JP2008232389A - Belt type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a belt type continuously variable transmission for preventing the lower productivity of a first movable sheave by facilitating the manufacture of the first movable sheave. <P>SOLUTION: In the belt type continuously variable transmission, a primary pulley 38 and a secondary pulley 39 are isolated from each other to form a distance W between a fixed sheave 40 and the outer peripheral end of the movable sheave 46, and an outer cylinder part 43B of the cylinder member 43 is installed between the movable sheave 41 and the fixed sheave 45. The movable sheave 41 includes: an inner cylinder part 41A provided encircling a primary shaft 32; a radiation part 41B molded integrally with the inner cylinder part 41A and protruded radially outward from the axial end of the inner cylinder part 41A; and a seal member 74 fitted in the radial outer peripheral end of the radiation part 41B. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a belt-type continuously variable transmission, and more particularly to a belt-type continuously variable transmission that can improve the productivity of a first movable sheave.

  Conventionally, a belt type continuously variable transmission (CVT) is known. As this type of belt-type continuously variable transmission, one shown in FIG. 6 is known (for example, see Patent Document 1).

  In FIG. 6, a primary pulley 111 of a belt-type continuously variable transmission includes a primary shaft 115 rotatably supported by a transmission case 112 via ball bearings 113 and 114, and a fixed sheave integrated with the primary shaft 115. 116, a movable sheave 117 mounted on the primary shaft 115 so as to be slidable in the axial direction and not to rotate relative to the axis, and a back surface of the movable sheave 117. A cylinder member 119 that defines the cylinder chamber 118 is provided, and the fixed sheave 116 and the movable sheave 117 are slid by sliding the movable sheave 117 as the oil flows into and out of the hydraulic cylinder chamber 118. The V-shaped pulley groove 128a formed by the inclined surfaces facing each other is made variable. It has become.

  The secondary pulley 120 of the belt-type continuously variable transmission includes a secondary shaft 123 that is rotatably supported by the transmission case 112 via ball bearings 121 and 122, and a fixed sheave 124 that is integrated with the secondary shaft 123. A movable sheave 125 mounted on the secondary shaft 123 so as to be slidable in the axial direction and so as not to rotate relative to the axis, and a cylinder member 127 defining a hydraulic cylinder chamber 126 between the back surface of the movable sheave 125; The movable sheave 125 is slid as the oil flows into and out of the hydraulic cylinder chamber 126, so that a V-shaped shape formed by the inclined surfaces of the fixed sheave 124 and the movable sheave 125 facing each other. The pulley groove 128b is made variable.

  Further, a transmission belt 129 is wound around the pulley groove 128a and the pulley groove 128b, and the movable sheave 117 and the movable sheave 125 are slid to increase / decrease the groove width of the pulley grooves 128a and 128b. Is configured to do.

  Specifically, the width of the pulley groove 128a of the primary pulley 111 is small (the pulley diameter is large), the width of the pulley groove 128b of the secondary pulley 120 is large (the pulley diameter is small), and the rotation speed of the secondary pulley 120 is the primary pulley 111. The pulley groove 128a of the primary pulley 111 is wide (the pulley diameter is small), the pulley groove 128b of the secondary pulley 120 is small (the pulley diameter is large), and the secondary pulley is increased in speed. Deceleration occurs when the rotational speed of 120 is lower than the rotational speed of the primary pulley 111.

  By the way, in the belt-type continuously variable transmission having such a configuration, the hydraulic cylinder chamber 126 of the secondary pulley 120 rotates at a high speed around the secondary shaft 123 at the time of acceleration, so that the hydraulic pressure generated by centrifugal force, so-called, The centrifugal oil pressure acts on the hydraulic cylinder chamber 126, and the hydraulic pressure in the hydraulic cylinder chamber 126 may become higher than the hydraulic pressure that is the control target.

  As a result, the clamping pressure of the transmission belt 129 increases more than necessary, and when performing a shift, the hydraulic pressure corresponding to the increased clamping pressure of the transmission belt 129 must be supplied to the hydraulic cylinder chamber 118. As a result, the controllability of shifting is reduced.

  In order to solve such a problem, the effective pressure receiving area of the hydraulic cylinder chamber 118 is set larger than the effective pressure receiving area of the hydraulic cylinder chamber 126, the centrifugal hydraulic pressure acting on the hydraulic cylinder chamber 126 is reduced, and the hydraulic cylinder chamber By applying an optimal hydraulic pressure to 118, the hydraulic pressure supplied to the hydraulic cylinder chamber 126 is prevented from becoming high.

  Further, it is necessary to prevent the outer shape of the movable sheave 117 from increasing in size by increasing the effective pressure receiving area of the hydraulic cylinder chamber 118. In order to satisfy such a requirement, a flange portion 117a extending toward the cylinder member 119 side and a piston portion 117b formed at the distal end in the extending direction of the flange portion 117a are provided at the outer peripheral end portion of the movable sheave 117. And an outer cylindrical portion 119a extending toward the movable sheave 117 is provided at the outer peripheral end portion of the cylinder member 119, and the piston portion 117b is slid along the inner peripheral surface of the outer cylindrical portion 119a. .

