JP6528361B2 - Toroidal type continuously variable transmission - Google Patents

Toroidal type continuously variable transmission Download PDF

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JP6528361B2
JP6528361B2 JP2014125940A JP2014125940A JP6528361B2 JP 6528361 B2 JP6528361 B2 JP 6528361B2 JP 2014125940 A JP2014125940 A JP 2014125940A JP 2014125940 A JP2014125940 A JP 2014125940A JP 6528361 B2 JP6528361 B2 JP 6528361B2
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cylinder
piston
disk
input
input shaft
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JP2016003746A (en
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寛孝 岸田
寛孝 岸田
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日本精工株式会社
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Description

  The present invention relates to a toroidal continuously variable transmission that can be used as a transmission for automobiles and various industrial machines.
For example, a double cavity type toroidal continuously variable transmission used as a transmission for an automobile is configured as shown in FIG. 4 and FIG. As shown in FIG. 4, the input shaft 1 is rotatably supported inside the casing 50, and on the outer periphery of the input shaft 1, two input side disks 2, 2 and two output side disks 3, 3 and is attached. Further, an output gear (transmission gear) 4 is rotatably supported on the outer periphery of the middle portion of the input shaft 1. The output side disks 3 and 3 are connected to the cylindrical flanges 4a and 4a provided at the center of the output gear 4 by spline connection.
The input shaft 1 is rotationally driven by the drive shaft 22 via a loading cam type pressing device 12 provided between the input side disk 2 positioned on the left side in FIG. 4 and the cam plate (loading cam) 7. It is supposed to be. In addition, the output gear 4 is supported in the casing 50 via a partition wall 13 configured by coupling of two members, and thereby, can rotate around the axis O of the input shaft 1, while the axis O Directional displacement is blocked.
  The output side disks 3, 3 are rotatably supported centering on the axis O of the input shaft 1 by needle bearings 5, 5 interposed between the output side disks 3 and 3. Further, the input side disk 2 on the left side in FIG. 4 is supported by the input shaft 1 via a ball spline 6, and the input side disk 2 on the right side in FIG. 4 is splined to the input shaft 1 The disk 2 is adapted to rotate with the input shaft 1. In addition, a power roller is provided between the inner side surfaces (concave; also referred to as traction surface) 2a, 2a of the input side disks 2 and 2 and the inner side surfaces (concave; also referred to as traction surfaces) 11 (see FIG. 5) is rotatably held.
  A step 2b is provided on the inner peripheral surface 2c of the input-side disc 2 positioned on the right side in FIG. 4, and the step 1b provided on the outer peripheral surface 1a of the input shaft 1 is butted against the step 2b. At the same time, the rear surface (right surface in FIG. 4) of the input side disk 2 is abutted against the loading nut 9 screwed to the screw formed on the outer peripheral surface of the input shaft 1. Thereby, the displacement of the input 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 portion 1 d of the input shaft 1, and the disc spring 8 has concave surfaces 2 a, 2 a, 3 a of the respective disks 2, 2, 3, 3. , 3a and a contact portion between the peripheral surfaces 11a and 11a of the power rollers 11 and 11, a pressing force (preload) is applied.
  FIG. 5 is a cross-sectional view taken along the line AA of FIG. As shown in FIG. 5, inside the casing 50, a pair of trunnions 15, 15 swinging around a pair of pivots 14, 14 located at a twisted position relative to the input shaft 1 are provided. In FIG. 5, the illustration of the input shaft 1 is omitted. Each of the trunnions 15, 15 is a pair of bent wall portions 20, 20 formed at both end portions in the longitudinal direction (vertical direction in FIG. 5) of the support plate portion 16 so as to be bent toward the inner side surface of the support plate portion 16. have. A concave pocket portion P for accommodating the power roller 11 is formed in each of the trunnions 15, 15 by the bent wall portions 20, 20. The pivots 14 and 14 are provided concentrically with each other on the outer surface of each of the bent wall portions 20 and 20.
