JP2008267420A - Continuously variable transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a continuously variable transmission device using an oil trapping member for trapping lubricating oil without lowering the power transmitting efficiency of a transmission. <P>SOLUTION: The continuously variable transmission device comprises the toroidal type continuously variable transmission and a planetary gear mechanism, wherein the oil trapping member 300 is supported by a carrier for trapping the lubricating oil to be splashed and supplied onto the planetary gear mechanism. The oil trapping member 300 has fins 300a for producing component force F in a rotating direction R of the carrier from the colliding force of the oil colliding with the oil trapping member 300. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a continuously variable transmission provided with a toroidal continuously variable transmission that can be used in transmissions of automobiles and various industrial machines.

  4 and 5 show a geared-neutral type continuously variable transmission in which a double cavity type toroidal continuously variable transmission used as a transmission for an automobile is incorporated. This continuously variable transmission is configured by combining a toroidal type continuously variable transmission 47 and first to third planetary gear type transmission units 48, 49, 50, and has a circular tubular input shaft 18, an output shaft 51, Have A transmission shaft 52 is provided between the input shaft 18 and the output shaft 51 so as to be concentric with the shafts 18 and 51 and to be rotatable relative to the shafts 18 and 51. The first and second planetary gear type transmission units 48 and 49 are stretched between the input shaft 18 and the transmission shaft 52, and the third planetary gear type transmission unit 50 is provided with the output shaft 51 and the transmission shaft 52. Are provided in a state of being spanned between each.

  Of these, the toroidal-type continuously variable transmission 47 includes input-side disks 2A and 2B and an integrated output-side disk 53 supported around the input shaft 18 so as to be freely rotatable and axially displaceable. . Both ends of the output side disk 53 in the axial direction are rotatably supported by rolling bearings such as a pair of thrust angular ball bearings 57 and 57.

  As shown in FIG. 5, inside the casing 59 in which the toroidal-type continuously variable transmission 47 is housed, a pair that swings about pivots (tilting shafts) 5, 5 that are twisted with respect to the input shaft 18. Trunnions 6 and 6 are provided. Each trunnion 6, 6 is a pair of bent wall portions 8, 8 formed at both ends in the longitudinal direction (vertical direction in FIG. 5) of the support plate portion 7 so as to be bent toward the inner surface side of the support plate portion 7. The end portions of these bent wall portions 8 and 8 are connected by connecting members 54 and 54. The bent wall portions 8 and 8 form a concave pocket portion P for accommodating the power roller 11 in the trunnion 6. Further, the pivot shafts 5 and 5 are concentrically provided on the outer side surfaces (surfaces opposite to the support plate portion 7) of the bent wall portions 8 and 8, respectively.

  A circular hole 10 is formed in the central portion of the support plate portion 7, and the base end portion 9 a of the displacement shaft 9 is supported in the circular hole 10. Then, by swinging each trunnion 6, 6 about each pivot 5, 5, the inclination angle of the displacement shaft 9 supported at the center of each trunnion 6, 6 can be adjusted. Further, a power roller 11 is rotatably supported around the tip end portion 9b of the displacement shaft 9 protruding from the inner surface of each trunnion 6, 6, and each power roller 11, 11 is connected to the input side disk 2A, 2B and the output side disk 53. In addition, the base end part 9a and the front-end | tip part 9b of each displacement axis | shaft 9 and 9 are mutually eccentric.

  Both ends of the pair of trunnions 6, 6 are supported so as to be swingable and displaceable in the axial direction (vertical direction in FIG. 5) with respect to the pair of yokes 23A, 23B. These yokes 23A and 23B are supported by a pair of support columns 61 and 61. That is, the upper yoke 23 </ b> A is movably supported by the spherical post 64 of the support 61 and the connecting plate 65 that supports the post. The lower yoke 23B is movably supported by the spherical post 68 of the support 61 and the upper cylinder body 60 that supports the post. The input shaft 18 is inserted through the insertion hole 63 formed at the center of the column 61. Further, as described above, the circular hole 10 formed in the central portion of the support plate portion 7 constituting each trunnion 6, 6 has a displacement shaft in which the base end portion 9 a and the tip end portion 9 b are parallel to each other and eccentric. 9, a base end portion 9a is rotatably supported. A power roller 11 is rotatably supported around the distal end portion 9b of each displacement shaft 9 protruding from the inner side surface of each support plate portion 7.

