JP4079691B2 - Toroidal continuously variable transmission - Google Patents

Description

[0001]
[Industrial application fields]
The toroidal continuously variable transmission according to the present invention is used as a transmission unit constituting an automatic transmission for an automobile or as a transmission for adjusting the operating speed of various industrial machines such as a pump.
[0002]
[Prior art]
A toroidal-type continuously variable transmission is known as a type of transmission unit that constitutes a transmission for an automobile, and is partially implemented. Such toroidal type continuously variable transmissions already implemented in part have been described in many publications such as JP-A-2-283949, JP-A-8-4869, and JP-A-8-61453. As is well known, the basic structure will be described with reference to FIG. The structure shown in FIG. 3 is a so-called double cavity type in which the transmission of power from the input unit to the output unit is divided into two parallel systems. On the other hand, so-called single-cavity toroidal continuously variable transmissions that transmit power by only one system are also well-known in many publications.
[0003]
In the case of the double-cavity toroidal-type continuously variable transmission shown in FIG. 3, around the intermediate portion proximal end (left side in FIG. 3) of the input side rotary shaft 1 corresponding to the rotary shaft described in the claims, The input side disk 2a, which is the first disk described in the claims, is similarly provided with another input side disk 2b around the tip (right side in FIG. 3), and the input side inner surfaces 3, 3 each having a toroidal curved surface. In a state where they are opposed to each other, they are concentrically supported via ball splines 4 and 4 respectively. Accordingly, both the input side disks 2a and 2b are supported around the input side rotary shaft 1 so as to be freely displaceable in the axial direction of the input side rotary shaft 1 and in synchronization with the input side rotary shaft 1. Has been.
[0004]
The ball splines 4 and 4 are respectively male spline grooves 5 and 5 formed on the outer peripheral surface of the input side rotating shaft 1 and female spline grooves 6 and 6 formed on the inner peripheral surfaces of the input side disks 2a and 2b. A plurality of balls 7 and 7 are provided so as to be freely rollable. Further, a rolling bearing 8 and a loading cam type pressing device 9 are provided between the base end portion of the input side rotating shaft 1 and the outer surface of the input side disk 2a as the first disk. The cam plate 10 constituting the pressing device 9 can be driven to rotate by a drive shaft 11. On the other hand, a loading nut 12 and a disc spring 13 having a large elasticity are provided between the tip of the input side rotating shaft 1 and the outer surface of the other input side disk 2b.
[0005]
The intermediate portion of the input side rotating shaft 1 is inserted through a through hole 15 provided in a partition wall portion 14 provided in a casing housing a toroidal type continuously variable transmission. A cylindrical sleeve 16 is rotatably supported by a pair of rolling bearings 17, 17 on the inner diameter side of the through hole 15, and an output gear 18 is fixed to the outer peripheral surface of the intermediate portion of the sleeve 16. ing. Further, output side discs 19a and 19b are respectively supported at both ends of the sleeve 16 so as to be rotatable in synchronism with the sleeve 16 by spline engagement. . In this state, the output side inner side surfaces 20 and 20 of the output side disks 19a and 19b, each of which is a toroidal curved surface, face the input side inner side surfaces 3 and 3, respectively. Further, between the inner peripheral surfaces of these output side disks 19a, 19b, the portions that protrude from the edge of the sleeve 16, and the outer peripheral surface of the intermediate portion of the input side rotary shaft 1, respectively, needle bearings 21, 21 is provided so as to freely rotate and axially displace the output side disks 19a and 19b with respect to the input side rotating shaft 1 while supporting a load applied to the output side disks 19a and 19b. Of these two output-side disks 19a and 19b, the output-side disk 19a on the side close to the pressing device 9 (left side in FIG. 3) corresponds to the second disk described in the claims.
[0006]
In addition, a plurality (generally two or three) of power rollers are provided in the space (cavity) between the input-side and output-side inner side surfaces 3 and 20 around the input-side rotary shaft 1. 22 and 22 are arranged. Each of the power rollers 22 and 22 has a spherical convex surface on the peripheral surface that abuts on the input side and output side inner side surfaces 3 and 20, and trunnions 23 and 23 corresponding to the support members described in the claims. Is supported by the displacement shafts 24, 24, radial needle bearings 25, 25, thrust ball bearings 26, 26, and thrust needle bearings 27, 27 so as to be able to rotate and slightly swing and displace. Yes. That is, each of the displacement shafts 24, 24 is an eccentric shaft in which the base half and the first half are eccentric from each other, and the base half of the shafts is placed in the middle of each trunnion 23, 23 and another radial (not shown). The needle bearing is supported so as to be able to swing and displace.