  A circular hole 21 is formed in the central portion of the support plate portion 16, and a base end 23 a of the displacement shaft 23 is supported by the circular hole 21. The tilt angles of the displacement shafts 23 supported at the central portions of the trunnions 15, 15 can be adjusted by swinging the trunnions 15, 15 about the pivots 14, 14, respectively. In addition, each power roller 11 is rotatably supported around the tip 23 b of the displacement shaft 23 protruding from the inner side surface of each trunnion 15, 15, and each power roller 11 is a disk on each input side 2, 2 and each output side disc 3, 3 are held. The proximal end 23a and the distal end 23b of each displacement shaft 23, 23 are eccentric to each other.
  The pivot shafts 14 and 14 of the trunnions 15 and 15 are respectively swingably supported on the pair of yokes 23A and 23B and displaceable in the axial direction (vertical direction in FIG. 5). The horizontal movement of trunnions 15, 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 23A and 23B, and pivot shafts 14 provided at both ends of the trunnion 15 are respectively pivoted through the radial needle bearings 30 in these support holes 18 It is freely supported. Further, a circular locking hole 19 is provided at the central portion in the width direction (left and right direction in FIG. 5) of the yokes 23A and 23B, and the inner peripheral surface of the locking hole 19 is a cylindrical surface. 64, 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 a spherical post 68 and a drive for supporting the same. It is pivotally supported by the upper cylinder body 56 of the cylinder 31.
  The displacement shafts 23 and 23 provided in the trunnions 15 and 15 are provided at positions 180 degrees opposite to each other with respect to the input shaft 1. Further, the direction in which the distal end portion 23b of each displacement shaft 23, 23 is eccentric with respect to the base end portion 23a is the same direction with respect to the rotation direction of both the disks 2, 2, 3 and 3 (in FIG. In the opposite direction). In addition, the eccentric direction is a direction substantially orthogonal to the arrangement direction of the input shaft 1. Therefore, each power roller 11 is supported so as to be slightly displaceable 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 or the like of each component based on the thrust load generated by the pressing device 12, each configuration 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 (thrust bearing) 24 and a thrust rolling bearing are sequentially arranged from the outer surface side of the power roller 11. And thrust needle bearings 25 are provided. Among these, the thrust ball bearings 24 allow 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 has a plurality of balls (hereinafter referred to as rolling elements) 26, 26 and an annular cage 27 for rollingly holding the rolling elements 26, 26, and a circle. It comprises 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 face) 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 side surface of the support plate portion 16 of the trunnion 15 and the outer side surface of the outer ring 28. The thrust needle bearing 25 supports the thrust load applied from the power roller 11 to the outer rings 28 and causes the power roller 11 and the outer ring 28 to swing around the proximal end 23 a of each displacement shaft 23. Tolerate.
  Further, drive rods (trunnion shafts) 29, 29 are provided at one end (lower end in FIG. 5) of each trunnion 15, 15, and a drive piston (an outer peripheral surface between the drive rods 29, 29 is provided) Hydraulic pistons 33, 33 are fixed. Each of the drive pistons 33, 33 is oil-tightly fitted in a drive cylinder 31 formed of an upper cylinder body 56 and a lower cylinder body 57. The drive pistons 33, 33 and the drive cylinder 31 constitute a drive device 32 for displacing the trunnions 15, 15 in the axial direction of the pivot shafts 14, 14 of the trunnions 15, 15.
  In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 1 is transmitted to the input side disks 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 output to the output gear 4. It is taken out.
When changing the rotational speed ratio between the input shaft 1 and the output gear 4, the drive pistons 33, 33 are displaced in opposite directions. With the displacement of the drive pistons 33, the pair of trunnions 15, 15 are displaced in opposite directions. For example, the power roller 11 on the left side in FIG. 5 is displaced downward, and the power roller 11 on the right side in FIG. 5 is displaced upward.
As a result, it acts on the contact portions between the circumferential surfaces 11a and 11a of the power rollers 11 and the inner side surfaces 2a 2a 3a and 3a of the input side disks 2 and 2 and the output side disks 3 and 3, respectively. The direction of the tangential force changes. Then, with the change in the direction of the force, the trunnions 15, 15 swing (tilt) in opposite directions with respect to the pivots 14, 14 pivotally supported by the yokes 23A, 23B.