  Further, the flange portion 117 a needs to be provided because the outer tube portion 119 a interferes with the fixed sheave 124 without the flange portion 117 a. That is, the continuously variable transmission needs to protect the transmission belt 129 so that the bending radius of the transmission belt 129 does not become as small as possible when the pulley diameter is varied from the minimum transmission ratio to the maximum transmission ratio.

  For this reason, when using transmission belts having the same length, the primary pulley 111 and the secondary pulley 120 are arranged as close as possible, and the transmission belt when the pulley diameter changes from the minimum gear ratio to the maximum gear ratio. The bending radius of 129 can be set to be large.

  That is, when the primary pulley 111 and the secondary pulley 120 are arranged close to each other, the primary pulley 111 is set in a state in which the bending radius of the transmission belt 129 is increased in advance as compared with the case where the primary pulley 111 and the secondary pulley 120 are arranged apart from each other. 111 and the secondary pulley 120 can be wound around.

Therefore, in order to increase the bending radius of the transmission belt 129 without causing an increase in the outer shape of the movable sheave 117, a flange portion 117a is provided at the outer peripheral end of the movable sheave 117, and the outer cylinder portion 119a is connected to the fixed sheave 124. It is necessary to avoid interference.
The movable sheave 117 is generally integrally formed by forging including the flange portion 117a and the piston portion 117b (see, for example, Patent Document 2).
JP 2006-132550 A JP 2002-106658 A

  However, in such a conventional belt-type continuously variable transmission, since the movable sheave 117 is integrally formed by forging or the like, an operation of forming a long flange portion 117a on the outer peripheral end portion of the movable sheave 117 is performed. There is a problem that the productivity of the movable sheave 117 is lowered because it is troublesome.

  The present invention has been made to solve the conventional problems, and can prevent the productivity of the first movable sheave from being lowered by making it possible to easily manufacture the first movable sheave. It is an object of the present invention to provide a belt type continuously variable transmission capable of performing

  The belt type continuously variable transmission according to the present invention includes: (1) a first fixed sheave fixed to an input shaft; and the first fixed sheave facing the first fixed sheave in the axial direction of the input shaft and the input shaft. A primary pulley having a first movable sheave manufactured by integral molding, and a second pulley fixed to an output shaft disposed below the input shaft. A secondary pulley having a fixed sheave and a second movable sheave that is opposed to the second fixed sheave in the axial direction of the output shaft and is movable in the axial direction with respect to the output shaft; A V-shaped first pulley groove formed on the opposing surfaces of the first fixed sheave and the first movable sheave, and an opposing surface of the second fixed sheave and the second movable sheave. Winding around V-shaped second pulley groove A hydraulic cylinder chamber having a predetermined effective pressure receiving area is defined between the established transmission belt and a back surface opposite to the facing surface of the first movable sheave, and between the back surface of the first movable sheave. An effective pressure receiving area smaller than the predetermined effective pressure receiving area is provided between the first cylinder member and a back surface opposite to the facing surface of the second movable sheave, and between the back surface of the second movable sheave. A second cylinder member defining a hydraulic cylinder chamber, and an outer cylindrical portion extending toward the first movable sheave side is provided at a radially outer peripheral end portion of the first cylinder member, In the belt-type continuously variable transmission in which the radially outer peripheral end portion of the first movable sheave moves along the inner peripheral surface of the outer cylinder portion of the first cylinder member, the primary pulley and the secondary pulley are Installed separately, outside the above It is composed of parts from those installed between the second fixed sheave and said first movable sheave.

  With this configuration, the primary pulley and the secondary pulley are installed separately from each other, and the outer cylinder portion of the first cylinder member is installed between the first movable sheave and the second fixed sheave. It is possible to prevent the outer cylinder portion of the cylinder member and the second fixed sheave from interfering with each other.

  Further, since it is possible to prevent the outer cylinder portion of the first cylinder member and the second fixed sheave from interfering with each other, it is unnecessary to provide a flange portion at the radially outer peripheral end portion of the first movable sheave. The radial outer peripheral end of the first movable sheave can be slid along the inner peripheral surface of the outer cylinder portion of the first cylinder member.

  Therefore, the first movable sheave can be easily manufactured by integral molding by forging or the like, and the productivity of the first movable sheave can be prevented from being lowered.

  In the belt type continuously variable transmission according to the present invention, in (1), (2) the separation distance between the primary pulley and the secondary pulley is larger than the plate thickness of the outer cylinder portion of the first cylinder member. It is composed of what is a distance.

  With this configuration, since the separation distance between the primary pulley and the secondary pulley is made larger than the plate thickness of the outer cylinder portion of the first cylinder member, it is possible to prevent the outer cylinder portion from interfering with the second fixed sheave. The primary pulley and the secondary pulley can be smoothly rotated.

