt 3 are disposed in the vicinity of the drive pulley 1 and the driven pulley 2.
  • the injector nozzles 10 and 11 are fluidly connected to the pressure regulator 8 via separate lubricating oil feed pipes 12 and 13, respectively.
  • the injector nozzles 10 and 11 are provided for injecting the lubricating oil fed from the pressure regulator 8 to the V-belt engaged with the drive and driven pulleys 1 and 2 to thereby cool the V-belt .
  • the injector nozzles 10 and 11 have outlets open to two hypothetical planes which are perpendicular to the axes of rotation of the drive and driven pulleys 1 and 2 and axially displaced by a predetermined distance from each other.
  • One of the hypothetical planes extends through substantially a midpoint of a maximum of the axial distance between the fixed and moveable drive pulley halves lb and lc, and the other extends through substantially a midpoint of a maximum of the axial distance between the fixed and moveable driven pulley halves 2b and 2c.
  • the injector nozzles are adapted to spray the lubricating oil from the outlets onto the V-belt along the hypothetical planes, respectively.
  • the injector nozzle 10 has the outlet open to a first hypothetical plane C extending perpendicularly to the axis of rotation of the drive pulley 1 through substantially the midpoint of the maximum axial distance between the fixed and moveable drive pulley halves lb and lc.
  • the radius of curvature over which the V-belt 3 contacts with the drive pulley halves lb and lc is smallest for the maximum speed ratio as explained above.
  • a center line of the V- belt 3 which extends in a longitudinal direction of the V-belt 3 is contained substantially in the first hypothetical plane C.
  • the outlet of the injector nozzle 10 is thus directed to a central portion of the V-belt 3 which extends along the center line, and so designed as to spray the lubricating oil onto the central portion of the V-belt 3 along the first hypothetical plane C.
  • the injector nozzle 11 has the outlet open to a second hypothetical plane C which is parallel to the first hypothetical plane C and axially offset by a predetermined distance ⁇ from the first hypothetical plane C in such a manner as to be away from the fixed driven pulley half 2b, and extends through substantially the midpoint of the maximum axial distance between the fixed and moveable driven pulley halves 2b and 2c.
  • the outlet of the injector nozzle 11 is so designed to spray the lubricating oil onto the V-belt 3 along the second hypothetical plane C.
  • the outlet of the injector nozzle 11 is directed to the central portion of the V-belt 3 between the driven pulley halves 2b and 2c, when the V-belt 3 is placed in a position, as shown in Fig. 6, for the minimum speed ratio of the CVT as explained later.
  • the injector nozzles 10 and 11 are disposed within an area defined by the drive pulley 1, the driven pulley 2 and the V-belt 3.
  • the outlets of the injector nozzles 10 and 11 are arranged near an inner circumferential portion of the V-belt 3.
  • the outlet of the injector nozzle 10 is directed to near a belt portion 31 of the V-belt 3 which engages the fixed and moveable drive pulley halves lb and lc.
  • the outlet of the injector nozzle 11 is directed to near a belt portion 32 of the V-belt 3 which engages the fixed and moveable driven pulley halves 2b and 2c.
  • the outlets of the injector nozzles 10 and 11 are oriented in opposite directions as shown in Fig. 5, such that the lubricant oil is sprayed in the opposite directions.
  • Fig. 6 illustrates the drive pulley halves lb and lc, the driven pulley halves 2b and 2c and the V-belt 3 of the CVT conditioned to achieve the minimum speed ratio.
  • the V-belt 3 is placed in the position displaced axially and along the plane C from the position shown in Fig. 4. In this position, the radius of curvature over which the V-belt 3 contacts with the driven pulley halves 2b and 2c is smallest, and the center line of the V-belt 3 lies substantially in the second hypothetical plane C.
  • Figs. 7A and 7B illustrate fragmentary schematic side views showing conditions of the contact between the ring 3a and the element 3b of the V-belt 3 tensioned over the drive and driven pulleys 1 and 2 in the cases of the larger speed ratio and the smaller speed ratio.
  • Point A i.e., the boundary A
  • Point B i.e., the bearing surface B
  • Fig. 7B forms arc trajectories on the drive pulley 1 and the driven pulley 2 on the radial outer side of the V-belt 3, as shown in Fig. 7B.
  • an angle of contact of the V-belt 3 with the drive pulley 1 is smaller than an angle of contact thereof with the driven pulley 2, and a length of the belt portion of the V-belt 3 which contacts with the drive pulley 1 is smaller than a length thereof contacting with the driven pulley 2.
  • a frictional force caused between the ring 3a and the element 3b on the drive pulley 1 is smaller than a frictional force caused between those on the driven pulley 2.
  • an angular velocity of the ring 3a on the bearing surface B at the curvature of the V-belt 3 is smaller than an angular velocity of the element 3b at the curvature thereof .
  • the relative slide movement causes frictional heat on the mutually contacting portions of the radial inner side surface of the ring 3a and the bearing surface B of the element 3b on the drive pulley 1.
