WO2016088650A1 - Transmission à variation continue de type à courroie - Google Patents

Transmission à variation continue de type à courroie Download PDF

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Publication number
WO2016088650A1
WO2016088650A1 PCT/JP2015/083277 JP2015083277W WO2016088650A1 WO 2016088650 A1 WO2016088650 A1 WO 2016088650A1 JP 2015083277 W JP2015083277 W JP 2015083277W WO 2016088650 A1 WO2016088650 A1 WO 2016088650A1
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WO
WIPO (PCT)
Prior art keywords
pulley half
belt
contact member
continuously variable
variable transmission
Prior art date
Application number
PCT/JP2015/083277
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English (en)
Japanese (ja)
Inventor
矢ケ崎　徹
Original Assignee
本田技研工業株式会社
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 本田技研工業株式会社 filed Critical 本田技研工業株式会社
Priority to JP2016562408A priority Critical patent/JP6379216B2/ja
Publication of WO2016088650A1 publication Critical patent/WO2016088650A1/fr

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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
    • F16H—GEARING
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
    • 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
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
    • F16H9/16—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts
    • F16H9/18—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts only one flange of each pulley being adjustable

Definitions

  • the present invention comprises a drive pulley and a driven pulley, and an endless belt wound around the drive pulley and the driven pulley, and changing the groove width of the belt groove formed between the two pulleys.
  • the present invention relates to a belt-type continuously variable transmission which can change the gear ratio between pulleys continuously.
  • a belt type continuously variable transmission that can change steplessly.
  • at least one of the drive pulley and the driven pulley forms a belt groove in cooperation with the fixed pulley half formed integrally with the rotating shaft and the fixed pulley half.
  • Patent Document 1 As a technique for preventing the inclination of the pulley surface of the movable pulley half due to the deviation of the thrust of the movable pulley half, there is a belt type continuously variable transmission described in Patent Document 1 conventionally.
  • the belt type continuously variable transmission described in Patent Document 1 three sets of hydraulic cylinder mechanisms are arranged in parallel on the back side of the movable pulley half.
  • the distribution of the thrust acting on the movable pulley half can be made as uniform as possible inside and outside the radial direction, and the inclination of the pulley surface of the movable pulley half due to the deviation of the moment can be effectively prevented. Therefore, problems such as an increase in power loss due to the inclination of the movable pulley half can be effectively suppressed while aiming to further expand the pressure receiving area of the movable pulley half.
  • the movable pulley half receives a thrust from the hydraulic drive means, and the movable pulley half contacts with the endless belt when advancing and retracting in the axial direction. Since the surface receives thrust from the three sets of hydraulic cylinder mechanisms, deviation of the moment acting on the movable pulley half is avoided. Therefore, by preventing the inclination of the contact surface of the movable pulley, it is possible to prevent an increase in power loss due to the inclination of the contact surface between the endless belt and the movable pulley.
  • the movable pulley half when the movable pulley half receives the thrust from the hydraulic drive means, the thrust is also transmitted to the fixed pulley half through the endless belt,
  • the contact surface of the fixed pulley half with the endless belt may be inclined. Therefore, not only the inclination of the contact surface of the movable pulley half is prevented but also the inclination of the contact surface of the fixed pulley half is also prevented in order to more effectively suppress the increase in power loss and the like in the belt type continuously variable transmission. It is effective to take measures that can be taken.
  • the present invention has been made in view of the above-described point, and an object thereof is to suppress the power transmission loss more effectively by suppressing the slip occurring on the contact surface of the fixed pulley half with the endless belt.
  • a belt-type continuously variable transmission is an endless belt wound around a drive pulley (P1) and a driven pulley (P2), and the drive pulley (P1) and the driven pulley (P2).
