JP5678610B2 - Shift control device for continuously variable transmission - Google Patents

Description

  The present invention relates to a transmission control device for a continuously variable transmission that can be used for transmissions of automobiles, various industrial machines, and the like, and more particularly to a transmission of a continuously variable transmission having a structure for preventing backlash in a transmission control link mechanism. The present invention relates to a control device.

  A continuously variable transmission, for example, a double cavity toroidal continuously variable transmission used as an automobile transmission is configured as shown in FIGS. As shown in FIG. 2, the input shaft 1 is rotatably supported inside the casing 50, and two input side disks 2, 2 and two output side disks 3 are disposed on the outer periphery of the input shaft 1. 3 is 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 driven to rotate by a drive shaft 22 via a loading cam type pressing device 12 provided between an input side disk 2 and a cam plate (loading cam) 7 located on the left side in the drawing. It has become. 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. A power roller is provided between the inner side surfaces (concave surface; also referred to as a traction surface) 2a and 2a of the input side disks 2 and 2 and the inner side surfaces (concave surface; also referred to as a traction surface) 3a and 3a of the output disks 3 and 3. 11 (see FIG. 3) is rotatably held.

  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 a loading nut 9 screwed into a screw portion 1 e formed on the outer peripheral surface of the input shaft 1. 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.

  As shown in FIG. 3 which is a cross-sectional view taken along the line AA of FIG. 2, both the disks 3 and 3 are sandwiched from both sides inside the casing 50 and at the side positions of the output side disks 3 and 3. The pair of yokes 23A and 23B is supported in the state. The pair of yokes 23A and 23B are formed in a rectangular shape by pressing or forging a metal such as steel. In order to support pivots 14 provided at both ends of the trunnion 15 to be described later in a swingable manner, circular support holes 18 are provided at the four corners of the yokes 23A and 23B, and the width direction of the yokes 23A and 23B. A circular locking hole 19 is provided at the center of the.

  The pair of yokes 23 </ b> A and 23 </ b> B are supported so as to be slightly displaceable by support posts 64 and 68 formed on portions of the inner surface of the casing 50 facing each other. These support posts 64 and 68 are provided so as to face the first cavity 221 and the second cavity 222, respectively, between the inner side surface 2a of the input side disk 2 and the inner side surface 3a of the output side disk 3. Yes.

  Therefore, the yokes 23 </ b> A and 23 </ b> B are supported by the support posts 64 and 68, and one end thereof faces the outer peripheral portion of the first cavity 221, and the other end faces the outer peripheral portion of the second cavity 222. doing.

  Since the first and second cavities 221 and 222 have the same structure, only the first cavity 221 will be described below.

  As shown in FIG. 3, inside the casing 50, the first cavity 221 is provided with a pair of trunnions 15, 15 that swing about a pair of pivots 14, 14 that are twisted with respect to the input shaft 1. It has been. In FIG. 3, the input shaft 1 is not shown. Each trunnion 15, 15 is a pair of bent portions formed in a state in which the trunnions 15, 15 are bent toward the inner side surface of the support plate 16 at both ends in the longitudinal direction (vertical direction in FIG. 3) of the support plate 16. Wall portions 20 and 20 are provided. 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 in the center portion of the support plate portion 16, and a base end portion (first shaft 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 23 supported at the center of each trunnion 15, 15 can be adjusted. In addition, each power roller 11 is rotatably supported around the tip end portion (second shaft 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, as described above, the pivot shafts 14 and 14 of the trunnions 15 and 15 are supported so as to be swingable with respect to the pair of yokes 23A and 23B and to be displaceable in the axial direction (vertical direction in FIG. 3). The trunnions 15 and 15 are restricted from moving in the horizontal direction by the yokes 23A and 23B. As described above, four circular support holes 18 are provided at the four corners of each of the yokes 23 </ b> A and 23 </ b> B. The pivot shafts 14 provided at both ends of the trunnion 15 are respectively provided in the support holes 18 with the radial needle bearings 30. It is supported so as to be able to swing through. Further, as described above, the circular locking hole 19 is provided in the central portion of the yokes 23A and 23B in the width direction (left and right direction in FIG. 3), and the inner peripheral surface of the locking hole 19 is spherical. Support posts 64 and 68 are internally fitted as concave surfaces. 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 (in FIG. (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 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 (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 (shaft portions extending from the pivot shaft) 29 and 29 are provided at one end portions (lower end portions in FIG. 3) of the trunnions 15 and 15, respectively, and outer peripheral surfaces of intermediate portions of the driving rods 29 and 29, respectively. The drive pistons (hydraulic pistons) 33, 33 are fixedly provided. 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. The drive pistons 33 and 33 and the drive cylinder 31 constitute a drive device 32 that displaces the trunnions 15 and 15 in the axial direction of the pivots 14 and 14 of the trunnions 15 and 15.