  In addition, by setting the separation distance between the primary pulley and the secondary pulley so that the bend radius of the transmission belt is not reduced between the maximum speed ratio and the minimum speed ratio, the primary pulley can be kept in a state where the bend radius of the transmission belt is increased in advance. The transmission belt can be protected by winding the transmission belt around the secondary pulley.

  In the belt-type continuously variable transmission according to the present invention, in (1) and (2), (3) the first movable sheave includes an inner cylindrical portion provided so as to surround the input shaft, A radiating portion provided integrally with the inner cylinder portion and projecting radially outward from an axial end portion of the inner cylinder portion; and a seal member fitted to a radially outer peripheral end portion of the radiating portion; The radially outer peripheral end portion is configured to move along the inner peripheral surface of the outer cylinder portion of the first cylinder member via the seal member.

  With this configuration, the movable sheave is configured with an inner cylinder portion provided so as to surround the input shaft and a radiation portion that is integrally formed with the inner cylinder portion and protrudes radially outward from the axial end portion of the inner cylinder portion. Therefore, the radiating portion can be formed in a substantially linear shape, and a long flange portion as in the prior art can be dispensed with. For this reason, the first movable sheave can be easily manufactured by integral molding by forging or the like, and the productivity of the first movable sheave can be prevented from being lowered.

  In the belt-type continuously variable transmission according to the present invention, in (1) to (3), (4) a radial outer peripheral end of the first movable sheave is formed in a planar shape, and the radial outer peripheral end It is comprised from what the recessed part by which the said sealing member is fitted is formed in a part.

  With this configuration, the radial outer peripheral end of the first movable sheave is formed in a flat shape, so that the holding portion of the seal member can be set by a single cutting process.

  The present invention provides a belt-type continuously variable transmission that can prevent the productivity of the first movable sheave from being lowered so that the first movable sheave can be easily manufactured. it can.

Embodiments of a belt-type continuously variable transmission according to the present invention will be described below with reference to the drawings.
1 to 5 are views showing an embodiment of a belt type continuously variable transmission according to the present invention.
First, the configuration will be described. FIG. 1 is a schematic configuration diagram showing a part of a vehicle 1 to which a belt-type continuously variable transmission according to the invention is applied. A vehicle 1 to which a belt-type continuously variable transmission according to this embodiment is applied is a so-called The vehicle is configured as an FF vehicle (front engine front drive: front-wheel drive vehicle for engine front), and includes an engine 2 as a drive source.

  As the engine 2, a gasoline engine, a diesel engine, an LPG engine, a hydrogen engine, a bi-fuel engine, or the like can be adopted. However, in the present embodiment, it is assumed that a gasoline engine is used as the engine 2.

  In FIG. 1, a vehicle 1 includes a transaxle 4 that is disposed on a side of an engine 2 that is installed horizontally and is connected to a crankshaft 3 of the engine 2, and the transaxle 4 includes a transaxle housing 5. The transaxle case 6 and the transaxle rear cover 7 are included. The transaxle case 6 and the transaxle rear cover 7 constitute a transmission case.

  The transaxle housing 5 is disposed on the side of the engine 2, and the transaxle case 6 is fixed to the opening end of the transaxle housing 5 opposite to the engine 2.

  The transaxle rear cover 7 is fixed to the opening end of the transaxle case 6 opposite to the transaxle housing 5. A torque converter 8 is disposed inside the transaxle housing 5, and a forward / reverse switching mechanism 9 and a belt type continuously variable transmission according to the present invention are disposed inside the transaxle case 6 and the transaxle rear cover 7. (Hereinafter simply referred to as CVT) 10 and a differential device 11 are arranged.

  The torque converter 8 includes a drive plate 12 and a front cover 13 fixed to the crankshaft 3 of the engine 2 via the drive plate 12, and a pump impeller 14 is attached to the front cover 13.

  The torque converter 8 includes a turbine runner 15 that can rotate while facing the pump impeller 14, and the turbine runner 15 is fixed to an input shaft 16 that extends substantially coaxially with the crankshaft 3.

  A stator 17 is arranged inside the pump impeller 14 and the turbine runner 15, and the rotation direction of the stator 17 is set only in one direction by the one-way clutch 18.

  A hollow shaft 19 is fixed to the stator 17 via a one-way clutch 18, and the input shaft 16 is inserted into the hollow shaft 19. A lock-up clutch 21 is attached to the end of the input shaft 16 on the front cover 13 side via a damper mechanism 20.

  The pump impeller 14, the turbine runner 15, and the stator 17 define a hydraulic fluid chamber. The hydraulic fluid chamber is operated by an oil pump 22 disposed between the torque converter 8 and the forward / reverse switching mechanism 9. Liquid is supplied.

  When the engine 2 is operated and the front cover 13 and the pump impeller 14 are rotated, the turbine runner 15 starts to be dragged by the flow of hydraulic fluid, and the stator 17 is connected to the pump impeller 14. When the rotational speed difference with the turbine runner 15 is large, the flow of hydraulic fluid is converted to a direction that assists the rotation of the pump impeller 14.