  As a result, the contact positions of the circumferential surfaces 11a, 11a of the power rollers 11, 11 and the inner side surfaces 2a, 3a change, and the rotational speed ratio between the input shaft 1 and the output gear 4 changes. In addition, 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, 11 and the outer rings attached to the power rollers 11, 11 28, 28 slightly pivot about the proximal ends 23a, 23a of the respective displacement axes 23, 23. Since the thrust needle bearings 25 and 25 exist between the outer surface of each of the outer rings 28 and 28 and the inner surface of the support plate portion 16 constituting each of the trunnions 15 and 15, respectively, the rotation smoothly proceeds. It will be. Therefore, as described above, the force for changing the inclination angle of each displacement shaft 23, 23 may be small.
A hydraulic pressure device may be used as the above-mentioned pressure device 12. What was described in patent documents 1 as an example of this hydraulic type pressing device is known.
FIG. 6 is a cross-sectional view showing the pressing device 40 of the toroidal continuously variable transmission described in Patent Document 1. As shown in FIG.
The pressing device 40 includes a first cylinder 41 integrated with the input end 1 a of the input shaft 1, a second cylinder 59 integrated with the input disc 2, a first piston 61, and a second piston 60. Is equipped. The first cylinder portion 41 is engaged with the outer periphery of the second cylinder portion 59, and is disposed in a state of facing the back surface 2d of the input side disk 2. The second cylinder portion 59 is formed in a cylindrical shape, and extends from the outer peripheral edge of the input side disk 2 toward the first cylinder portion 41.
  The second piston portion 60 has its inner circumferential surface fitted to the outer circumferential surface of the input shaft 1 and its outer circumferential surface fitted to the inner circumferential surface of the second cylinder portion 59. It is distribute | arranged in the state facing the back 2d. Further, the inner peripheral surface of the first piston portion 61 is fitted to the outer peripheral surface of the input shaft 1, and the outer peripheral surface is slidably fitted to the inner peripheral surface of the first cylinder portion 41. The second piston portion 60 and the first cylinder portion 41 are disposed.
  A space surrounded by the inner surface of the first cylinder portion 41, the first piston portion 61, and a part of the outer peripheral surface of the input shaft 1 constitutes a first hydraulic chamber (oil chamber) 70. The first hydraulic chamber 70 is kept fluid-tight (fluid-tight and airtight) by seal members 71 and 72 mounted on the outer peripheral portion and the inner peripheral portion of the first piston portion 61. Further, a space surrounded by the inner circumferential surface of the second cylinder portion 59, the second piston portion 60, the back surface 2d of the input side disk 2 and a part of the outer circumferential surface of the input shaft 1 is a second hydraulic chamber (Oil chamber) 67 is configured. The second hydraulic chamber 67 is kept fluid tight by the seal member 65 mounted on the outer peripheral portion of the second piston portion 60. In addition, on the inner peripheral side of the second cylinder portion 59, a space 75 located between the second piston portion 60 and the first piston portion 61 is an air chamber. The air chamber 75 is kept fluid tight by a plurality of seal members 65, 72. Further, the second cylinder portion 59 has a gap S between itself and the first piston portion 61 which also functions as a communication groove for communicating the air chamber 75 to the outside, and the first piston portion via the gap S It can be in contact with 61. And between the 1st piston part 61 and the 2nd cylinder part 59, disc spring 100 for applying pre-load is inserted. In this case, the disc spring 100 is disposed in a state of being constantly in contact with the second cylinder portion 59 by the plate 102 for preload adjustment.
In order to supply oil to the respective hydraulic pressure chambers 67 and 70, an oil passage is formed in the drive shaft on the engine side. Specifically, an inner hole 1f coaxial with the axis O is formed in the input end portion 1a of the input shaft 1 along the longitudinal direction, and a drive shaft coupled to the input shaft 1 is formed in the inner hole 1f. The extension part of the is to be inserted. Further, an oil passage extending in the longitudinal direction and an oil hole extending in a radial direction orthogonal to the oil passage are formed in the extension portion. Further, oil holes 82 and 80 are formed in the input shaft 1 to connect the oil holes and the oil pressure chambers 67 and 70, respectively.