  In the case of the toroidal continuously variable transmission configured as described above, the rotation of the drive shaft 22 is transmitted to the input side disks 2 and 2 and the input shaft 1 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 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 rotational speed 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 one gear ratio control valve 112 as shown in FIG. 4 regardless of the number of the drive devices 32. The movement of each trunnion 15 is fed back to the gear ratio control valve 112. 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. . Also, a precess cam 118 is provided at the end of the drive rod 29 attached to any one of the trunnions 15 among the drive rods 29 and 29 that connect the trunnions 15 and 15 and the drive pistons 33 and 33 of the drive devices 32. The feedback mechanism is fixed, and the movement of the drive rod 29, that is, the combined value of the displacement amount in the axial direction and the displacement amount in the rotation direction is transmitted to the spool 115 via the recess cam 118 and the link arm 119. Is configured.

  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 of these driving devices 32, 32 displaces each trunnion 15, 15 in a predetermined direction. That is, the trunnions 15 and 15 are displaced in the axial direction of the pivots 14 and 14 as the pressure oil is fed, and swing around the pivots 14 and 14. Then, the movement (axial direction and swinging displacement) of any one of the trunnions 15 is transmitted to the spool 115 via the recess cam 118 fixed to the end of the drive rod 29 and the link arm 119. 115 is displaced in the axial direction. As a result, in the state where the trunnion 15 is 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 the drive devices 32 and 32 are stopped. Therefore, the displacement amounts of the trunnions 15 and 15 in the axial direction and the swinging direction are only in accordance with the displacement amount of the sleeve 114 by the stepping motor 113.

  By the way, since the engagement between the link member 120, the tip of the output rod of the stepping motor 113, and the end of the sleeve 114 constituting the gear ratio control valve 112 is generally rattle, Has been devised (see, for example, Patent Document 1 to Patent Document 3). Specifically, for example, as shown in FIG. 4, the sleeve 114 is biased in the direction of the link member 120 by a spring 130 attached to the transmission ratio control valve 112 (spool 115). I try to prevent backlash.

JP 2002-168329 A JP 2004-225888 A No. 1-40367

  It is desirable that the above-described rattling-preventing spring 130 has a large thrust to prevent sticking of the transmission ratio control valve 112 and improve the sliding performance of the sleeve 114, but the thrust of the stepping motor 113 for moving the sleeve 114 is preferable. You can't do more. If the thrust of the spring 130 is increased too much, the movement of the stepping motor 113 becomes dull and not only the shift response is lowered, but also an excessive force is applied to the stepping motor 113 and the durability of the stepping motor 113 may be lowered. There is also. In the case of the conventional rattling prevention structure, there is a concern about the generation of such an excessive thrust. For example, when a spring for preventing rattling as described in Patent Document 2 is used, the thrust of the extra spring is applied to the stepping motor. May work.

  The present invention has been made in view of the above circumstances, and it is possible to increase the thrust of a spring for preventing rattling, while preventing an excessive force from being applied to the stepping motor. The purpose is to provide.

In order to solve the above-mentioned problems, the present invention provides a gear ratio for controlling the supply and discharge of pressure oil to a drive device that axially displaces a trunnion of a 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 slidably fitted in the sleeve in the axial direction. A continuously variable transmission having a feedback mechanism for transmitting a movement of the drive rod to the spool by connecting a drive rod holding the drive piston of the drive device of the step transmission to the spool via a cam link mechanism. In this gear change control device, the sleeve is attached to the spool of the gear ratio control valve, and the sleeve is biased in the direction of the link member to prevent rattling of the engaging portions of these members. First urging body that the attached to the stepping motor of the output rod, and a second urging body to offset the thrust of the first urging member,
The first and second biasing bodies are springs;
The spring forming the second urging body is interposed between a retaining projection provided on the output rod and the base body of the stepping motor in a state of being wound around the output rod of the stepping motor. It is inserted and it is provided between this base body and the said link member, It is characterized by the above-mentioned.

  According to this configuration, since the thrust of the first urging body that prevents rattling is canceled out by the second urging body, the first urging body of the first urging body is not caused to act excessively on the stepping motor. The thrust can be increased as compared with the prior art. Therefore, it is possible to prevent sticking of the transmission ratio control valve and improve the sliding performance of the sleeve. Moreover, since it is only necessary to provide the second urging body for canceling the thrust of the first urging body with respect to the conventional structure, the above-described effects can be obtained with the minimum necessary number of parts.