  By this operation, the torque converter 8 operates as a torque amplifier when the rotational speed difference between the pump impeller 14 and the turbine runner 15 is large, and operates as a fluid coupling when the rotational speed difference between the two becomes small. When the vehicle speed reaches a predetermined speed after the vehicle 1 starts, the lockup clutch 21 is operated, and the power transmitted from the engine 2 to the front cover 13 is mechanically and directly transmitted to the input shaft 16. Further, the fluctuation of the torque transmitted from the front cover 13 to the input shaft 16 is absorbed by the damper mechanism 20.

  The oil pump 22 provided between the torque converter 8 and the forward / reverse switching mechanism 9 includes a rotor 23, and the rotor 23 is connected to the pump impeller 14 via a hub 24. The hub 24 is spline-fitted to the hollow shaft 19, and the main body 25 of the oil pump 22 is fixed to the transaxle case 6 side. Therefore, the power of the engine 2 is transmitted to the rotor 23 via the pump impeller 14, thereby driving the oil pump 22.

  The forward / reverse switching mechanism 9 includes a planetary gear mechanism 26 of a double pinion type, and the planetary gear mechanism 26 is concentrically arranged on the outer peripheral side of the sun gear 27 and a sun gear 27 attached to an end of the input shaft 16 on the CVT 10 side. The arranged ring gear 28, the plurality of pinion gears 29 that mesh with the sun gear 27, the plurality of pinion gears 30 that mesh with both the ring gear 28 and the pinion gear 29, the pinion gears 29, 30 are rotatably held, and the pinion gear 29 , 30 are held in a state where they can revolve integrally around the sun gear 27.

  The carrier 31 of the forward / reverse switching mechanism 9 is fixed to a primary shaft 32 as an input shaft included in the CVT 10, and the power transmission path between the carrier 31 and the input shaft 16 is connected or disconnected using the forward clutch CR. It has come to be. The forward / reverse switching mechanism 9 has a reverse brake BR that controls the rotation and fixation of the ring gear 28.

  On the other hand, the CVT 10 includes a primary shaft 32 that extends substantially coaxially with the input shaft 16 and a secondary shaft 33 that is provided below the primary shaft 32 and extends parallel to the primary shaft 32.

  The primary shaft 32 is rotatably supported by a bearing 34 as a first bearing member and a bearing 35 as a second bearing member, and the secondary shaft 33 is a bearing 36 and a fourth bearing as third bearing members. It is rotatably supported by a bearing 37 as a bearing member. The primary shaft 32 is provided with a primary pulley 38, and the secondary shaft 33 is provided with a secondary pulley 39. Note that the bearings 34, 35, and 36 of the present embodiment are constituted by ball joints.

  The primary pulley 38 is fixed as a first fixed sheave 40 integrally formed on the outer peripheral portion of the primary shaft 32 and movable as a first movable sheave slidably mounted on the outer peripheral portion of the primary shaft 32. The fixed sheave 40 and the movable sheave 41 are opposed to each other, and a substantially V-shaped pulley groove 42 is formed between the fixed sheave 40 and the movable sheave 41 as a first pulley groove. ing.

  The movable sheave 41 is movable in the axial direction of the primary shaft 32 with respect to the fixed sheave 40, and the CVT 10 moves the movable sheave 41 in the axial direction of the primary shaft 32 to move the movable sheave 41 and the fixed sheave 40. Is provided with a cylinder member 43 as a first cylinder member for approaching and separating.

  The secondary pulley 39 is a fixed sheave 45 as a second fixed sheave integrally formed on the outer peripheral portion of the secondary shaft 33 and a second movable sheave slidably mounted on the outer peripheral portion of the secondary shaft 33. A movable sheave 46 is provided, the fixed sheave 45 and the movable sheave 46 are opposed to each other, and a substantially V-shaped pulley groove 47 is formed between the fixed sheave 45 and the movable sheave 46 as a second pulley groove. ing.

  The movable sheave 46 is movable in the axial direction of the secondary shaft 33 with respect to the fixed sheave 45. The CVT 10 moves the movable sheave 46 in the axial direction of the secondary shaft 33 to move the movable sheave 46 and the fixed sheave 45. A cylinder member 48 is provided as a second cylinder member that approaches and separates.

  Also, a pulley belt 42 of the primary pulley 38 and a pulley groove 47 of the secondary pulley 39 are wound around a transmission belt 49 composed of a large number of metal pieces and a plurality of steel rings. By separately controlling the hydraulic pressure by 48, the groove widths of the primary pulley 38 and the secondary pulley 39 are changed, and the winding radius of the transmission belt 49 is changed. As a result, the transmission ratio by the CVT 10 is set to a desired value, and the tension of the transmission belt 49 is adjusted.