  The pair of displacement shafts 9 and 9 provided for each pair of trunnions 6 and 6 are provided at positions 180 degrees opposite to the input shaft 18. Further, the direction in which the distal end portion 9b of each of the displacement shafts 9 and 9 is eccentric with respect to the base end portion 9a is the same as the rotation direction of the input side disks 2A and 2B and the output side disk 53 (FIG. 5). In the upside down direction). The eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 18 is disposed. Accordingly, the power rollers 11 and 11 are supported so that they can be slightly displaced in the longitudinal direction of the input shaft 18. As a result, even when each of the power rollers 11 and 11 tends to be displaced in the axial direction of the input shaft 18 due to elastic deformation of each component member based on a thrust load generated by the pressing device 23a described later, This displacement is absorbed without applying an excessive force to each component member.

  In addition, a thrust rolling bearing is provided between the outer surface of each power roller 11, 11 and the inner surface of the support plate portion 7 constituting each trunnion 6, 6 in order from the outer surface side of the power roller 11. A ball bearing 24 and a thrust needle bearing 25 are provided. Among these, the thrust ball bearing 24 supports the rotation of each power roller 11 while supporting the load in the thrust direction applied to each power roller 11. Each of the thrust ball bearings 24 is composed of a plurality of balls 26, 26, an annular retainer 27 for holding the balls 26, 26 in a freely rolling manner, and an annular outer ring 28. ing. Further, the inner ring raceway of each thrust ball bearing 24 is formed on the outer side surface of each power roller 11, and the outer ring raceway is formed on the inner side surface of each outer ring 28.

  Further, the thrust needle bearing 25 is sandwiched between the inner surface of the support plate portion 7 constituting each trunnion 6, 6 and the outer surface of the outer ring 28. Such a thrust needle bearing 25 supports the thrust load applied to each outer ring 28 from each power roller 11, and each power roller 11 and outer ring 28 swings and displaces around the base end portion 9 a of each displacement shaft 9. Allow to do.

  Further, a drive rod (trunnion shaft) 29 is provided at one end (the lower end in FIG. 5) of each trunnion 6, 6, and a drive piston (hydraulic piston) 30 is provided on the outer peripheral surface of the intermediate portion of each drive rod 29. Is fixed. Each of these drive pistons 30 is oil-tightly fitted in the drive cylinder 31 to constitute a hydraulic drive device. In this case, the drive cylinder (cylinder body) 31 is formed by the upper cylinder body 60 and the lower cylinder body 62.

  A cable support 100 is integrally attached to the outer periphery of the drive rod 29 below the trunnions 6 and 6 in the vicinity of the yoke 23B. In addition, a synchronous cable 102 for transmitting the operation of one trunnion 6 to the other trunnion 6 is hung around the outer periphery of the cable support 100.

  Further, a crankshaft of an engine (not shown) as a drive source (not shown) is coupled to a base end portion (left end portion in FIG. 4) of the input shaft 18 via a drive shaft 72, and the input shaft 18 is rotationally driven by the crankshaft. It is supposed to be. Further, rolling contact portions (traction) between the inner side surfaces 2a and 2b of both the input side disks 2A and 2B and both axial side surfaces (inner side surfaces) 53a and 53a of the output side disk 53 and the peripheral surface 11a of the power rollers 11 and 11 As the pressing device 23a for applying an appropriate surface pressure to the part), a hydraulic device is used. In addition, an oil pump (not shown) which is a hydraulic source built in the front end wall 73 of the casing 59 is used to displace the pressing device 23a and the drive cylinder 31, the low speed clutch 44a and the high speed clutch for displacing the trunnions 6 and 6 for shifting. Pressure oil can be supplied to a hydraulic cylinder for connecting and disconnecting 45a.

  Further, the base end portion (left side in FIG. 4) of the hollow rotary shaft 75 is spline-coupled to the output side disk 53. The hollow rotary shaft 75 is inserted inside the input side disk 2B on the side far from the engine (right side in FIG. 4) so that the rotational force of the output side disk 53 can be taken out freely. A first sun gear 76 for constituting the first planetary gear type transmission unit 48 is fixed to a portion protruding from the outer surface of the input side disk 2B at the front end portion (right end portion in FIG. 5) of the hollow rotating shaft 75. is doing.

  In addition, the first carrier 77 is provided so as to be passed between the portion protruding from the hollow rotary shaft 75 at the tip end portion (right end portion in FIG. 4) of the input shaft 18 and the input side disk 2B, and this input side. The disk 2B and the input shaft 18 rotate in synchronization with each other. Then, first and second planetary gear type transmission units 48, each of which is a double pinion type, are disposed at equal circumferentially spaced positions (generally 3 to 4 positions) on both axial sides of the first carrier 77. 49, planetary gears 78, 79, 80 for constituting 49 are rotatably supported. Further, a first ring gear 81 is rotatably supported around one half of the first carrier 77 (the right half in FIG. 5).