  • At least one of the drive pulley (P1) and the driven pulley (P2) is a fixed pulley half (1) integrally formed with the rotary shaft (1k), and a fixed pulley half Working together with (1) to form the belt groove (G) and change the groove width of the movable groove half (2) and the belt groove (G) which are slidably supported on the rotating shaft (1k)
  • the movable pulley half (2) against the fixed pulley (1) half
  • a plate-like contact member provided on the surface of the fixed pulley half on the movable pulley half side and in contact with the endless belt, the contact member and the fixed pulley half And a joining means for joining them so as to rotate integrally, and forming a clearance between the fixed pulley half and the contact member allows the driving means to move the thrust (axial direction) to the movable pulley half.
  • the thrust force is applied, the thrust is transmitted to the contact member through the endless belt, so that the contact member is deformed toward the fixed pulley half so as to narrow the gap between the fixed pulley half and the fixed pulley half.
  • the inclination of the contact surface of the contact member with the endless belt is optimized, thereby reducing slippage between the endless belt and the contact member.
  • a continuously variable transmission can be provided.
  • the contact member when a thrust is transmitted from the endless belt to the contact member, the contact member is first deformed, and then the contact member is deformed to a position where it abuts against the fixed pulley half, and then the fixed pulley half is applied with a thrust The pulley half is deformed. Therefore, in the belt type continuously variable transmission of the conventional structure, only the fixed pulley reverser is deformed because all the thrust from the endless belt is applied to the fixed pulley half, but the belt type according to the present invention In the continuously variable transmission, the amount of deformation due to the thrust applied from the endless belt is dispersed into the amount of deformation of the contact member and the amount of deformation of the fixed pulley half.
  • a belt type continuously variable transmission can be provided.
  • the clearance (22) has a maximum winding diameter (L1) at which the endless belt (B) contacts the contact member (20) in the radial direction of the fixed pulley half (1). And the minimum winding diameter (L2). According to this configuration, even when the endless belt is at any position in the radial direction, the deformation of the contact member by the thrust applied from the endless belt to the contact member is allowed. Therefore, regardless of the ratio set in the belt type continuously variable transmission, slippage of the contact surface of the contact member (fixed pulley half) with the endless belt can be effectively prevented.
  • the joint means (21) is provided at the radial outer end (22a) of the gap (22), and the gap (22) is in the radial direction
  • the axial width dimension may gradually increase from the outer end (22a) to the inner end (22b).
  • the surface (1c) on the contact member (20) side of the fixed pulley half (1) is a surface perpendicular to the axial direction of the rotating shaft (1k), and the endless shape of the contact member (20)
  • the surface (20c) in contact with the belt (B) may be a surface inclined with respect to the axial direction of the rotation axis (1k). According to this configuration, it is possible to effectively suppress the slip of the contact surface between the contact member (fixed pulley half) and the endless belt while the fixed pulley half is easily processed.
  • the axial thickness dimension of the contact member (20) may be formed so that the outer side is thicker than the inner side in the radial direction. According to this configuration, the radial inner side of the contact member is preferentially deformed when a thrust is applied to the contact member. Therefore, the slip of the contact surface between the contact member (fixed pulley half) and the endless belt can be more effectively suppressed.
  • the belt type continuously variable transmission is provided with an oil passage (12) formed in the rotary shaft (1k) and communicating with the clearance (22), and the working oil from the oil passage (12) 22) may be supplied.
  • the hydraulic oil supplied to the gap can exert a buffer action against the deformation of the contact member, so that the inclination of the contact surface of the contact member with the endless belt can be further optimized. . Therefore, the slip between the endless belt and the surface of the contact member can be reduced more effectively.
  • the working oil exerts the above-described shock absorbing action, the rigidity of the contact member can be reduced to that extent, so that the thickness and weight of the contact member can be reduced.
