JP2012177393A - Shift control device for toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a shift control device for a toroidal type continuously variable transmission, having a structure for inputting the direction of normal/reverse rotation to a toroidal transmission part to suppress an increase in the size of the whole device.SOLUTION: The shift control device for the toroidal type continuously variable transmission, where two speed ratio control valves 112 for normal rotation and reverse rotation exist, includes a sleeve to be displaced via a link mechanism 200 in the axial direction by one common stepping motor 113, and a spool fitted into the sleeve displaceably in the axial direction. Namely, the two speed ratio control valves 112, 112 are connected to the one common stepping motor 113 via the link mechanism 200 for operation.

Description

  The present invention relates to a shift control device for a toroidal-type continuously variable transmission that can be used in transmissions of automobiles and various industrial machines.

  For example, a double-cavity toroidal continuously variable transmission used as a transmission for an automobile is configured as shown in FIGS. As shown in FIG. 2, an input shaft (center shaft) 1 is rotatably supported inside the casing 50, and two input side disks 2, 2 and two outputs are provided on the outer periphery of the input shaft 1. Side disks 3 and 3 are attached. An output gear 4 is rotatably supported on the outer periphery of the intermediate portion of the input shaft 1. Output side disks 3 and 3 are connected to cylindrical flange portions 4a and 4a provided at the center of the output gear 4 by spline coupling.

  The input shaft 1 is rotationally driven by a drive shaft 22 via a loading cam type pressing device 12 provided between an input side disk 2 and a cam plate 7 located on the left side in the drawing. . The output gear 4 is supported in the casing 50 via a partition wall 13 formed by coupling two members, so that the output gear 4 can rotate around the axis O of the input shaft 1 while the axis O. Directional displacement is prevented.

  The output side disks 3 and 3 are supported by needle bearings 5 and 5 interposed between the input shaft 1 so as to be rotatable about the axis O of the input shaft 1. Further, the left input side disk 2 in the figure is supported on the input shaft 1 via a ball spline 6, and the right side input disk 2 in the figure is splined to the input shaft 1. Rotates with the input shaft 1. Further, the power roller 11 (see FIG. 3) is freely rotatable between the inner side surfaces (concave surfaces) 2a, 2a of the input side discs 2, 2 and the inner side surfaces (concave surfaces) 3a, 3a of the output side discs 3, 3. Is sandwiched between.

  A step 2b is provided on the inner peripheral surface 2c of the input disk 2 located on the right side in FIG. 2, and the step 1b provided on the outer peripheral surface 1a of the input shaft 1 is abutted against the step 2b. At the same time, the back surface (right surface in FIG. 2) of the input side disk 2 is abutted against the loading nut 9. Thereby, the displacement of the input side disk 2 in the direction of the axis O with respect to the input shaft 1 is substantially prevented. Further, a disc spring 8 is provided between the cam plate 7 and the flange 1d of the input shaft 1, and this disc spring 8 is a concave surface 2a, 2a, 3a of each disk 2, 2, 3, 3. , 3a and the contact surface between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 are applied with a pressing force.

  3 is a cross-sectional view taken along line AA in FIG. As shown in FIG. 3, a pair of trunnions 15, 15 that swing around a pair of pivots 14, 14 that are twisted with respect to the input shaft 1 are provided inside the casing 50. In FIG. 3, the input shaft 1 is not shown. Each trunnion 15, 15 is a pair of bent wall portions 20, 20 formed at both ends in the longitudinal direction (vertical direction in FIG. 3) of the support plate portion 16 so as to be bent toward the inner surface side of the support plate portion 16. have. The bent wall portions 20 and 20 form concave pocket portions P for accommodating the power rollers 11 in the trunnions 15 and 15. Further, the pivot shafts 14 and 14 are concentrically provided on the outer side surfaces of the bent wall portions 20 and 20, respectively.