  The first carrier 77 includes an intermediate support plate 242 having an L-shaped cross section and an annular shape as a whole, and first and second connecting plates each formed in an annular shape, as shown in an enlarged view in FIG. A plurality of (for example, three) first and second planetary shafts 245 and 246 are provided between the first and second connecting plates 243 and 244, respectively. (Three) third planetary shafts 247 are stretched over each other. The planetary gears 78, 79, and 80 are rotatably supported around the planetary shafts 245, 246, and 247 through radial needle bearings 248a, 248b, and 248c, respectively.

  Among the planetary gears 78, 79, 80, the planetary gear 78 provided on the inner side in the radial direction of the first carrier 77 near the toroidal type continuously variable transmission 47 (leftward in FIG. 4) is connected to the first sun gear 76. Meshed. The planetary gear 79 provided on the inner side in the radial direction of the first carrier 77 on the side far from the toroidal-type continuously variable transmission 47 (right side in FIG. 4) is the base end portion (left end portion in FIG. 4) of the transmission shaft 52. Is engaged with the second sun gear 82. Further, the remaining planetary gear 80 provided on the outer side in the radial direction of the first carrier 77 has a larger axial dimension than the planetary gears 78 and 79 provided on the inner side, and meshes with both the planetary gears 78 and 79. I am letting. Further, the remaining planetary gear 80 and the first ring gear 81 are engaged with each other. Instead of making the radially outward planetary gears independent of each other between the first and second planetary gear type transmission units 48 and 49, a structure in which a wide ring gear is engaged with both planetary gears is also adopted. Is possible. The first carrier 77 is rotatably supported to support the planetary gears 78, 79, 80 so as to be revolved and rotated with respect to the sun gears 81, 82.

  On the other hand, the second carrier 83 for constituting the third planetary gear type transmission unit 50 is coupled and fixed to the base end portion (left end portion in FIG. 4) of the output shaft 51. The second carrier 83 and the first ring gear 81 are coupled via a low speed clutch 44a. Further, a third sun gear 84 is fixed to the portion near the tip of the transmission shaft 52 (near the right end in FIG. 4). A second ring gear 85 is disposed around the third sun gear 84, and a high speed clutch 45a is provided between the second ring gear 85 and a fixed portion such as the casing 59. Further, a reciprocal set of planetary gears 86 and 87 arranged between the second ring gear 85 and the third sun gear 84 are rotatably supported by the second carrier 83. These planetary gears 86 and 87 mesh with each other, the planetary gear 86 provided on the inner side in the radial direction of the second carrier 83 is used as the third sun gear 84, and the planetary gear 87 provided on the outer side is used as the second ring gear. 85, respectively.

  In the case of the continuously variable transmission configured as described above, the power transmitted from the input shaft 18 to the integrated output-side disk 53 via the pair of input-side disks 2A and 2B and the power rollers 11 and 11 is a hollow rotation. It is taken out through the shaft 75. In the state where the low speed clutch 44a is connected and the high speed clutch 45a is disconnected, the speed ratio of the toroidal-type continuously variable transmission unit 47 is changed so that the rotational speed of the input shaft 18 remains constant. The rotational speed of the shaft 51 can be freely converted into forward rotation and reverse rotation with the stop state interposed therebetween. That is, in this state, the differential component between the first carrier 77 that rotates in the forward direction together with the input shaft 18 and the first sun gear 76 that rotates in the reverse direction together with the hollow rotation shaft 75 is generated from the first ring gear 81. It is transmitted to the output shaft 51 through the low speed clutch 44 a and the second carrier 83. In this state, the output shaft 51 is stopped by setting the transmission ratio of the toroidal continuously variable transmission 47 to a predetermined value, and the transmission ratio of the toroidal continuously variable transmission 47 is increased from the predetermined value to the speed increasing side. By changing it, the output shaft 51 is rotated in the direction in which the vehicle moves backward. On the other hand, by changing the gear ratio of the toroidal-type continuously variable transmission 47 from the predetermined value to the deceleration side, the output shaft 51 is rotated in the direction in which the vehicle moves forward.