  • another plate-like contact member provided on the surface on the fixed pulley half (1) side of the movable pulley half (2) and in contact with the endless belt (B) 30) and other joining means (31) for joining the other contact members (30) and the movable pulley half (2) so that they rotate together, the movable pulley half (2) and the other It may further comprise another clearance (32) formed between the contact member (30).
  • the power transmission loss can be more effectively suppressed by suppressing the slip occurring on the contact surface of the fixed pulley half with the endless belt.
  • FIG. 1 is a skeleton diagram of a power transmission system including a belt type continuously variable transmission according to one embodiment of the present invention. It is a longitudinal cross-sectional view of the drive pulley with which the belt type continuously variable transmission concerning 1st Embodiment is provided. It is a schematic diagram which shows the deformation state of a pulley face plate and a fixed pulley half body. It is a schematic diagram which shows the deformation state of a pulley face plate and a fixed pulley half body. It is a figure which shows the other structural example of a fixed pulley half body and a pulley face plate. It is a longitudinal cross-sectional view of the drive pulley with which the belt type continuously variable transmission concerning 2nd Embodiment is provided.
  • FIG. 1 is a skeleton diagram of a power transmission system including a belt type continuously variable transmission according to an embodiment of the present invention.
  • FIG. 2 is a longitudinal sectional view of a drive pulley provided in the belt-type continuously variable transmission according to the first embodiment.
  • the power of the engine E mounted on the vehicle is the damper D, the drive shaft Si, the forward / reverse switching mechanism 4, the metal belt type continuously variable transmission (hereinafter simply referred to as "continuously variable transmission") And T), the driven shaft So, the starting clutch 5, the gear transmission mechanism 6, and the differential mechanism 7 sequentially to the left and right driving wheels W, W.
  • the continuously variable transmission T is interposed between a drive shaft Si and a driven shaft So arranged in parallel to each other, and continuously changes the transmission ratio between the both shafts Si and So.
  • the continuously variable transmission T includes an endless metal belt B wound around a drive pulley P1 supported on a drive shaft Si, a driven pulley P2 provided on a driven shaft So, and both pulleys P1 and P2. And And by changing the groove width of the belt groove G which both pulleys P1 and P2 have, it is possible to change the transmission ratio between both pulleys P1 and P2 and hence the drive shaft Si and the driven shaft So steplessly.
  • Hydraulic fluid is supplied to and discharged from each of the pulleys P1 and P2 from the hydraulic control unit U, which is operationally controlled by the electronic control unit ECU, according to the operating state of the engine E, and stepless control of the transmission ratio is performed.
  • the metal belt B is configured by attaching a large number of metal elements 9 to the left and right two metal ring assemblies 8 and 8. Since the structure of the metal belt B is conventionally known, the specific description thereof is omitted.
  • the end of the crankshaft Ec of the engine E is connected to one end of the drive shaft Si via the damper D, and on the middle portion of the drive shaft Si, the drive pulley of the continuously variable transmission T P1 is rotatably fitted and supported. Further, the other end of the drive shaft Si is connected to the input side of a forward / reverse switching mechanism 4 consisting of a planetary gear mechanism, and the output side of the forward / reverse switching mechanism 4 is connected to the fixed pulley half 1 of the drive pulley P1. Be done.
  • the input side of the starting clutch 5 is connected to one end of the driven shaft So, and on the output side of the clutch 5, the left and right driving wheels W, W are connected via the gear transmission mechanism 6 and the differential mechanism 7. It is connected.
  • the drive pulley P1 forms a belt groove G in cooperation with the fixed pulley half 1 integrally having a rotary shaft 1k integrally fitted and supported with the drive shaft Si so as to be relatively rotatable.
  • a hydraulic drive means (drive means) A which can be driven to advance and retract in the axial direction with respect to the pulley half 1 is provided.
  • the back of the movable pulley half 2 extends from the inner peripheral end of the back in the opposite direction to the fixed pulley half 1 and can be relatively rotated through the bearing 10 on the outer circumference of the rotary shaft 1k.