  • the ring 3a and the element 3b on the driven pulley 2 make a substantially unitary rotation so that the relative slide movement therebetween is not substantially caused.
  • CVT ratio the speed ratio of the CVT
  • CVT ratio difference in speed between the ring 3a and the element 3b of the V-belt 3
  • Fig. 8 shows calculation results of the difference in speed between the ring 3a and the element 3b which is produced by changing the CVT ratio assuming that the V-belt 3 has an entire length of 700 mm, a distance between the driver shaft la and the follower shaft 2a is 160 mm, and a rotation speed of the driver shaft la is 4000 rpm.
  • the difference in speed between the ring 3a and the element 3b is caused on the input pulley side, i.e., the drive pulley side, when the CVT ratio is larger than 1.0, while the difference in speed therebetween is caused on the output pulley side, i.e., the driven pulley side, when the CVT ratio is smaller than 1.0.
  • the CVT ratio becomes much larger or much smaller than 1.0, the difference in speed between the ring 3a and the element 3b and thus the relative slide movement therebetween increases, causing the larger frictional heat.
  • the CVT ratio is maximum as shown in Fig.
  • the outlet of the injector nozzle 10 is oriented to the belt portion which is influenced by the frictional heat and disposed substantially in the first hypothetical plane C. This arrangement of the outlet of the injector nozzle 10 assures that the lubricant oil is injected to the belt portion on the drive pulley 1 to thereby cool the belt portion frictionally heated and at the same time effectively lubricate the belt portion.
  • the outlet of the injector nozzle 11 is axially offset by the predetermined distance ⁇ , for instance 9.5 mm assuming the condition explained above by referring to Fig. 8.
  • the lubricating oil is injected to the belt portion of the V-belt 3 which is engaged with the driven pulley 2 , in such a manner as axially offset by the predetermined distance ⁇ from the central portion of the V-belt 3.
  • the belt portion engaged with the driven pulley 2 is not influenced by frictional heat caused by the relative slide movement.
  • the lubricant oil is injected from the outlet of the injector nozzle 11 to the belt portion on the driven pulley 2 to cool the belt portion frictionally heated and effectively lubricate the belt portion.
  • the relative slide movement between the ring 3a and the element 3b of the belt portion of the V-belt 3 which is engaged with the drive pulley 1 is not caused. Therefore, the belt portion on the drive pulley 1 is not exposed to frictional heat caused by the relative slide movement between the ring 3a and the element 3b.
  • FIGs. 9 and 10 the CVT of the second embodiment according to the invention is explained, which is similar to the CVT of the first embodiment except that injector nozzles 100 and 110 are connected with a common lubricating oil feed pipe 14.
  • injector nozzles 100 and 110 are connected with a common lubricating oil feed pipe 14.
  • Like reference numerals and symbols denote like parts and therefore detailed explanations therefor are omitted.
  • Figs. 9 and 10 illustrate the condition of the drive pulley 1, the driven pulley 2 and the V-belt 3 in the case of the maximum speed ratio, as shown in Figs. 4 and 5.
  • the injector nozzles 100 and 110 are coupled with the common lubricating oil feed pipe 14.
  • the common lubricating oil feed pipe 14 is fluidly connected to the hydraulic pump 7 via the pressure regulator 8, as well as the lubricating oil feed pipes 12 and 13 of the first embodiment.
  • the injector nozzles 100 and 110 are substantially same as the injector nozzles 10 and 11 of the first embodiment in otherwise structural features. Accordingly, in the case of the maximum speed ratio, an outlet of the injector nozzle 100 is open to the first hypothetical plane C extending through substantially the center line of the V-belt 3, and an outlet of the injector nozzle 110 is open to the second hypothetical plane C axially offset by the predetermined distance ⁇ from the first hypothetical plane C. Then, the outlet of the injector nozzle 110 is axially displaced substantially by the predetermined distance ⁇ from the center line of the V-belt 3.
  • the injector nozzles 100 and 110 connected by the lubricating oil feed pipe 14 are concentratedly arranged in the area defined by the drive and driven pulleys 1 and 2 and the V- belt 3.
  • the outlets of the injector nozzles 100 and 110 are oriented in substantially diametrically opposite directions so as to spray lubricating oil in the substantially diametrically opposite directions toward the belt portions of the V-belt 3 which are engaged with the drive and driven pulleys 1 and 2, respectively.
  • This concentrated arrangement of the injector nozzles 100 and 110 serves for saving a space required for installing lubricating oil feed pipes , thereby providing a wide variety of design of the CVT.
  • the arrangement of the second embodiment can assure the injection of lubricating oil to the belt portion of the V-belt which is exposed to frictional heat caused in the CVT operation, facilitating cooling and lubricating of the V-belt and then increasing a performance of the CVT.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmissions By Endless Flexible Members (AREA)
  • General Details Of Gearings (AREA)