The first oil hole 80 communicating with the first hydraulic chamber 70 extends radially so as to be orthogonal to the axis O of the input shaft 1 and the second oil hole 82 communicating with the second hydraulic chamber 67 is the input shaft It extends obliquely to the axis O of 1.
  In the pressing device 40 having such a configuration, when the pressure oil is supplied into the second hydraulic chamber 67, the pressure oil is input in the direction in which the second piston portion 60 and the back surface 2d of the input side disk 2 separate from each other. Move the side disc 2 Thereby, the input side disc 2 is pressed toward the output side disc. On the other hand, when the pressure oil is supplied into the first hydraulic chamber 70, the pressure oil moves the first cylinder portion 41 in the direction in which the first piston portion 61 and the first cylinder portion 41 are separated. As a result, the input shaft 1 integrally formed with the first cylinder portion 41 moves to the engine side, is located far from the engine, and is provided on the input shaft 1 with its outward movement in the axial direction restricted. The disc 2 is pressed against the output disc. Thus, the traction part of each power roller is in rolling contact with both the input / output side disks 2 and 3 to transmit the rotational drive force of the input side disk 2 to the output side disk 3 at a desired reduction ratio.
Patent No. 4605495
By the way, in the toroidal type continuously variable transmission provided with the pressing device as shown in FIG. 6, an annular recessed groove is provided on the side surface on the outer diameter side of the first piston portion 61, and this recessed groove is a disc spring as an elastic member. I have inserted 100. Therefore, it is necessary to form the first piston portion 61 thickly by the amount of providing the recessed groove, which causes an increase in the weight of the first piston portion.
In addition, since the outer diameter side of the first piston portion 61 receives a load from the second cylinder portion 59, it becomes a high stressed area, but since the concave groove is provided at this high stressed area, the durability of the first piston portion is deteriorated. Are concerned.
Furthermore, the contact portion between the second cylinder portion 59 and the first piston portion 61 causes fretting wear due to the deformation of the input side disk 2 integrally formed with the second cylinder portion 59 (which is deformed by being pressed by the power roller). In order to reduce the contact pressure, a predetermined contact area is required. In this case, it is necessary to reduce the inner diameter of the second cylinder portion 59 or to increase the outer diameter of the input side disk 2, which results in an increase in pump pressure or an increase in weight of the second cylinder portion.
  The present invention has been made in view of the above-mentioned circumstances, and even if an elastic member such as a disc spring is provided, the pump of the second cylinder portion does not cause an increase in weight of the first piston portion and a decrease in durability. It is an object of the present invention to provide a toroidal continuously variable transmission provided with a pressing device which does not cause an increase in pressure or an increase in weight.
In order to achieve the above object, the toroidal type continuously variable transmission of the present invention comprises a first disc and a second disc concentrically and rotatably provided to each other with their respective inner side surfaces facing each other. A power roller interposed between the two disks, and a hydraulic pressing device disposed on the back side of the first disk and pressing the first disk toward the second disk.
The pressing device includes a first cylinder portion provided on the back side of the first disc, a second cylinder portion integrally provided with the first disc, and a first cylinder portion provided on the first cylinder portion. A piston portion and a second piston portion provided in the second cylinder portion;
With the introduction of oil into the first hydraulic chamber of the first cylinder portion, the first piston portion and the first cylinder portion move in the axial direction so as to be separated from each other, and the first piston portion (2) A toroidal type in which the second piston portion and the second cylinder portion move in the axial direction so as to be separated from each other with the introduction of oil into the second hydraulic pressure chamber of the second cylinder portion. It is a continuously variable transmission,
The contact portion between the second cylinder portion and the first piston portion is axially inner than the end face on the outer diameter side with which the first piston portion of the second cylinder portion abuts, and the second cylinder portion An elastic member is provided between the inner diameter surface side and the first piston portion , the other end of the elastic member being in contact with the side surface of the first piston portion while the other end is the second cylinder. characterized in that it is engaged with the engaging portion formed by the inner surface of the snap ring fitted in an annular groove provided on the inner surface and the second cylinder portion parts.