  A circular hole 21 is formed at the center of the support plate portion 16, and a base end portion 23 a of the displacement shaft 23 is supported in the circular hole 21. Then, by swinging each trunnion 15, 15 about each pivot 14, 14, the inclination angle of the displacement shaft (shaft) 23 supported at the center of each trunnion 15, 15 can be adjusted. It has become. In addition, each power roller 11 is rotatably supported via a radial needle bearing 99 around the distal end portion 23b of the displacement shaft 23 protruding from the inner surface of each trunnion 15, 15. 11 is sandwiched between the input disks 2 and 2 and the output disks 3 and 3. In addition, the base end part 23a and the front-end | tip part 23b of each displacement shaft 23 and 23 are mutually eccentric.

  Further, the pivot shafts 14 and 14 of the trunnions 15 and 15 are supported so as to be swingable and axially displaceable with respect to the pair of yokes 23A and 23B, respectively. The horizontal movement of the trunnions 15 and 15 is restricted by 23B. Each yoke 23A, 23B is formed in a rectangular shape by pressing or forging a metal such as steel. Four circular support holes 18 are provided at the four corners of each of the yokes 23 </ b> A and 23 </ b> B, and the pivot shafts 14 provided at both ends of the trunnion 15 swing through the radial needle bearings 30. It is supported freely. In addition, a circular locking hole 19 is provided in the central portion of the yokes 23A and 23B in the width direction (the left-right direction in FIG. 2). The inner peripheral surface of the locking hole 19 is a spherical concave surface, and is a spherical post. 64 and 68 are fitted inside. That is, the upper yoke 23A is swingably supported by the spherical post 64 supported by the casing 50 via the fixing member 52, and the lower yoke 23B is supported by the spherical post 68 and the drive for supporting the same. The upper cylinder body 61 of the cylinder 31 is swingably supported.

  The displacement shafts 23 and 23 provided in the trunnions 15 and 15 are provided at positions 180 degrees opposite to the input shaft 1. Further, the direction in which the distal end portion 23b of each of the displacement shafts 23 and 23 is eccentric with respect to the base end portion 23a is the same direction as the rotational direction of both the disks 2, 2, 3 and 3 (up and down in FIG. 3). (Reverse direction). Further, the eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1 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 1. As a result, even if each power roller 11, 11 tends to be displaced in the axial direction of the input shaft 1 due to elastic deformation of each component member based on the thrust load generated by the pressing device 12, each component This displacement is absorbed without applying an excessive force to the member.

  Further, between the outer surface of the power roller 11 and the inner surface of the support plate portion 16 of the trunnion 15, a thrust ball bearing 24 that is a thrust rolling bearing, and a thrust needle bearing, in order from the outer surface side of the power roller 11. 25. 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 such thrust ball bearings 24 includes a plurality of balls (hereinafter referred to as rolling elements) 26, 26, an annular retainer 27 that holds the rolling elements 26, 26 in a freely rolling manner, And an annular outer ring 28. Further, the inner ring raceway of each thrust ball bearing 24 is formed on the outer side surface (large end surface) of each power roller 11, and the outer ring raceway is formed on the inner side surface of each outer ring 28.

  The thrust needle bearing 25 is sandwiched between the inner surface of the support plate portion 16 of the trunnion 15 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 the power roller 11, while the power roller 11 and the outer ring 28 swing around the base end portion 23 a of each displacement shaft 23. Allow.

  Further, driving rods (trunnion shafts) 29 and 29 are provided at one end portions (lower end portions in FIG. 3) of the trunnions 15 and 15, respectively, and a driving piston ( Hydraulic pistons) 33, 33 are fixed. Each of these drive pistons 33 and 33 is oil-tightly fitted in a drive cylinder 31 constituted by an upper cylinder body 61 and a lower cylinder body 62. These drive pistons 33 and 33 and the drive cylinder 31 constitute a drive device (which constitutes a toroidal transmission unit) 32 that displaces the trunnions 15 and 15 in the axial direction of the pivots 14 and 14 of the trunnions 15 and 15. is doing.