[0007]
The power rollers 22 and 22 are rotatably supported by the radial needle bearings 25 and 25 and the thrust ball bearings 26 and 26 on the front half portions of the displacement shafts 24 and 24, respectively. Further, the displacement of each of the power rollers 22 and 22 in the axial direction of the input-side rotary shaft 1 based on the elastic deformation of each constituent member is caused by the separate radial needle bearing and the thrust needle bearings 27 and 27. It is free. Further, the trunnions 23, 23 are supported by pivots provided at both ends (in the front and back directions in FIG. 3) so as to be displaceable in the clockwise and counterclockwise directions in FIG. It can be displaced in the axial direction (front and back direction in FIG. 3).
[0008]
During operation of the toroidal-type continuously variable transmission configured as described above, the drive shaft 11 rotates and drives the input side disk 2a corresponding to the first disk via the pressing device 9. The pressing device 9 rotationally drives the input side disk 2a while generating an axial thrust, so that a pair of input side disks 2a and 2b including the input side disk 2a are connected to the output side disks 19a, While being pressed toward 19b, they rotate in synchronization with each other. As a result, the rotation of the input disks 2a and 2b is transmitted to the output disks 19a and 19b via the power rollers 22 and 22, and the output disks 19a and 19b are transmitted via the sleeve 16. The output gear 18, which is coupled to, rotates.
[0009]
During operation, the thrust generated by the pressing device 9 secures the surface pressure of each contact portion between the peripheral surface of each of the power rollers 22 and 22 and the input side and output side inner side surfaces 3 and 20. The surface pressure increases as the power (torque) transmitted from the drive shaft 11 to the output gear 18 increases. For this reason, good transmission efficiency can be obtained regardless of torque change. Further, even when the torque to be transmitted is zero or very small, the preload spring 28 provided on the inner diameter side of the pressing device 9 ensures a certain level of surface pressure at each contact portion. Therefore, torque transmission at each of the abutting portions is smoothly performed without excessive sliding immediately after startup.
[0010]
When changing the gear ratio between the drive shaft 11 and the output gear 18, the trunnions 23, 23 are displaced in the front and back direction in FIG. 3 by an actuator (not shown). In this case, the trunnions 23 and 23 in the upper half part and the trunnions 23 and 23 in the lower half part of FIG. 3 are displaced in the opposite directions by the same amount. Along with this displacement, the direction of the force applied in the tangential direction of the contact portion between the peripheral surface of each of the power rollers 22 and 22 and the input side and output side inner side surfaces 3 and 20 changes. Then, the trunnions 23 and 23 swing around the pivots provided at both ends by the tangential force. With this swinging, the positions of the contact portions between the peripheral surfaces of the power rollers 22 and 22 and the input side and output side inner side surfaces 3 and 20 in the radial direction of the inner side surfaces 3 and 20 are changed. Change. The gear ratio changes to the speed increasing side as these abutting portions change radially outward of the input side inner surface 3 and radially inward of the output side inner surface 20. On the other hand, the gear ratio changes to the deceleration side as the contact portions change inward in the radial direction of the input side inner surface 3 and outward in the radial direction of the output side inner surface 20. .
[0011]
In the case of the above-described conventional structure, a mechanical device is used as the pressing device 9 for ensuring the surface pressure of each contact portion between the peripheral surface of each power roller 22 and 22 and the input side and output side inner side surfaces 3 and 20. A loading cam device was used. In the case of such a mechanical pressing device 9, the surface pressure can be adjusted according to the torque to be transmitted, but the surface pressure cannot be adjusted by other elements. On the other hand, in order to further improve the transmission efficiency and durability of the toroidal-type continuously variable transmission, for example, it is conceivable to change the surface pressure by a temperature change that leads to a viscosity change of the traction oil. Furthermore, in order to realize a continuously variable transmission that combines a toroidal type continuously variable transmission and a planetary gear mechanism, it is necessary to adjust the surface pressure in addition to factors other than torque.
[0012]
For example, in Japanese Patent Publication No. 47-962, an input side disk is oil-tightly fitted in a cylinder cylinder fixed to the outer peripheral surface of an input shaft, and the cylinder cylinder and the input side disk are key-engaged. A structure in which a preload spring is provided between the cylinder and the input side disk is described. According to such a structure, the surface pressure of the contact portion between the inner surface of each disk on the input side and the output side and the outer peripheral surface of each power roller is transmitted by changing the hydraulic pressure introduced into the cylinder cylinder. It can be changed in consideration of factors other than power torque. Therefore, it is considered that control that further improves the transmission efficiency and durability of the toroidal-type continuously variable transmission is possible.