In the present invention, in the contact portion between the second cylinder portion and the first piston portion, the second cylinder portion is axially inner than the end surface on the outer diameter side with which the first piston portion of the second cylinder portion contacts. Since an elastic member is provided between the inner diameter surface side of the first piston portion and the first piston portion, a recess for inserting an elastic member such as a disc spring on the side surface on the outer diameter side of the first piston portion unlike the prior art. There is no need to provide a groove. Therefore, since it is not necessary to form the first piston portion thickly, the weight increase of the first piston portion is not caused.
Also, since the outer diameter side of the first piston portion receives a load from the second cylinder portion, it becomes a high stressed area, but since it is not necessary to provide the above-mentioned recessed groove in this high stressed area, the first piston portion It does not cause a decrease in the durability of the
Furthermore, the contact portion between the second cylinder portion and the first piston portion needs a predetermined contact area to reduce the contact surface pressure, but unlike the conventional case, the side surface on the outer diameter side of the first piston portion Since it is not necessary to provide a recessed groove for inserting an elastic member such as a spring, it is not necessary to reduce the inner diameter of the second cylinder portion or to increase the outer diameter of the input side disk. Therefore, the increase in pump pressure or the increase in weight of the second cylinder portion does not occur.
In the configuration of the present invention, the inner surface side of the second cylinder portion, the engaging portion for engaging said elastic member that is provided.
  According to such a configuration, the elastic member is engaged with the engagement portion provided on the inner diameter side of the second cylinder portion to ensure that the elastic member is positioned in the axial direction of the second cylinder portion. Can.
  According to the first aspect of the present invention, even if an elastic member such as a disc spring is provided in the pressing device, the weight increase and the durability decrease of the first piston portion are not caused, and the pump pressure of the second cylinder portion Does not cause an increase in weight or an increase in weight.
FIG. 1 is a cross-sectional view of a toroidal continuously variable transmission according to a first embodiment of the present invention. It is sectional drawing of the press apparatus equally. The press apparatus of the toroidal type continuously variable transmission which concerns on the 2nd Embodiment of this invention is shown, (a) is sectional drawing, (b) is an expanded sectional view of 2nd cylinder part vicinity. It is sectional drawing which shows an example of the conventional toroidal type continuously variable transmission. It is sectional drawing in alignment with the AA in FIG. The other example of the conventional toroidal type continuously variable transmission is shown, and it is sectional drawing of the press apparatus.
Hereinafter, embodiments of the present invention will be described with reference to the drawings. The same reference numerals as in the toroidal continuously variable transmission of the present embodiment and the conventional toroidal continuously variable transmission shown in FIGS. 4 to 6 denote the same parts, and a description thereof will be omitted or simplified.
First Embodiment
The toroidal type continuously variable transmission according to the first embodiment shown in FIG. 1 is, for example, an input shaft 1, an input side disc 2, an output side disc 3A, an outer peripheral gear 4A, before being accommodated in a casing. Upper and lower yokes 23A and 23B, trunnion, power roller 11, drive device 32, hydraulic pressing device 40, fixing member 52 (upper plate) and the like are integrally assembled into a variator module 43, and the variator module 43 is a casing It is housed inside and attached.
  In such a variator module 43, the lower spherical post 68 fixed to the upper cylinder body 56 and the lower cylinder body 57 constituting the drive cylinder 31 of the drive device 32, and the upper one fixed to the upper plate 52. The spherical post 64 is a columnar post 69 integrally joined in the upper and lower direction, and in the variator module 43, a pair of columnar posts 69 is the upper plate 52, the cylinder body of the drive cylinder 31 (upper cylinder body 56 and lower cylinder body 57 ) Is connected.
Further, the input shaft 1 is in a state in which the upper and lower central portions of the columnar posts 69 pass through. The input shaft 1 supports a pair of input side disks 2 and 2, an output side disk 3A, a pressing device 40 and the like.
The output side disk 3A is rotatably supported by the input shaft 1 via a radial needle bearing (radial bearing) 35.