  The bearing 36 that supports the secondary shaft 33 is fixed to the transaxle rear cover 7, and a parking gear 50 is provided between the bearing 36 and the secondary pulley 39.

  Further, a counter driven gear 51 is fixed to the outer peripheral portion of the secondary shaft 33 of the CVT 10 by spline fitting, and power is transmitted from the CVT 10 to the differential device 11 via the counter driven gear 51. .

  The differential device 11 includes an intermediate shaft 52 disposed in parallel with the secondary shaft 33, and the intermediate shaft 52 is supported by bearings 53 and 54, and the intermediate shaft 52 includes a counter of the secondary shaft 33. A counter driven gear 56 and a final drive gear 57 that mesh with the driven gear 51 are fixed.

  Further, the differential 11 includes a hollow differential case 58, and the differential case 58 is rotatably supported by bearings 59 and 60, and a ring gear 61 is formed on the outer peripheral portion of the differential case 58.

  The ring gear 61 is in mesh with the final drive gear 57 of the intermediate shaft 52. The differential case 58 has a pinion shaft 62 supported therein, and two pinion gears 63 are fixed to the pinion shaft 62.

  Each of the pinion gears 63 is engaged with two side gears 64, and a front drive shaft 65 is separately connected to each side gear 64. A wheel (front wheel) 66 is fixed to each front drive shaft 65. Yes.

  FIG. 2 is an enlarged cross-sectional view showing a main part of the CVT 10. In FIG. 2, the primary shaft 32 is rotatable about an axis, and a fixed sheave 40 is integrally formed at one end of the primary shaft 32.

  The primary shaft 32 is rotatably supported by a bearing 35 fixed to the transaxle case 6 outside the fixed sheave 40 and rotated by a bearing 34 fixed to the transaxle rear cover 7 outside the movable sheave 41. It is supported freely.

  In addition, an oil passage 71 is formed in the primary shaft 32 in the axial direction, and the oil passage 71 communicates with a hydraulic circuit of a hydraulic control device (not shown). The primary shaft 32 is formed with an oil passage 72 that penetrates in the radial direction toward the outer peripheral surface of the primary shaft 32 and communicates with the oil passage 71.

  On the other hand, the movable sheave 41 is provided so as to surround the primary shaft 32, and is movable along the outer peripheral surface of the primary shaft 32, and the radial direction of the primary shaft 32 from the axial end of the inner cylinder portion 41A. And a radiation portion 41B continuously formed outward, and the movable sheave 41 is manufactured by being integrally formed by forging or the like.

  In addition, an oil passage 73 that penetrates from the inner peripheral surface of the inner cylinder portion 41A to the outer peripheral surface is formed in the inner cylindrical portion 41A. The oil passage 73 and the oil passage 72 are formed on the outer peripheral surface of the primary shaft 32. It communicates via the formed spline part.

  That is, the inner cylindrical portion 41A of the movable sheave 41 and the primary shaft 32 are spline-coupled, and the primary shaft 32 and the movable sheave 41 are smoothly and relatively movable in the axial direction. The primary shaft 32 and the movable sheave 41 are connected so that they do not move relative to each other in the circumferential direction.

  In addition, inclined surfaces 40a and 41a are formed on the opposed surfaces of the fixed sheave 40 and the radiating portion 41B of the movable sheave 41, respectively, and a V-shaped pulley groove 42 is formed by the inclined surfaces 40a and 41a. A transmission belt 49 is wound around 42.

  The cylinder member 43 is provided on the back surface of the movable sheave 41 opposite to the inclined surface 41a. The cylinder member 43 extends from the outer peripheral portion of the primary shaft 32 between the bearing 34 and the movable sheave 41 to the outer side in the radial direction of the primary shaft 32, and the radiating portion 43 </ b> A is bent at the radial center. An outer cylinder 43B extending toward the fixed sheave 40 along the axial direction of the primary shaft 32 from the outer peripheral end of the hydraulic cylinder chamber 75 between the cylinder member 43 and the back surface of the movable sheave 41. It is made.

  The inner edge portion of the radiating portion 43 </ b> A of the cylinder member 43 is positioned and fixed to the primary shaft 32 by being sandwiched between the bearing 34 and the stepped portion 32 a of the primary shaft 32.

  Further, a sealing member 74 slidably in contact with the inner peripheral surface of the outer cylindrical portion 43B of the cylinder member 43 is fitted to the radial outer peripheral end portion 41b of the radiating portion 41B of the movable sheave 41. When moving along the axial direction, the radial outer peripheral end 41b of the radiating portion 41B slides along the inner peripheral surface of the outer cylindrical portion 43B of the cylinder member 43 via the seal member 74. Yes.

  In the primary pulley 38 having such a configuration, the hydraulic oil in the hydraulic cylinder chamber 75 is controlled by supplying the hydraulic oil into the hydraulic cylinder chamber 75 via the oil passages 71, 72, 73 from the hydraulic circuit of the hydraulic control device. Thus, the desired transmission ratio can be obtained by moving the movable sheave 41 relative to the fixed sheave 40 and changing the winding radius of the transmission belt 49.