  Further, in a state where the low speed clutch 44a is disconnected and the high speed clutch 45a is connected, the output shaft 51 is rotated in the direction of moving the vehicle forward. That is, in this state, according to the differential component between the first carrier 77 rotating in the forward direction together with the input shaft 18 and the first sun gear 76 rotating in the opposite direction to the first carrier 77 together with the hollow rotating shaft 75. The rotation of the planetary gear 78 of the rotating first planetary gear type transmission unit 48 is transmitted to the planetary gear 79 of the second planetary gear type transmission unit 49 via another planetary gear 80 and via the second sun gear 82. Then, the transmission shaft 52 is rotated. The third sun gear 84 provided at the tip of the transmission shaft 52, and the second ring gear 85 and the planetary gears 86 and 87 that constitute the third planetary gear type transmission unit 50 together with the third sun gear 84. Based on the meshing, the second carrier 83 and the output shaft 51 coupled to the second carrier 83 are rotated in the forward direction. In this state, the rotational speed of the output shaft 51 can be increased as the speed ratio of the toroidal-type continuously variable transmission 47 is changed to the speed increasing side.

  In the toroidal type continuously variable transmission 47 incorporated in such a continuously variable transmission, when changing the rotational speed ratio between the input shaft 18 and the output gear, the pair of drive pistons 30 and 30 are moved in opposite directions. Displace to. As the drive pistons 30 and 30 are displaced, the pair of trunnions 6 and 6 are displaced in directions opposite to each other. As a result, the peripheral surfaces 11a and 11a of the power rollers 11 and 11 act on the abutting portions between the inner side surfaces 2a and 2b of the input side disks 2A and 2B and the axial side surfaces 53a and 53a of the output side disk 53. The direction of the tangential force changes. As the force changes, the trunnions 6 and 6 swing in directions opposite to each other about the pivots 5 and 5 pivotally supported by the support plates 23 and 23.

  As a result, the contact positions between the peripheral surfaces 11a, 11a of the power rollers 11, 11 and the inner surfaces 2a, 2b, 53a change, and the rotational speed ratio between the input shaft 18 and the output gear changes. When the torque transmitted between the input shaft 18 and the output gear fluctuates and the amount of elastic deformation of each component changes, the power rollers 11 and 11 and the outer ring 28 attached to the power rollers 11 The displacement shaft 9 is slightly rotated around the base end portion 9a. Since each thrust needle bearing 25 exists between the outer side surface of each outer ring 28 and the inner side surface of the support plate portion 7 constituting each trunnion 6, the rotation can be performed smoothly. Therefore, as described above, the force for changing the inclination angle of each displacement shaft 9, 9 can be small.

  Many transmissions combining the toroidal type continuously variable transmission and the planetary gear mechanism as described above have been proposed so far (see, for example, Patent Document 1).

JP 2005-249181 A

  Meanwhile, during operation, power is always transmitted to the planetary gears 78, 79, 80... And the carrier 77 rotates at the same rotational speed as that of the engine, so that the planetary gears 78, 79. The centrifugal force to be applied is also applied to the needle bearings 248a, 248b,. Therefore, it is necessary to supply a considerable amount of lubricating oil for cooling the needle bearings 248a, 248b,.

  Therefore, in the conventional structure shown in FIG. 6, the lubricating oil supplied from the output shaft 51 side in the subsequent stage is ejected from the oil hole 302 on the radially inner side of the oil catching member (oil catcher) 300 supported by the carrier 77. Then, the oil catching member 300 holds it. At this time, since the output shaft 51 and the carrier 77 (input shaft 18) rotate in opposite directions, the jetted lubricating oil and the oil catching member 300 collide with each other. Since this collision force acts as a stirring resistance, it causes a reduction in the power transmission efficiency of the transmission.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a continuously variable transmission that can capture lubricating oil in an oil capturing member without reducing the power transmission efficiency of the transmission. To do.

  In order to achieve the above object, the present invention provides an input disk and an output disk that are supported concentrically and rotatably with their inner surfaces facing each other, and are sandwiched between these two disks. A toroidal-type continuously variable transmission having a plurality of power rollers, the input-side disk and the output-side disk being supported concentrically and rotatably, and the planetary gear can revolve and rotate with respect to the sun gear. A planetary gear mechanism having a carrier supported by the carrier, wherein the input side disk and the carrier rotate synchronously, and are supported by the carrier and scattered and supplied to the planetary gear mechanism side. An oil capturing member that captures the lubricating oil is provided, and this oil capturing member generates a component force in the rotation direction of the carrier from the collision force of the oil that collides with the oil capturing member. Wherein the fins are provided that.