  • a cylindrical boss portion 2b slidably fitted and supported, and a cylindrical cylinder portion 2c concentric with the boss portion 2b from the outer peripheral end of the back surface and extending in the same direction are integrally provided. Ru.
  • the hydraulic drive means A is composed of first to third hydraulic cylinders A1 to A3 arranged in parallel with each other on the back side of the movable pulley half 2.
  • the movable pulley half 2 By supplying hydraulic fluid to the oil chambers c1, c2 and c3 of the first to third hydraulic cylinders A1 to A3, the movable pulley half 2 generates a thrust toward the fixed pulley half 1, ie, an advancing thrust. I am trying to
  • the first hydraulic cylinder A1 is for applying a forward thrust to a radially intermediate portion on the back surface of the movable pulley half 2, and is slidable between the cylinder 2c and the boss 2b of the movable pulley half 2. And a first piston p1 whose rear surface is engaged with the tip end of the inner cylindrical portion Ci of the pulley cover C, and is defined between the front surface of the first piston p1 and the rear surface of the movable pulley half 2 And a first oil chamber c1.
  • the second hydraulic cylinder A2 is for applying a forward thrust to the inner peripheral end of the rear surface of the movable pulley half 2 via the boss 2b, and the outer periphery of the inner cylindrical portion Ci of the pulley cover C
  • a second piston p2 in which the first portion is slidably fitted via an annular seal member and the inner peripheral portion is liquid-tightly fitted to the outer peripheral step portion of the boss portion 2b of the movable pulley half 2;
  • a second oil chamber c2 defined between the back surface of the piston p2 and the front surface of the pulley cover C is provided.
  • the second piston p2 is appropriately fixed to the boss portion 2b by fixing means (in the illustrated example, the circlip 16 elastically engaged with the outer periphery of the end portion of the boss portion 2b).
  • the third hydraulic cylinder A3 is for applying a forward thrust to the outer peripheral end of the back surface of the movable pulley half 2 via the cylinder portion 2c.
  • a third piston p3 slidably fitted between Co and having a front surface engaged with the tip of the cylinder portion 2c of the movable pulley half 2, and between the rear surface of the third piston p3 and the front surface of the pulley cover C And a third oil chamber c3 defined in
  • the rotary shaft 1k is hollow, and the hollow portion communicates with the hydraulic control unit U and functions as an oil passage 12 into which hydraulic oil from the unit U is introduced.
  • a plurality of first communication oil passages 13 communicating with the oil passage 12 are radially formed on the peripheral wall of the rotary shaft 1k, and the outer peripheral surface of the rotary shaft 1k and the inner peripheral surface of the boss portion 2b of the movable pulley half 2
  • a plurality of second communication oil passages 14 extending in the axial direction and having an outer end directly opening to the second oil chamber c2 are formed between the fitting surfaces of the two at intervals in the circumferential direction.
  • the boss 2b of the movable pulley half 2 is provided with a lateral hole 15 for connecting the second communication oil passage 14 to the first oil chamber c1, and the inner cylindrical portion Ci of the pulley cover C is , And the third oil chamber c2 and c3 are communicated with each other. Accordingly, the hydraulic oil introduced into the oil passage 12 from the hydraulic control unit U is introduced into the first oil chamber c1 via the first and second communication oil passages 13 and 14 and the lateral hole 15, and at the same time substantially simultaneously with the first oil chamber c1. It is introduced into the second oil chamber c2 via the first and second communication oil passages 13 and 14, and is also substantially simultaneously introduced into the third oil chamber c3 from the second oil chamber c2 through the lateral hole 17.
  • the drive pulley P1 of the continuously variable transmission T is a pulley face plate (contact member) that forms a contact surface 20c with the metal belt B and the fixed pulley half 1 integrally formed with the rotary shaft 1k. It has 20 and.
  • the pulley face plate 20 is a plate-like member provided on a surface (a side surface in the axial direction) on the movable pulley half 2 side of the fixed pulley half 1 and in contact with the metal belt B.
  • the pulley face plate 20 is integrally joined to the fixed pulley half 1 by a pin (joining means) 21.
  • the pin 21 joins the fixed pulley half 1 and the outer end (peripheral end) in the radial direction of the pulley face plate 20.
  • a hollow clearance 22 is formed between the fixed pulley half 1 and the pulley face plate 20 (a clearance in the axial direction).