  On the other hand, the secondary shaft 33 is rotatable about an axis, and a fixed sheave 45 is integrally formed at one end of the secondary shaft 33.

  The secondary shaft 33 is rotatably supported by a bearing 36 fixed to the transaxle rear cover 7 outside the fixed sheave 45, and a parking gear 50 is integrally provided on the outer periphery of the fixed sheave 45. Yes.

  An oil passage 77 is formed in the secondary shaft 33 in the axial direction. The oil passage 77 communicates with a hydraulic circuit of a clamping pressure control device that controls the clamping pressure of the transmission belt 49 (not shown). The secondary shaft 33 is formed with an oil passage 78 extending outward in the radial direction of the secondary shaft 33, and the oil passage 78 communicates with the oil passage 77.

  The movable sheave 46 includes an inner cylindrical portion 46A that is movable along the outer peripheral surface of the secondary shaft 33, and a radiating portion 46B that is formed continuously from the inner cylindrical portion 46A outward in the radial direction of the secondary shaft 33. And an outer cylindrical portion 46C that is continuous with the outer peripheral end of the radiating portion 46B and extends from the outer peripheral end of the radiating portion 46B toward the counter driven gear 51 along the axial direction of the secondary shaft 33.

  Further, the inner cylindrical portion 46A of the movable sheave 46 and the secondary shaft 33 are spline-coupled, and the secondary shaft 33 and the movable sheave 46 are relatively movable in the axial direction smoothly. The secondary shaft 33 and the movable sheave 46 are connected so that they do not move relative to each other in the circumferential direction.

  In addition, inclined surfaces 45a and 46b are formed on the opposed surfaces of the fixed sheave 45 and the radiating portion 46B of the movable sheave 46, respectively, and a V-shaped pulley groove 47 is formed by these inclined surfaces 45a and 46b. A transmission belt 49 is wound around 47.

  The cylinder member 48 is provided on the back surface of the movable sheave 46 opposite to the inclined surface 46b. The cylinder member 48 includes a first radiating portion 48A extending outward in the radial direction of the secondary shaft 33, a cylindrical portion 48B extending substantially parallel to the axial direction of the secondary shaft 33 from the first radiating portion 48A, A second radiating portion 48C that inclines toward the back surface of the movable sheave 46 from the tubular portion 48B and extends radially outward of the secondary shaft 33, and extends from the second radiating portion 48C to the radial outward direction of the secondary shaft 33. A third radiating portion 48 </ b> D is provided, and a hydraulic cylinder chamber 80 is defined between the cylinder member 48 and the back surface of the movable sheave 46.

  Further, a seal member 81 that is in sliding contact with the inner peripheral surface of the outer cylindrical portion 46C of the movable sheave 46 is fitted to the outer edge portion of the third radiating portion 48D of the cylinder member 48, and the movable sheave 46 is the axis of the secondary shaft 33. When moving along the direction, the third radiating portion 48D slides along the inner peripheral surface of the outer cylindrical portion 46C of the movable sheave 46 via the seal member 81.

  A spring 82 is interposed in the hydraulic cylinder chamber 80. One end of the spring 82 abuts on the cylinder member 48 and the other end abuts on the movable sheave 46. The movable sheave 46 is connected to the fixed sheave 45 side. The initial thrust is imparted to the transmission belt 49 by pressing the belt.

  The inner end edge of the cylinder member 48 is sandwiched between a sleeve 79 fitted to the outer peripheral portion of the secondary shaft 33 and a step portion 33a of the secondary shaft 33. The cylinder member 48 is sandwiched between the sleeve 79 and the step portion 33a. Positioned and fixed to 33.

  In the secondary pulley 39 having such a configuration, hydraulic oil is supplied from the hydraulic circuit of the clamping pressure control device into the hydraulic cylinder chamber 80 via the oil passages 77 and 78 to control the hydraulic pressure in the hydraulic cylinder chamber 80. Thus, the desired gear ratio can be obtained by moving the movable sheave 46 relative to the fixed sheave 45 and changing the winding radius of the transmission belt 49.

  On the other hand, the magnitude relationship between the effective pressure receiving area P1 of the hydraulic cylinder chamber 75 and the effective pressure receiving area P2 of the hydraulic cylinder chamber 80 is P1> P2, and the hydraulic receiving surface of the radiating portion 41B of the movable sheave 41 is radiated by the movable sheave 46. The area is larger than the hydraulic pressure receiving surface of the portion 46B.

  Therefore, in order to prevent the outer shape of the movable sheave 41 of the present embodiment from increasing in size, the radially outer peripheral end portion 41b of the radiating portion 41B of the movable sheave 41 is replaced with the inner peripheral portion of the outer cylindrical portion 43B of the cylinder member 43. The hydraulic cylinder chamber 75 is defined between the movable sheave 41 and the cylinder member 43 using the entire movable sheave 41.