  In the case of the toroidal continuously variable transmission configured as described above, the rotation of the input shaft 1 is transmitted to the input side disks 2 and 2 via the pressing device 12. Then, the rotation of the input side disks 2 and 2 is transmitted to the output side disks 3 and 3 via the pair of power rollers 11 and 11, and the rotation of the output side disks 3 and 3 is further transmitted to the output gear 4. It is taken out more.

  When changing the rotational speed ratio between the input shaft 1 and the output gear 4, the pair of drive pistons 33, 33 are displaced in opposite directions. As the drive pistons 33 and 33 are displaced, the pair of trunnions 15 and 15 are displaced in directions opposite to each other. For example, the power roller 11 on the left side of FIG. 3 is displaced downward in the figure, and the power roller 11 on the right side of FIG. 3 is displaced upward in the figure. As a result, the peripheral surfaces 11a and 11a of the power rollers 11 and 11 act on contact portions of the input side disks 2 and 2 and the inner side surfaces 2a, 2a, 3a and 3a of the output side disks 3 and 3, respectively. The direction of the tangential force changes. As the force changes, the trunnions 15 and 15 swing (tilt) in opposite directions around the pivots 14 and 14 pivotally supported by the yokes 23A and 23B.

  As a result, the contact position between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 and the inner surfaces 2a and 3a changes, and the gear ratio between the input shaft 1 and the output gear 4 changes. Further, when the torque transmitted between the input shaft 1 and the output gear 4 fluctuates and the amount of elastic deformation of each component changes, the power rollers 11 and 11 and the outer rings attached to the power rollers 11 and 11 will be described. 28 and 28 slightly rotate around the base end portions 23a and 23a of the displacement shafts 23 and 23, respectively. Since the thrust needle bearings 25 and 25 exist between the outer side surfaces of the outer rings 28 and 28 and the inner side surfaces of the support plate portions 16 constituting the trunnions 15 and 15, respectively, the rotation is performed smoothly. Is called. Therefore, as described above, the force for changing the inclination angle of each displacement shaft 23, 23 can be small.

  Further, in the above configuration, the supply / discharge state of the pressure oil to / from the drive device 32 is performed by the transmission ratio control valve 112 as shown in FIG. 4, and the movement of the trunnion 15 is fed back to the transmission ratio control valve 112. It is like that. The transmission ratio control valve 112 includes a sleeve 114 that is displaced in the axial direction by the stepping motor 113 via the link member 120, and a spool 115 that is fitted on the inner diameter side of the sleeve 114 so as to be axially displaceable. . Further, a recess cam 118 is fixed to an end portion of a drive rod 29 that connects the trunnion 15 and the drive piston 33 of each drive device 32, and the movement of the drive rod 29 via the recess cam 118 and link arm 119 That is, a feedback mechanism is configured in which a combined value of the axial displacement amount and the rotational displacement amount is transmitted to the spool 115.

  When switching the speed change state, the sleeve 114 is displaced by a predetermined amount via the link member 120 by the stepping motor 113, and the flow path of the speed ratio control valve 112 is opened. As a result, the pressure oil is fed into each driving device 32 in a predetermined direction, and each driving device 32 displaces each trunnion 15 in a predetermined direction. That is, the trunnions 15 swing around the pivots 14 while being displaced in the axial directions of the pivots 14 as the pressure oil is fed. The movement (axial direction and swing displacement) of the trunnion 15 is transmitted to the spool 115 via the recess cam 118 and the link arm 119 fixed to the end of the drive rod 29, and the spool 115 is displaced in the axial direction. Let As a result, with the trunnion 15 displaced by a predetermined amount, the flow path of the transmission ratio control valve 112 is closed, and the supply and discharge of the pressure oil to and from each drive device 32 is stopped. Therefore, the displacement amount of each trunnion 15 in the axial direction and the swinging direction is only in accordance with the displacement amount of the sleeve 114 by the stepping motor 113.