Abstract

Cette invention concerne une transmission à variation continue, laquelle comprend une poulie d'entraînement (1) et une poulie asservie (2) qui tournent autour d'axes parallèles. La poulie d'entraînement (1) comporte une moitié de poulie mobile (1c) qui peut se déplacer axialement par rapport à une moitié de poulie fixe (1b) de manière à faire varier une première distance axiale entre ces dernières. La poulie asservie (2) comporte une moitié de poulie mobile (2c) qui peut se déplacer axialement par rapport à une moitié de poulie fixe (2b) de manière à faire varier une seconde distance axiale entre ces dernières. Les moitiés de poulies mobiles (1c, 2c) entrent en interaction de manière à faire varier les première et seconde distances axiales selon des proportions inverses. Une courroie en forme de V (3) assure la connexion et l'entraînement entre la poulie d'entraînement (1) et la poulie asservie (2). Deux buses d'injection (10, 11) possèdent des ouvertures qui s'ouvrent sur deux plans parallèles, imaginaires et décalés axialement, respectivement. Ces plans sont perpendiculaires aux axes et passent globalement par le point médian de la première distance axiale maximale, ainsi que par le point médian de la seconde distance axiale maximale, respectivement.
PCT/JP1997/003952 1996-11-05 1997-10-30 Transmission a variation continue equipee d'un appareil de lubrification Ceased WO1998020269A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP97909695A EP0866929A1 (fr) 1996-11-05 1997-10-30 Transmission a variation continue equipee d'un appareil de lubrification

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP8/292763 1996-11-05
JP8292763A JPH10141459A (ja) 1996-11-05 1996-11-05 ベルト式無段変速機の潤滑装置

Publications (1)

Publication Number Publication Date
WO1998020269A1 true WO1998020269A1 (fr) 1998-05-14

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1997/003952 Ceased WO1998020269A1 (fr) 1996-11-05 1997-10-30 Transmission a variation continue equipee d'un appareil de lubrification

Country Status (4)

Country Link
EP (1) EP0866929A1 (fr)
JP (1) JPH10141459A (fr)
KR (1) KR20000004901A (fr)
WO (1) WO1998020269A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2331561A (en) * 1997-11-24 1999-05-26 Luk Getriebe Systeme Gmbh Lubrication of a continuously variable speed transmission
EP1162390A1 (fr) 2000-06-09 2001-12-12 Ford Global Technologies, Inc., A subsidiary of Ford Motor Company Dispositif de lubrification pour transmission à variation continue de type à courroie
EP1188957A1 (fr) 2000-09-14 2002-03-20 Ford Global Technologies, Inc., A subsidiary of Ford Motor Company Système de lubrification pour variateur continu de vitesse à poulies coniques
US6626781B2 (en) 2000-06-20 2003-09-30 Van Doorne's Transmissie B.V. Continuously variable transmission having lubrication nozzle outputs at maximum power transmitting secondary radial belt position
WO2009076999A1 (fr) * 2007-12-17 2009-06-25 Robert Bosch Gmbh Transmission à variation continue incorporant une courroie d'entraînement, procédé de fonctionnement de cette transmission et procédé de fabrication de la courroie d'entraînement
EP2187098A4 (fr) * 2007-09-18 2011-03-23 Honda Motor Co Ltd Dispositif de lubrification pour transmission à variation continue de type courroie
EP2998614A4 (fr) * 2013-05-17 2017-03-01 Toyota Jidosha Kabushiki Kaisha Transmission à variation continue
WO2017186701A1 (fr) * 2016-04-27 2017-11-02 Punch Powertrain N.V. Dispositif de lubrification pour système de transmission, système de transmission, et procédé de production dudit dispositif
WO2019008122A1 (fr) 2017-07-05 2019-01-10 Punch Powertrain N.V. Dispositif de lubrification et/ou de refroidissement pour système de transmission à variation continue, et système de transmission à variation continue le comprenant