  Further, when the hydraulic cylinder chamber 75 rotates at a high speed around the secondary shaft 39 when the secondary shaft 39 is accelerated, centrifugal hydraulic pressure acts on the hydraulic cylinder chamber 75, and the clamping pressure of the transmission belt 49 increases more than necessary. Therefore, in the present embodiment, the effective pressure receiving area P1 of the hydraulic cylinder chamber 75 is made larger than the effective pressure receiving area P2 of the hydraulic cylinder chamber 80.

  For this reason, the moving force of the movable sheave 41 can be increased only by supplying the optimum hydraulic pressure to the hydraulic cylinder chamber 75, and the movable sheave 41 can be easily moved against the increased clamping force of the transmission belt 49. Can be made.

  On the other hand, the primary pulley 38 and the secondary pulley 39 are installed so that the outer peripheral ends of the fixed sheave 40 and the movable sheave 46 are separated by a distance W, and the outer cylinder portion 43B of the cylinder member 43 is connected to the movable sheave 41 and the fixed sheave 45. , That is, within the range of the distance W.

  The distance W between the outer peripheral end portions of the fixed sheave 40 and the movable sheave 46 is set to be larger than the plate thickness of the outer cylinder portion 43B of the cylinder member 43. In the present embodiment, the distance W of the outer cylinder portion 43B is set. The distance W is set to about twice.

  Further, when the transmission belts having the same length are used, when the distance W increases, the transmission belt 49 is wound around the transmission belt 49 from the minimum transmission ratio to the maximum transmission ratio. Since the winding radius becomes small, a load is applied to the transmission belt 49 and the durability of the transmission belt 49 may be deteriorated.

  Therefore, the distance W is such that no load is applied to the transmission belt 49 when the winding radius of the transmission belt 49 changes from the minimum transmission ratio to the maximum transmission ratio, that is, the winding radius (bending radius) of the transmission belt 49 is By setting the distance so as not to decrease, the transmission belt 49 can be protected by winding the transmission belt 49 around the primary pulley 38 and the secondary pulley 39 in a state where the bending radius of the transmission belt 49 is increased in advance. .

  As described above, in the present embodiment, the primary pulley 38 and the secondary pulley 39 are separated from each other so that the distance W is formed between the outer peripheral ends of the fixed sheave 40 and the movable sheave 46. Since the cylinder part 43B is installed between the movable sheave 41 and the fixed sheave 45, it is possible to prevent the outer cylinder part 43B of the cylinder member 43 and the fixed sheave 45 from interfering with each other as in the prior art.

  Further, since it is possible to prevent the outer cylindrical portion 43B of the cylinder member 43 and the fixed sheave 45 from interfering with each other, a flange portion is provided on the radial outer peripheral end portion 41b of the radiating portion 41B of the movable sheave 41 as in the prior art. The radial outer peripheral end 41b of the radiating portion 41B of the movable sheave 41 can be slid along the inner peripheral surface of the outer cylindrical portion 43B of the cylinder member 43. Therefore, the movable sheave 41 can be easily manufactured by integral molding by forging or the like, and the productivity of the movable sheave 41 can be prevented from being lowered.

  In particular, in the present embodiment, the distance W between the primary pulley 38 and the secondary pulley 39 is set to a distance larger than the plate thickness of the outer cylinder portion 43B of the cylinder member 43. Therefore, the outer cylinder portion 43B of the cylinder member 43 Can be reliably prevented from interfering with the fixed sheave 45, and the primary pulley 38 and the secondary pulley 39 can be smoothly rotated.

  Further, the transmission belt 49 can be protected by setting the separation distance between the primary pulley 38 and the secondary pulley 39 so that the bending radius of the transmission belt 49 does not become small.

  In addition, the movable sheave 41 of the present embodiment includes an inner cylinder portion 41A provided so as to surround the primary shaft 32, and an outer cylindrical portion formed integrally with the inner cylinder portion 41A and radially outward from the axial end portion of the inner cylinder portion 41A. Since the radiating portion 41B projecting in the direction and the sealing member 74 fitted to the radially outer peripheral end portion 41b of the radiating portion 41B are configured, the radiating portion 41B can be formed in a substantially linear shape. For this reason, the movable sheave 41 can be easily manufactured by integral molding by forging or the like, and the productivity of the movable sheave 41 can be prevented from being lowered.

  In the present embodiment, the seal member 74 is fitted to the radial outer peripheral end portion 41b of the radiating portion 41B of the movable sheave 41, and when the holding portion of the seal member 74 is formed, FIG. As shown in FIG. 4, after the radial outer peripheral end 41b of the radiating portion 41B is cut by the cutting surface C1 to form the radial outer peripheral end 41b of the seal member 74, the upper surface of the radial outer peripheral end 41b is planarized. Cutting is performed (the cut surface is indicated by C2), and the recess 91 is formed at the radially outer peripheral end portion so that the seal member 74 is fitted into the recess 91. For this reason, the cutting process until it cuts the recessed part 91 in the radial direction outer peripheral edge part 41b will be two processes.