In the above configuration, the spring forming the first urging body is interposed between the retaining protrusion provided on the spool and the end surface of the sleeve while being wound around the spool. It is preferable that

  According to the present invention, it is possible to provide a transmission control device for a continuously variable transmission that enables an increase in thrust of a spring for preventing rattling, while preventing an excessive force from being applied to a stepping motor.

1 is a schematic configuration diagram of a shift control device according to an embodiment of the present invention. 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.

  Embodiments of the present invention will be described below 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 continuously variable transmission, and the other structure and operation are the same as the conventional structure and function described above. Only the characteristic part of the present invention will be described, and the other parts will be simply described with the same reference numerals as those in FIGS.

  FIG. 1 shows a transmission ratio control valve 112 that controls the supply and discharge of pressure oil to and from a drive unit 32 that axially displaces the trunnion 15 of the continuously variable transmission described above to cause a continuously variable transmission of the continuously variable transmission. The shift control apparatus 230 of embodiment of this invention provided is shown. The transmission control device 230 according to the present invention can be applied to continuously variable transmissions having various structures. Here, an example applied to the above-described toroidal continuously variable transmission will be described.

  As shown in the figure, the transmission ratio control valve 112 includes a sleeve 114 that is displaced in the axial direction by a stepping motor 113 via a link member 120, and a spool 115 that is slidably fitted in the sleeve 114 in the axial direction. Have As described above with reference to the prior art, the speed change control device 230 includes a cam / link mechanism in which the drive rod 29 that holds the drive piston 33 of the drive device 32 of the continuously variable transmission includes the prince cam 118 and the link arm 119. By connecting to the spool 115 via the, a feedback mechanism for transmitting the movement of the drive rod 29 to the spool 115 is configured.

  A first urging body 130 is attached to the spool 115 of the transmission ratio control valve 112 to urge the sleeve 114 in the direction of the link member 120 to prevent the engaging portions of the members 114 and 120 from rattling. It has been. Specifically, the first urging member 130 is formed of a spring, and is provided between the end of the sleeve 114 and the end face of the sleeve 114 provided on the spool 115 while being wound around the spool 115. Is inserted.

  A second urging body 135 for canceling the thrust of the first urging body 130 is attached to the output rod 113a of the stepping motor 113. Specifically, the second urging body 135 is formed of a spring and is stepped with the retaining protrusion 202 provided on the output rod 113a while being wound around the output rod 113a of the stepping motor 113. The motor 113 is interposed between the base body 113b (specifically, the outer surface of the motor housing). In this case, the second urging body 135 urges the output rod 113a in the direction of the link member 120 so as to cancel the thrust of the first urging body 130.

  In addition, as the 1st and 2nd biasing bodies 130 and 135, the various elastic members containing a spring can be mentioned. In short, any form may be used as long as it has an urging function and a canceling function.

  As described above, according to the transmission control device 230 of the present embodiment, the thrust of the first urging body 130 that prevents rattling is canceled out by the second urging body 135, so that the stepping motor 113 is excessively large. Therefore, the thrust of the first urging body 130 can be increased more than before without applying any force, and therefore, the sticking of the transmission ratio control valve 112 can be prevented and the sliding performance of the sleeve 114 can be improved.

15 trunnion 29 drive rod 32 drive device 33 drive piston 112 gear ratio control valve 113 stepping motor 113a output rod 113b housing (base body)
114 Sleeve 115 Spool 118 Prince cam (cam link mechanism)
119 Link arm (cam link mechanism)
120 Link member 130 First urging body (spring)
135 Second biasing body (spring)
200 Retaining convex portion 202 Retaining convex portion

Claims (2)

A transmission ratio control valve that controls the supply and discharge of pressure oil to and from the drive device that axially displaces the trunnion of the continuously variable transmission to cause the continuously variable transmission of the continuously variable transmission; A sleeve that is displaced in the axial direction by a stepping motor via a link member, and a spool that is slidably fitted in the sleeve in the axial direction, and holds the drive piston of the drive device of the continuously variable transmission. In a transmission control device for a continuously variable transmission, a feedback mechanism configured to transmit a movement of the drive rod to the spool by connecting the drive rod to the spool via a cam link mechanism,
A first biasing body which is attached to the spool of the gear ratio control valve and prevents rattling of the engaging portions of these members by biasing the sleeve in the direction of the link member;
A second urging body attached to the output rod of the stepping motor and for canceling out the thrust of the first urging body,
The first and second biasing bodies are springs;
The spring forming the second urging body is interposed between a retaining projection provided on the output rod and the base body of the stepping motor in a state of being wound around the output rod of the stepping motor. A transmission control device for a continuously variable transmission, which is inserted between the base body and the link member . The spring forming the first urging body is interposed between a retaining protrusion provided on the spool and an end surface of the sleeve while being wound around the spool. The transmission control device for a continuously variable transmission according to claim 1 .

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