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KR100366851B1 (ko) * 1998-11-25 2003-04-11 삼성전자 주식회사 세탁기의동력전달장치
DE10245588A1 (de) * 2002-09-27 2004-04-08 Zf Batavia L.L.C., Batavia Stufenloses Umschlingungsgetriebe
KR100692125B1 (ko) 2003-10-30 2007-03-12 현대자동차주식회사 무단 변속기의 벨트 윤활 제어장치
JP4961716B2 (ja) * 2005-10-21 2012-06-27 トヨタ自動車株式会社 ベルト式無段変速機の潤滑装置
JP4582086B2 (ja) 2006-12-13 2010-11-17 トヨタ自動車株式会社 無段変速機用ベルト
JP5055324B2 (ja) * 2009-05-19 2012-10-24 ジヤトコ株式会社 ベルト式無段変速機
CN108591438B (zh) * 2018-07-04 2024-04-09 中国汽车技术研究中心有限公司 一种试验用齿轮箱散热系统

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Cited By (15)

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Publication number Priority date Publication date Assignee Title
GB2331561B (en) * 1997-11-24 2002-09-18 Luk Getriebe Systeme Gmbh Continuously variable speed transmission
GB2331561A (en) * 1997-11-24 1999-05-26 Luk Getriebe Systeme Gmbh Lubrication of a continuously variable speed transmission
EP1162390A1 (fr) 2000-06-09 2001-12-12 Ford Global Technologies, Inc., A subsidiary of Ford Motor Company Dispositif de lubrification pour transmission à variation continue de type à courroie
US6626781B2 (en) 2000-06-20 2003-09-30 Van Doorne's Transmissie B.V. Continuously variable transmission having lubrication nozzle outputs at maximum power transmitting secondary radial belt position
EP1167829B1 (fr) * 2000-06-20 2004-11-10 Van Doorne's Transmissie B.V. Transmission à variation continue avec buses de lubrification aux endroits entraínés de la courroie positionnée radialement pour transmettre la puissance maximale
EP1188957A1 (fr) 2000-09-14 2002-03-20 Ford Global Technologies, Inc., A subsidiary of Ford Motor Company Système de lubrification pour variateur continu de vitesse à poulies coniques
US8672097B2 (en) 2007-09-18 2014-03-18 Honda Motor Co., Ltd Lubrication device for belt type continuously variable transmission
EP2187098A4 (fr) * 2007-09-18 2011-03-23 Honda Motor Co Ltd Dispositif de lubrification pour transmission à variation continue de type courroie
WO2009076999A1 (fr) * 2007-12-17 2009-06-25 Robert Bosch Gmbh Transmission à variation continue incorporant une courroie d'entraînement, procédé de fonctionnement de cette transmission et procédé de fabrication de la courroie d'entraînement
EP2998614A4 (fr) * 2013-05-17 2017-03-01 Toyota Jidosha Kabushiki Kaisha Transmission à variation continue
US9746056B2 (en) 2013-05-17 2017-08-29 Toyota Jidosha Kabushiki Kaisha Continuously variable transmission
WO2017186701A1 (fr) * 2016-04-27 2017-11-02 Punch Powertrain N.V. Dispositif de lubrification pour système de transmission, système de transmission, et procédé de production dudit dispositif
BE1024171B1 (nl) * 2016-04-27 2017-11-27 Punch Powertrain Nv Smeerinrichting voor een transmissiesysteem, transmissiesysteem, en werkwijze voor het produceren van een dergelijke inrichting
CN109154381A (zh) * 2016-04-27 2019-01-04 邦奇动力有限责任公司 用于传动系统的润滑装置、传动系统以及用于生产所述装置的方法
WO2019008122A1 (fr) 2017-07-05 2019-01-10 Punch Powertrain N.V. Dispositif de lubrification et/ou de refroidissement pour système de transmission à variation continue, et système de transmission à variation continue le comprenant

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JPH10141459A (ja) 1998-05-29
KR20000004901A (ko) 2000-01-25
EP0866929A1 (fr) 1998-09-30

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