  By the way, when the rotational direction input to the toroidal transmission unit is both forward and reverse, two speed ratio control valves are provided for forward and reverse rotation, but the forward and reverse rotations are provided in the toroidal transmission unit. When the direction is input, it is necessary to control the inclination direction of the power roller 11 transmitted between the output side disks 3 and 3 important for the shift control and the shift feedback in accordance with the input rotation direction. Therefore, in Patent Documents 1 to 5, etc., a transmission hydraulic actuator that drives the power roller 11 to a predetermined tilt position, and a transmission that outputs a hydraulic signal to the shift control valve while feeding back the tilt amount of the power roller 11. And are provided.

Japanese Patent Publication No.7-113410 Japanese Patent Laid-Open No. 7-027212 JP-A-7-269673 Japanese Patent No. 4055253 JP-A-8-28645

  As described above, the structure in which the rotation direction of the forward rotation and the reverse rotation is input to the toroidal transmission portion tends to cause the device to be complicated and large. However, in the conventional structure, two steppings corresponding to the forward rotation and the reverse rotation are apt to occur. Since the motor and the precess cam are provided, the apparatus is further increased in size and complexity.

  The present invention has been made in view of the above circumstances, and provides a shift control device for a toroidal-type continuously variable transmission that can suppress an increase in the size of the entire device in a structure in which forward and reverse rotation directions are input to a toroidal transmission unit. The purpose is to provide.

  In order to achieve the above object, the present invention controls the supply and discharge of pressure oil to a drive device that axially displaces a trunnion of a toroidal type continuously variable transmission to cause a continuously variable transmission of the continuously variable transmission. The gear ratio control valve includes a sleeve that is displaced in the axial direction by a stepping motor via a link member, and a spool that is fitted in the sleeve so as to be freely displaceable in the axial direction. A toroidal type in which a drive rod that holds a drive piston of the drive device of the continuously variable transmission is connected to the spool via a cam link mechanism to transmit a movement of the drive rod to the spool. A transmission control device for a continuously variable transmission, wherein two transmission ratio control valves are provided for inputting a normal rotation direction and a reverse rotation direction to a toroidal transmission unit with the drive device. And a detection means for detecting whether the rotational direction input to the toroidal transmission unit is normal rotation or reverse rotation, and a forward rotation speed ratio control valve to be driven based on a detection result of the detection means and a reverse rotation In a shift control device for a toroidal-type continuously variable transmission that selectively switches between a gear ratio control valve and a switching valve, the two gear ratio control valves are connected to a common stepping motor via a link mechanism. It is characterized by being.

  According to the transmission control device for a toroidal-type continuously variable transmission of the present invention, since only one stepping motor is required for the two transmission ratio control valves, the forward and reverse rotation directions are input to the toroidal transmission unit. Therefore, the enlargement of the entire apparatus can be suppressed.

It is a figure which shows the transmission control apparatus of the continuously variable transmission which concerns on embodiment of this invention, Comprising: (a) is a perspective view, (b) is a schematic plan view. It is sectional drawing which shows an example of the specific structure of the toroidal type continuously variable transmission conventionally known. It is sectional drawing which follows the AA line of FIG. It is a schematic block diagram of the conventional transmission control apparatus.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The feature of the present invention lies in the structure of the speed change control device that causes the continuously variable transmission of the toroidal type continuously variable transmission, and the other structures and operations are the same as the conventional structures and functions described above. In the above, only the characteristic part of the present invention will be referred to, and other parts will be simply described with the same reference numerals as those in FIGS.

  FIG. 1 is a transmission ratio control valve that controls the supply and discharge of pressure oil to and from a drive device 32 that axially displaces the trunnion 15 of the above-described toroidal continuously variable transmission to cause a continuously variable transmission of the continuously variable transmission. 1 shows a transmission control apparatus according to an embodiment of the present invention that includes 112.