  On the other hand, as shown in FIGS. 4 and 5, the radial outer peripheral end 41c of the radiating portion 41B of the movable sheave 41 is formed in a flat shape, and the sealing member 74 is fitted to the radial outer peripheral end 41c. If the recessed portion 92 to be formed is formed, the cutting process until the recessed portion 92 is cut can be made into one step (the cutting surface is indicated by C3), and the workability of the manufacturing operation of the movable sheave 41 is improved. Can be made.

  In addition, the embodiment disclosed this time is illustrative in all respects and is not limited to this embodiment. The scope of the present invention is shown not by the above description of the embodiments but by the scope of the claims, and is intended to include all modifications within the meaning and scope equivalent to the scope of the claims.

  As described above, the belt-type continuously variable transmission according to the present invention can easily manufacture the first movable sheave and prevent the productivity of the first movable sheave from decreasing. This is useful as a belt-type continuously variable transmission or the like that can improve the productivity of the first movable sheave.

1 is a diagram showing an embodiment of a belt-type continuously variable transmission according to the present invention, and is a schematic configuration diagram of a vehicle power transmission device including a belt-type continuously variable transmission. BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows one Embodiment of the belt-type continuously variable transmission which concerns on this invention, and is sectional drawing of a belt-type continuously variable transmission. It is a figure which shows one Embodiment of the belt type continuously variable transmission which concerns on this invention, and is an enlarged view of the radial direction outer peripheral end part of a movable sheave. It is a figure which shows one Embodiment of the belt-type continuously variable transmission which concerns on this invention, and is sectional drawing of the belt-type continuously variable transmission of another structure. FIG. 5 is an enlarged view of the radially outer peripheral end portion of the movable sheave of the belt type continuously variable transmission shown in FIG. 4. It is sectional drawing of the conventional belt-type continuously variable transmission.

Explanation of symbols

10 CVT (Belt-type continuously variable transmission)
38 Primary pulley 39 Secondary pulley 40 Fixed sheave (first fixed sheave)
41 Movable sheave (first movable sheave)
41A Inner cylinder part 41b, 41c Radial direction outer peripheral end 42 Pulley groove (first pulley groove)
43 Cylinder member (first cylinder member)
43B Radiation part 45 Fixed sheave (second fixed sheave)
46 Movable sheave (second movable sheave)
47 Pulley groove (second pulley groove)
48 Cylinder member (second cylinder member)
49 Transmission belt 74 Seal member 91, 92 Recess

Claims (4)

A first fixed sheave fixed to the input shaft, and opposed to the first fixed sheave in the axial direction of the input shaft and movable in the axial direction with respect to the input shaft. A primary pulley having a first movable sheave manufactured;
A second fixed sheave fixed to the output shaft disposed below the input shaft; and an axial direction of the output shaft opposed to the second fixed sheave in the axial direction of the output shaft. A secondary pulley having a second movable sheave provided movably in a direction;
A V-shaped first pulley groove formed on the opposing surfaces of the first fixed sheave and the first movable sheave, and an opposing surface of the second fixed sheave and the second movable sheave. A transmission belt wound around a V-shaped second pulley groove;
A first cylinder member provided on a back surface opposite to the opposing surface of the first movable sheave and defining a hydraulic cylinder chamber having a predetermined effective pressure receiving area with the back surface of the first movable sheave;
A hydraulic cylinder chamber having an effective pressure receiving area smaller than the predetermined effective pressure receiving area is defined between the second movable sheave and the back surface opposite to the opposing surface of the second movable sheave. A second cylinder member;
An outer cylindrical portion extending toward the first movable sheave side is provided at a radially outer peripheral end portion of the first cylinder member, and a radially outer peripheral end portion of the first movable sheave is the first movable sheave. In the belt-type continuously variable transmission configured to move along the inner peripheral surface of the outer cylinder portion of the cylinder member,
A belt-type continuously variable transmission characterized in that the primary pulley and the secondary pulley are spaced apart and the outer cylinder portion is disposed between the first movable sheave and the second fixed sheave. 2. The belt-type continuously variable transmission according to claim 1, wherein a separation distance between the primary pulley and the secondary pulley is greater than a plate thickness of an outer cylinder portion of the first cylinder member. The first movable sheave includes an inner cylindrical portion provided so as to surround the input shaft, and is provided integrally with the inner cylindrical portion and protrudes radially outward from an axial end portion of the inner cylindrical portion. And a sealing member fitted to the radially outer peripheral end of the radiating portion,
The belt-type continuously variable transmission according to claim 1, wherein the radially outer peripheral end portion moves along the inner peripheral surface of the outer cylinder portion of the first cylinder member via the seal member. The radial outer peripheral end portion of the first movable sheave is formed in a flat shape, and a concave portion in which the seal member is fitted is formed in the radial outer peripheral end portion. The belt type continuously variable transmission according to any one of claims 3 to 4.

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