In addition, an output side disk 3A is disposed between the pair of columnar posts 69, and the output side disk 3A is axially positioned at both ends in the axial direction of the output side disk 3A and is thrust rotatably supported about the axis. A bearing 55 is provided. That is, the thrust ball bearing (thrust bearing) 55 is disposed between the columnar post 69 and the small diameter end of the output side disk 3A, and the position of the output side disk 3A in the axial direction of the input shaft 1 is restricted. And allows rotation about the axis of the output side disk 3A.
  Next, the pressing device 40 will be described with reference to FIG. This pressing device 40 is an improvement of the conventional pressing device shown in FIG. Therefore, in the following, only the points in which the pressing device 40 in the present embodiment is different from the pressing device 40 shown in FIG. 5 will be described, and the other common parts will be assigned the same reference numerals to omit or simplify the description.
  The pressing device 40 includes a first cylinder portion 41 coupled to the right end portion of the input shaft 1, a second cylinder portion 59 provided on the input side disk 2, an annular first piston portion 61, and an annular second And a piston unit 60.
A space surrounded by the inner surface of the first cylinder portion 41, the first piston portion 61, and a part of the outer peripheral surface of the input shaft 1 constitutes a first hydraulic chamber.
Further, a space surrounded by the inner circumferential surface of the second cylinder portion 59, the second piston portion 60, the back surface 2d of the input side disk 2 and a part of the outer circumferential surface of the input shaft 1 is a second hydraulic chamber It constitutes 67.
In addition, on the inner peripheral side of the second cylinder portion 59, a space 75 located between the second piston portion 60 and the first piston portion 61 is an air chamber. Further, the second cylinder portion 59 has a gap S between itself and the first piston portion 61 which also functions as a communication groove for communicating the air chamber 75 to the outside, and the first piston portion via the gap S It can be in contact with 61.
In order to supply oil to the respective hydraulic chambers 67, 70, an inner hole 1f is formed at the input end 1a of the input shaft 1, and an extension of a drive shaft coupled to the input shaft 1 is formed in the inner hole 1f. The part is to be inserted. Oil is supplied from the extended portion to the inner hole 1 f. Further, an oil hole 80 connecting the inner hole 1 f and the first hydraulic chamber 70 is formed in the input shaft 1, an oil hole 81 is formed in the middle of the oil hole 80, and the oil hole 81 and the second oil hole 81 are further formed. An oil hole 82 connecting the hydraulic chamber 67 is formed.
The oil hole 80 communicating with the first hydraulic chamber 70 extends obliquely with respect to the axial direction of the input shaft 1, and the oil hole 82 communicating with the second hydraulic chamber 67 perpendicularly intersects with the axial direction of the input shaft 1. An oil hole 81 extending between the oil hole 80 and the oil hole 82 extends obliquely with respect to the axial direction of the input shaft 1.
Further, between the first piston portion 61 and an inner side in the axial direction (left side in FIG. 2) of the end face 59 a of the second cylinder portion 59 with which the first piston portion 61 abuts, A disc spring 100 is provided as an elastic member for applying a preload.
That is, first, on the inner diameter surface of the second cylinder portion 59, an annular recessed groove 101 is formed along the circumferential direction. The recessed groove 101 is formed on the inner side in the axial direction from the end face 59a of the second cylinder portion 59, and an annular retaining ring 102A is fitted to the recessed groove 101.
The outer peripheral side of the disc spring 100 is engaged with a corner portion formed by the side surface of the snap ring 102A facing the first piston portion 61 and the tip inner diameter surface of the second cylinder portion 59. That is, the corner formed by the snap ring 102A fitted in the recessed groove 101 and the inner diameter surface of the tip of the second cylinder 59 corresponds to the engaging portion 110 according to the present invention. Spring 100 is engaged.
Further, the inner peripheral side of the disc spring 100 protrudes axially outward from the end face 59 a of the second cylinder portion 59, and the protruding inner diameter side is in contact with the side surface on the outer peripheral side of the first piston portion 61.