  According to the present invention, due to the action of the fin provided on the oil catching member, a component force in the rotation direction of the carrier is generated from the collision force of the oil colliding with the oil catching member. That is, the rotation of the carrier is promoted by the supply of scattered lubricant. Therefore, the lubricating oil can be captured by the oil capturing member without reducing the power transmission efficiency of the transmission.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The feature of the present invention lies in the supply form of the lubricating oil to the planetary gear mechanism side, and the other configurations and operations are the same as the conventional configurations and operations described above. Therefore, the features of the present invention will be described below. Only the other parts are referred to, and the same reference numerals as those in FIGS.

  As shown in FIG. 1, in the continuously variable transmission according to the present embodiment, the first carrier is provided between a portion protruding from the hollow rotary shaft 75 (see FIG. 4) at the tip of the input shaft 18 and the input side disk 2 </ b> B. 77 is provided so as to hang over and the third planetary shaft 247 of the first carrier 77 supports an oil catching member 300 that catches the lubricating oil scattered and supplied to the planetary gear mechanism side. . In the present embodiment, the lubricating oil supplied from the output shaft 51 (see FIG. 4), not shown, is ejected from the oil hole 302 on the radially inner side of the oil capturing member 300 supported by the carrier 77. The oil catching member 300 catches the oil.

  In the present embodiment, the oil catching member 300 is provided with fins 300 a that generate a component force in the rotational direction of the carrier 77 from the collision force of the oil that collides with the oil catching member 300. Specifically, as shown in FIG. 2, the oil capturing member 300 has an annular shape, and a plurality of fins 300 a are provided at predetermined intervals over the entire circumference of the annular oil capturing member 300. As shown also in FIG. 3, each fin 300 a extends substantially along the rotational direction R of the carrier 77 from the radially outer side of the oil capturing member 300 toward the radially inner side, and in the radial direction of the oil capturing member 300. It is inclined at a predetermined angle. That is, as shown in FIG. 3, when the lubricating oil L collides against the fin 300a from the inside in the radial direction, the inclination of the fin 300a is a component force of the collision force with respect to the rotation direction R of the carrier 7 (of the carrier 77). The direction in which the component force (F) in the rotational direction F is generated is set.

  According to the above configuration, the component force F in the rotation direction R of the carrier 77 is generated from the collision force of the oil that collides with the oil capturing member 300 by the action of the fins 300 a provided in the oil capturing member 300. That is, the rotation of the carrier 77 is urged by the scattered supply of the lubricating oil. Therefore, the lubricating oil can be captured by the oil capturing member 300 without reducing the power transmission efficiency of the transmission.

  The present invention can be applied to various continuously variable transmissions including a toroidal continuously variable transmission including a full toroidal type having no trunnion and a planetary gear mechanism in addition to a half toroidal type.

It is principal part sectional drawing of the planetary gear mechanism of the continuously variable transmission which concerns on embodiment of this invention. FIG. 2 is a perspective view of an oil catching member supported by a carrier of the planetary gear mechanism of FIG. 1. It is a top view (action explanatory drawing) of the oil capture member of FIG. It is principal part sectional drawing of the geared neutral type continuously variable transmission in which the conventional double cavity type toroidal type continuously variable transmission was incorporated. It is sectional drawing which follows the AA line of FIG. It is a principal part expanded sectional view of the conventional continuously variable transmission.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 Power roller 2A Input side disk 53 Output side disk 47 Toroidal type continuously variable transmission 48, 49, 50 Planetary gear type transmission unit 76, 81, 82, 84 Sun gear 77 First carrier (carrier)
78, 79, 80 Planetary gear 300 Oil capturing member 300a Fin

Claims (4)

A toroidal type non-rotation having an input side disk and an output side disk that are supported concentrically and rotatably with their inner surfaces facing each other, and a plurality of power rollers sandwiched between these disks. A step transmission,
A planetary gear mechanism having a carrier that is concentrically and rotatably supported by the input-side disk and the output-side disk, and that supports the planetary gear so as to revolve and rotate with respect to the sun gear;
With
In the continuously variable transmission in which the input disk and the carrier rotate synchronously,
An oil catching member that captures the lubricating oil supported by the carrier and scattered and supplied to the planetary gear mechanism side is provided. The oil catching member rotates the carrier from the collision force of the oil colliding with the oil catching member. A continuously variable transmission comprising a fin for generating a directional component force.   The continuously variable transmission according to claim 1, wherein the oil catching member forms an annular shape, and the plurality of fins are provided at predetermined intervals over the entire circumference of the annular oil catching member.   3. The continuously variable transmission according to claim 2, wherein each of the fins extends substantially along a rotation direction of the carrier from a radially outer side to a radially inner side of the oil capturing member.   The continuously variable transmission according to claim 3, wherein each of the fins extends at a predetermined angle with respect to a radial direction of the oil catching member.

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