  • the clearance 22 is formed on the inner diameter side relative to the pin 21.
  • the axial width dimension of the clearance 22 is gradually increased from the radial outer end 22a to the inner diameter end 22b.
  • the thrust when the thrust is applied to the movable pulley half 2 from the hydraulic drive means A by providing the pulley face plate 20 having the above configuration, the load from the metal belt B to the pulley face plate 20. The contact pressure is applied.
  • the pulley face plate 20 is configured to be bent and deformed by this load.
  • the pulley face plate 20 is bent to a position where the end 20 b on the inner diameter side contacts the fixed pulley half 1.
  • the pulley face plate 20 provided on the surface of the fixed pulley half 1 on the movable pulley half 2 side and in contact with the metal belt B, and the pulley face plate 20 From the hydraulic drive means A, the fixed pulley half 1 is provided with a pin 21 for jointing them so that they rotate integrally, and a clearance 22 is formed between the fixed pulley half 1 and the pulley face plate 20.
  • FIG.3 and FIG.4 is a schematic diagram which shows the deformation
  • FIG. 4A When no thrust (force in the axial direction) is applied to the movable pulley half 2 from the hydraulic drive means A, neither the pulley face plate 20 nor the fixed pulley half 1 is deformed as shown in FIG. 4A.
  • a load from the metal belt B is applied to the pulley face plate 20 by the application of thrust (axial thrust) to the movable pulley half 2 from the hydraulic drive means A, first, as shown in FIG. 4B
  • the pulley face plate 20 deforms so as to narrow the gap 22.
  • the inner diameter end 20b of the pulley face plate 20 is deformed to a position where it abuts on the fixed pulley half 1, as shown in FIG. 4C, a thrust is also applied to the fixed pulley half 1 to deform the fixed pulley half 1 Do. Therefore, in the drive pulley P1 of the present embodiment, as shown in FIG. 3, the inner diameter end 20b of the pulley face plate 20 is deformed (moved) in the axial direction by applying a thrust from the hydraulic drive means A to the movable pulley half 2. At the same time, the outer diameter end of the fixed pulley half 2 deforms (moves) in the axial direction.
  • the deformation (movement) of the pulley face plate 20 is M1
  • the deformation (movement) of the fixed pulley half 2 is M2.
  • the pulley face plate 20 is bent and deformed while narrowing the gap 22 as described above to receive the thrust. Therefore, the amount of deformation can be controlled by appropriately setting the rigidity of the pulley face plate 20 by selecting the thickness dimension and material of the pulley face plate 20 or the like. Furthermore, by adjusting the rigidity of the fixed pulley half 1 together, it is possible to control the amount of combined deformation of the pulley surface 20 and the fixed pulley half 1.
  • the rigidity of the pulley face plate 20 referred to herein is the rigidity of the pulley face plate 20 alone, and for example, the contact portion with the rotary shaft 1k provided at the inner end 20b of the pulley face plate 20 has a wedge shape.
  • the thrust (energy) required for the deformation can be calculated. Control is also included.
  • the gap portion 22 has a maximum winding diameter L1 and a minimum winding diameter L2 at which the endless belt B in the radial direction of the fixed pulley half 1 contacts the pulley face plate 20 ( It is formed in the position between (refer FIG. 4A).
  • the pin 21 is provided at the outer end 22 a in the radial direction of the clearance 22, and the clearance 22 is in the radial direction
  • the axial width dimension gradually increases from the outer end 22a to the inner end 22b.
  • FIG. 5 is a view showing another configuration example of the fixed pulley half and the pulley face plate.
  • the surface 1c on the pulley face plate 20 side of the fixed pulley half 1 may be a surface perpendicular to the axial direction of the rotation shaft 1k. According to this configuration, slippage of the contact surface between the pulley face plate 20 (fixed pulley half 1) and the endless belt B can be effectively suppressed while the fixed pulley half 1 is easily processed.
  • the thickness dimension of the axial direction of the pulley face plate 20 can also be formed in the dimension whose outer direction is thicker than the inner side of radial direction. According to this configuration, when a thrust is applied to the pulley face plate 20, the radial inner side (inner diameter side) of the pulley face plate 20 is deformed more preferentially. Therefore, the slip of the contact surface between the pulley face plate 20 (fixed pulley half 1) and the endless belt B can be suppressed more effectively.