  In the pressing device 40 having such a configuration, when the pressure oil is supplied into the second hydraulic chamber 67, the pressure oil is input in the direction in which the second piston portion 60 and the back surface 2d of the input side disk 2 separate from each other. Move the side disc 2 Thereby, the input side disc 2 is pressed toward the output side disc. On the other hand, when the pressure oil is supplied into the first hydraulic chamber 70, the pressure oil moves the first cylinder portion 41 in the direction in which the first piston portion 61 and the first cylinder portion 41 are separated. As a result, the input shaft 1 integral with the first cylinder portion 41 moves to the engine side (right side in FIG. 2), and the opposite input located far from the engine via the cotter 9a (see FIG. 1) The side disc 2 is pressed towards the output side disc. Thus, the traction portion of each power roller 11 is in rolling contact with both the input / output disks 2 and 3 and transmits the rotational drive force of the input disk 2 to the output disk 3 at a desired reduction ratio.
  In addition, at the time of such pressing operation (when pressure oil is supplied into the first hydraulic chamber 70 and the second hydraulic chamber 67), the first piston portion 61 fills the gap S with the second cylinder portion 59. Of the disc spring 100, which is in contact with the end face 59a of the second cylinder portion 59, and the first piston portion 61 and the second cylinder portion 59 abut each other. The amount remains only for the length of the gap S.
  As described above, in the present embodiment, the disc spring 100 as an elastic member for applying a preload is interposed between the first piston portion 61 and the second cylinder portion 59. Even when the pressure is increased by supplying oil into the inner and second hydraulic chambers 67, the amount of compression of the disc spring 100 is limited by the first piston portion 61 and the second cylinder portion 59 abutting on each other. Since over-constriction of the disc spring 100 is prevented, it is possible to reduce the change in thrust. That is, the change of the pressing force can be suppressed, and the thrust from the pressing device 40 can be prevented from becoming excessive or too small. As a result, it is possible to prevent the decrease in the efficiency and the durability of the toroidal continuously variable transmission. In addition, since the amplitude of the disc spring 100 is reduced, fatigue of the disc spring 100 can be suppressed.
  In addition, a disc spring 100 is provided axially inside the end face 59a of the second cylinder part 59 on which the first piston part 61 abuts and between the inner diameter side of the second cylinder part 59 and the first piston part 61. Therefore, unlike the prior art, it is not necessary to provide a recess on the outer diameter side of the first piston portion 61 for inserting an elastic member such as a disc spring. Therefore, since it is not necessary to form the first piston portion 61 thicker than the first piston portion 61 shown in FIG. 6, the weight increase of the first piston portion is not caused.
In addition, the outer diameter side of the first piston portion 61 receives a load from the second cylinder portion 59, and thus becomes a high stressed portion, but since it is not necessary to provide a recessed groove in this high stressed portion, the first piston portion 61 There is no reduction in durability.
Furthermore, although the contact portion between the second cylinder portion 59 and the first piston portion 61 requires a predetermined contact area to reduce the contact surface pressure, the side surface on the outer diameter side of the first piston portion 61 is different from the prior art. In addition, since it is not necessary to provide a recessed groove for inserting an elastic member such as a disc spring, it is not necessary to reduce the inner diameter of the second cylinder portion 59 or to increase the outer diameter of the input side disk 2. Therefore, the increase in pump pressure or the increase in weight of the second cylinder portion 59 does not occur.
In addition, the snap ring 102A is fitted in the concave groove 101 provided on the inner diameter surface of the second cylinder portion 59, and the corner portion formed by the snap ring 102A and the tip inner diameter surface of the second cylinder portion 59 Since the outer peripheral side of the disc spring 100 is engaged with the engaging portion 110), the positioning of the second cylinder portion 59 of the disc spring 100 in the axial direction can be reliably performed.
Further, unlike the conventional case, since the disc spring 100 is not fitted in the recessed groove, the radial width of the disc spring 100 can be easily expanded, and the difference between the inner and outer diameters of the disc spring 100 can be increased. .
Second Embodiment
FIG. 3 shows a second embodiment, and is a cross-sectional view of the pressing device 40. As shown in FIG. This pressing device 40 differs from the pressing device 40 in the first embodiment in how to attach the disc spring 100 as an elastic member, so this point will be described below, and the pressing in the first embodiment will be described. The same parts as those of the apparatus are denoted by the same reference numerals and the description thereof is omitted.