  As shown in the figure, there are two gear ratio control valves 112, one for forward rotation and one for reverse rotation, and a sleeve that is displaced in the axial direction via a link mechanism 200 by a common stepping motor 113, and in this sleeve And a spool that is slidably fitted in the axial direction. In other words, in the present embodiment, the two gear ratio control valves 112 and 112 are operated by being connected to one common stepping motor 113 via the link mechanism 200 (one common stepping motor 113 and two gear ratios). The control valves 112 and 112 are linked by the link mechanism 200). The link mechanism 200 can be rotated around the link fulcrums 200a and 200a.

  Further, as described above in relation to the background art, in the speed change control device of this embodiment, the drive rod 29 that holds the drive piston 33 of the drive device 32 of the toroidal-type continuously variable transmission includes the recess cam 118, the link arm 119, By connecting to the spool via a cam / link mechanism, a feedback mechanism for transmitting the movement of the drive rod 29 to the spool is formed. As can be seen from the figure, in this embodiment, the recess cam 118 is shared by the two gear ratio control valves 112 and 112.

  Further, in the present embodiment, detection means 220 for detecting whether the rotation direction input to the toroidal transmission unit is normal rotation or reverse rotation is provided, and for normal rotation to be driven based on the detection result of the detection means 220. The transmission ratio control valve 112 and the reverse transmission ratio control valve 112 are switched by a switching valve 210 (the switching valve 210 switches the hydraulic pressures of the transmission ratio control valves 112 and 112). The switching valve is also connected to the drive device 32 (transmission actuator) by a hydraulic circuit.

  In such a configuration, as described above in the background art, when a shift signal is sent to the stepping motor 113, the transmission ratio control valve 112 is operated, and the pressure oil of the drive device 32 is changed to offset the power roller 11. . As a result, a tilting force is generated and a speed change operation is performed. Further, in order to end the shift, the pre-rotation cam and the reverse-rotation cam lift are integrally provided in the recess cam 118 by the above-described feedback mechanism. 112 and the reverse speed ratio control valve 112 are fed back. Thereby, the valve of the gear ratio control valve 112 is closed, and the shift is completed.

  As described above, according to the present embodiment, since only one stepping motor 113 and one recess cam 118 are required for the two gear ratio control valves 112 and 112, the forward and reverse rotation directions are input to the toroidal transmission unit. In the structure, the enlargement of the entire apparatus can be suppressed.

  The present invention can be applied to various half-toroidal continuously variable transmissions such as a single cavity type and a double cavity type.

2 input side disk 3 output side disk 11 power roller 15 trunnion 29 drive rod 32 drive device (toroidal transmission)
33 Driving piston 112 Gear ratio control valve 113 Stepping motor 114 Sleeve 115 Spool 118 Precess cam (cam / link mechanism)
119 Link arm (cam link mechanism)
200 Link mechanism

Claims (1)

A transmission ratio control valve for controlling the supply and discharge of pressure oil to and from a drive device that axially displaces the trunnion of the toroidal type continuously variable transmission to cause the continuously variable transmission of the continuously variable transmission; Has a sleeve that is displaced in the axial direction by a stepping motor via a link member, and a spool that is fitted in the sleeve so as to be displaceable in the axial direction, and is a driving piston of the driving device of the continuously variable transmission. A toroidal-type continuously variable transmission speed change control device comprising a feedback mechanism for transmitting the movement of the drive rod to the spool by connecting a drive rod holding the drive rod to the spool via a cam link mechanism, Two gear ratio control valves are provided to input the forward and reverse rotation directions to the toroidal transmission unit with the drive device, and the toroidal transmission unit is also input to the toroidal transmission unit. Detecting means for detecting whether the rotation direction to be rotated is normal rotation or reverse rotation, and switches between a forward rotation speed ratio control valve and a reverse speed ratio control valve to be driven based on the detection result of the detection means In the shift control device for the toroidal type continuously variable transmission, which is selectively switched by
A transmission control apparatus for a toroidal continuously variable transmission, wherein the two transmission ratio control valves are connected to and operated by a common stepping motor via a link mechanism.

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