  • FIG. 6 is a longitudinal sectional view of a drive pulley P1 included in a continuously variable transmission T according to a second embodiment of the present invention.
  • the drive pulley P1 included in the continuously variable transmission T according to the present embodiment has a clearance from an oil passage 12 formed in the rotation shaft 1k in addition to the configuration of the drive pulley P1 included in the continuously variable transmission T according to the first embodiment.
  • a communication passage 23 communicating with the portion 22 is provided, and the working oil from the oil passage 12 is supplied to the gap portion 22 through the communication passage 23.
  • the gap portion 22 of the present embodiment has a liquid-tight structure in which the hydraulic oil supplied from the oil passage 12 is accommodated without leaking.
  • the hydraulic oil supplied to the gap 22 exerts a buffer action against the deformation of the pulley face plate 20, whereby the inclination of the contact face of the pulley face plate 20 with the metal belt B can be further optimized. . Therefore, slippage between the metal belt B and the pulley face plate 20 can be reduced more effectively.
  • the hydraulic oil supplied from the oil passage 12 through the communication passage 23 exerts the above-described shock absorbing action, the rigidity of the pulley face plate 20 can be suppressed to a low level, so that the pulley face plate 20 can be thin. And weight reduction can be achieved.
  • FIG. 7 is a longitudinal sectional view of a drive pulley P1 included in a continuously variable transmission T according to a third embodiment of the present invention.
  • the drive pulley P1 included in the continuously variable transmission T according to the present embodiment includes the movable pulley half 2 on the fixed pulley half 1 side in addition to the configuration of the drive pulley P1 included in the continuously variable transmission T according to the first embodiment.
  • Another joining means) 31 and a clearance 32 formed between the movable pulley half 2 and the pulley face plate 30 are provided.
  • the pulley face plate 30 of the movable pulley half 2 is deformed toward the movable pulley half 2 so as to narrow the gap 32 between the pulley face plate 30 and the movable pulley half 2. .
  • the inclination of the contact surface of the movable pulley half 2 with the metal belt B in the pulley face plate 30 is made appropriate, and slippage between the metal belt B and the pulley face plate 30 is reduced. Therefore, the inclination of both the contact surface of the metal belt B and the fixed pulley half 1 and the contact surface of the metal belt B and the movable pulley half 2 is optimized, so that the slip of the metal belt B is more effective. Can be reduced.
  • FIG. 8 is a longitudinal sectional view of a drive pulley P1 included in a continuously variable transmission T according to a fourth embodiment of the present invention.
  • the drive pulley P1 included in the continuously variable transmission T according to the present embodiment is fixed from the oil passage 12 formed in the rotation shaft 1k in addition to the configuration of the drive pulley P1 included in the continuously variable transmission T according to the third embodiment.
  • a communication passage 23 communicating with the clearance 22 of the pulley half 1 is provided, and hydraulic fluid from the oil passage 12 is supplied to the clearance 22 through the communication passage 23.
  • the hydraulic oil supplied to the gap portion 22 of the fixed pulley half 1 exerts a buffer action against the deformation of the pulley face plate 20, whereby the contact of the pulley face plate 20 with the metal belt B. It is possible to further optimize the inclination of the surface. Therefore, the slippage between the metal belt B and the pulley face plate can be reduced more effectively.
  • the hydraulic oil supplied from the oil passage 12 through the communication passage 23 exerts the above-described shock absorbing action, the rigidity of the pulley face plate 20 can be suppressed to a low level, so that the pulley face plate 20 can be thin. And weight reduction can be achieved.
  • Reference Signs List 1 fixed pulley half 2 movable pulley 1 k rotary shaft 4 forward / backward switching mechanism 5 starting clutch 6 gear transmission mechanism 7 differential mechanism 8, 8 metal ring assembly 9 metal element 10 bearing 12 oil passage 20 pulley face plate (contact Element) 20c contact surface 21 pin (joint member) 22 Clearance 23 Communication passage A Hydraulic drive means B Metal belt (endless belt) C Pulley cover D Damper E Engine Ec Crankshaft ECU Electronic control unit G Belt groove P1 Drive pulley P2 Driven pulley Si Drive shaft (rotation shaft) So driven shaft T Metal belt type continuously variable transmission (belt type continuously variable transmission) U Hydraulic control unit W, W Drive wheel