In the first embodiment, the outer peripheral side of the disc spring 100 is formed by the snap ring 102A fitted in the concave groove 101 on the inner diameter side of the second cylinder portion 59 and the tip inner diameter surface of the second cylinder portion 59. In the present embodiment, the outer peripheral side of the disc spring 100 is engaged in the following manner, while the corner portion (engaging portion 110) is engaged.
That is, the cylindrical shape having a predetermined step with the inner diameter surface on the inner diameter surface of the tip end of the second cylinder portion 59 in the axial direction from the end face 59a of the second cylinder portion 59 which contacts the first piston portion 61. A stepped surface 103 is formed along the circumferential direction, and an annular installation surface 104 orthogonal to the stepped surface 103 is formed along the circumferential direction.
The outer diameter side of the disc spring 100 is engaged with the corner formed by the step surface 103 and the installation surface 104. That is, such a corner corresponds to the engaging portion 111 according to the present invention, and the disc spring 100 is engaged with the engaging portion 111.
Further, the inner peripheral side of the disc spring 100 protrudes axially outward from the end face 59 a of the second cylinder portion 59, and the protruding inner diameter side is in contact with the side surface on the outer peripheral side of the first piston portion 61.
  According to the present embodiment, in addition to the same effects as in the first embodiment, the engaging portion 111 (step surface for engaging the disc spring 100) is obtained as compared with the first embodiment. The corner formed by the mounting surface 103 and the mounting surface 104 can be easily formed, and since the retaining ring 102A is not necessary, the cost can be reduced accordingly.
  In the toroidal type continuously variable transmission, the input / output relationship between the input disc and the output disc may be reversed. Therefore, the present invention can be applied to the case where the input side disk 2 and the output side disk 3 are interchanged. The present invention can also be applied to full toroidal continuously variable transmissions as well as half toroidal continuously variable transmissions.
2 Input disk (first disk)
3 Output side disk (second disk)
11 power roller 40 pressing device 41 first cylinder portion 59 second cylinder portion 59a end face 60 second piston portion 61 first piston portion 67 second hydraulic chamber 70 first hydraulic chamber 100 disc spring (elastic member)
101 concave groove 102A retaining ring 103 step surface 104 installation surface 110 engagement portion 111 engagement portion

Claims (1)

  1. A first disk and a second disk concentrically and rotatably provided to each other in a state in which the respective inner surfaces face each other, a power roller sandwiched between the both disks, and the first disk And a hydraulic pressing device disposed on the back side and pressing the first disk toward the second disk,
    The pressing device includes a first cylinder portion provided on the back side of the first disc, a second cylinder portion integrally provided with the first disc, and a first cylinder portion provided on the first cylinder portion. A piston portion and a second piston portion provided in the second cylinder portion;
    With the introduction of oil into the first hydraulic chamber of the first cylinder portion, the first piston portion and the first cylinder portion move in the axial direction so as to be separated from each other, and the first piston portion (2) A toroidal type in which the second piston portion and the second cylinder portion move in the axial direction so as to be separated from each other with the introduction of oil into the second hydraulic pressure chamber of the second cylinder portion. It is a continuously variable transmission,
    The contact portion between the second cylinder portion and the first piston portion is axially inner than the end face on the outer diameter side with which the first piston portion of the second cylinder portion abuts, and the second cylinder portion An elastic member is provided between the inner diameter surface side and the first piston portion , the other end of the elastic member being in contact with the side surface of the first piston portion while the other end is the second cylinder. toroidal type continuously variable, characterized in that is engaged with the engaging portion formed by the inner surface of the snap ring fitted in an annular groove provided on the inner surface and the second cylinder portion parts transmission.
JP2014125940A 2014-06-19 2014-06-19 Toroidal type continuously variable transmission Active JP6528361B2 (en)

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JP6528361B2 true JP6528361B2 (en) 2019-06-12

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Publication number Priority date Publication date Assignee Title
JP4605495B2 (en) * 2004-08-17 2011-01-05 日本精工株式会社 Toroidal continuously variable transmission
JP4696537B2 (en) * 2004-11-18 2011-06-08 日本精工株式会社 Toroidal continuously variable transmission

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