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

Abstract

L'invention concerne une transmission à variation continue de type à courroie dans laquelle la perte de transmission de puissance est limitée de manière plus efficace par la réduction du glissement entre les surfaces de contact entre un demi-corps de poulie fixe contre une courroie sans fin. La poulie d'entraînement d'une transmission à variation continue de type à courroie est dotée des éléments suivants : un élément de contact en forme de plaque prévu sur la surface du demi-corps de poulie fixe, qui fait face au demi-corps de poulie mobile, et en contact avec une courroie sans fin; un moyen de jonction pour joindre l'élément de contact et le demi-corps de poulie fixe de manière à ce que l'élément de contact et le demi-corps de poulie fixe tournent ensemble; et un espace formé entre le demi-corps de poulie fixe et l'élément de contact. Lorsqu'une force de propulsion est appliquée sur le demi-corps de poulie mobile par le moyen d'entraînement, l'élément de contact se déforme vers le demi-corps de poulie fixe de manière à rétrécir l'espace. En conséquence, l'inclinaison des surfaces de contact est corrigée, et le glissement entre la courroie sans fin et l'élément de contact est réduit.
PCT/JP2015/083277 2014-12-01 2015-11-26 Transmission à variation continue de type à courroie WO2016088650A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2016562408A JP6379216B2 (ja) 2014-12-01 2015-11-26 ベルト式無段変速機

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JP2014243043 2014-12-01
JP2014-243043 2014-12-01

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WO2016088650A1 true WO2016088650A1 (fr) 2016-06-09

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6389458U (fr) * 1986-12-02 1988-06-10
JP2000337480A (ja) * 1999-05-17 2000-12-05 Luk Lamellen & Kupplungsbau Gmbh 伝動装置
JP2002106659A (ja) * 2000-10-03 2002-04-10 Fuji Heavy Ind Ltd ベルト式無段変速機およびその製造方法
JP2009150496A (ja) * 2007-12-21 2009-07-09 Toyota Central R&D Labs Inc ベルト式無段変速機及びそのプーリ

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JPS6389458U (fr) * 1986-12-02 1988-06-10
JP2000337480A (ja) * 1999-05-17 2000-12-05 Luk Lamellen & Kupplungsbau Gmbh 伝動装置
JP2002106659A (ja) * 2000-10-03 2002-04-10 Fuji Heavy Ind Ltd ベルト式無段変速機およびその製造方法
JP2009150496A (ja) * 2007-12-21 2009-07-09 Toyota Central R&D Labs Inc ベルト式無段変速機及びそのプーリ

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