[0013]
[Problems to be solved by the invention]
In the case of a toroidal type continuously variable transmission incorporating a hydraulic pressing device, including the structure described in Japanese Patent Publication No. 47-962 described above, a preload spring is installed in the cylinder cylinder. Therefore, the state of the preload spring cannot be confirmed after the assembly of the pressing device is completed. On the other hand, depending on the basic structure of the toroidal continuously variable transmission, there may be a case where the compression amount of the preload spring must be strictly regulated in order to further improve the performance such as transmission performance and durability performance. In such a case, after the assembly of the pressing device, it is necessary to check the state of the preload spring, and it is preferable that the preload spring has a structure that can easily adjust the compression state. .
In view of such circumstances, the toroidal continuously variable transmission of the present invention has been invented to realize a structure in which the state of the preload spring can be confirmed after the assembly of the pressing device is completed.
[0014]
[Means for Solving the Problems]
A toroidal type continuously variable transmission according to the present invention includes a rotary shaft, a first disk, a second disk, a plurality of support members, a plurality of displacement shafts, a plurality of power rollers, and a hydraulic press. Device.
Of these, the first disk is supported around the rotating shaft so that the axial displacement of the rotating shaft is free.
The second disk is disposed concentrically with the first disk, and is rotatable independently of the first disk.
Each of the support members is provided between the first and second disks, and swings about a pivot that is in a twisted position with respect to the central axes of the two disks.
One displacement shaft is provided for each support member.
Each of the power rollers is provided for each of the support members, and is sandwiched between the inner surfaces of the two disks while being rotatably supported by the displacement shafts.
The pressing device is provided between the rotating shaft and the first disk, and presses the first disk toward the second disk by feeding pressure oil.
[0015]
  In particular, in the toroidal type continuously variable transmission of the present invention, the pressing device includes an inner diameter side cylinder ring, an outer diameter side cylinder ring, and a preload spring.
  Of these, the inner diameter side cylinder ring isOil tight on the outer surfaceThe outer fitting is supported.Further, the inner diameter side cylinder ring is formed such that an annular portion is formed in a radially continuous manner from one end portion of the inner diameter side cylindrical portion that can be fitted onto the rotating shaft, and further, the outer peripheral edge of the annular portion. The outer diameter side cylindrical portion is formed in a state continuous with the inner diameter side cylindrical portion in the opposite direction to the inner diameter side cylindrical portion. Is oil-tightly fitted on the rotating shaft.
  The outer diameter side cylinder ring is stretched between the inner diameter side cylinder ring and the first disk. Therefore, the inner peripheral edge of the outer diameter side cylinder ring is the same as the inner diameter side cylinder ring.Of the outer cylinderThe outer peripheral surface is supported in an oil-tight manner so as to be movable in the axial direction. Further, a cylinder cylinder portion formed in a state of being bent toward the first disk at the outer peripheral edge of the outer diameter side cylinder ring is oil-tightly attached to the first disk in a state where relative movement in the axial direction is possible. It is fitted. Then, pressure oil can be freely supplied and discharged into a cylinder space surrounded by the first disk and the inner and outer cylinder rings.
  The preload spring is for pressing the outer diameter side cylinder ring against the first disk. For this purpose, the preload spring is connected to the inner diameter side cylinder ring.Inner peripheral edge on the outer peripheral surface of the outer cylindrical portionIs supported, the side opposite to the first disk is pressed in the outer diameter side cylinder ring.
[0016]
  Furthermore,The inner diameter side cylinder ring is prevented from being displaced in a direction away from the first disk by a cotter locked in a locking groove formed on the outer peripheral surface of the rotating shaft. Then, the inner peripheral edge of the retaining ring locked to the inner diameter side cylinder ring is brought into contact with or close to the outer peripheral edge of the cotter to prevent the inner peripheral edge of the cotter from coming out of the locking groove.is doing.
[0017]
[Action]
  In the case of the toroidal type continuously variable transmission of the present invention configured as described above, the thrust load that presses the first disk toward the second disk by changing the hydraulic pressure introduced into the cylinder space is defined as the transmission torque. Can be arbitrarily adjusted independently. In addition, since the preload spring can be viewed from the outside after the assembly of the pressing device, the amount of compression of the preload spring can be strictly regulated.
  or,In the case of the present invention, Cotter thickness dimensionchangeAdjusting the axial length that allows the first disc to be displaced away from the second disc when the pressing device is inactiveBy doingThe contact state between the inner side surfaces of these discs and the peripheral surface of each power roller can be properly regulated.
[0018]
DETAILED DESCRIPTION OF THE INVENTION
1 and 2 show an example of an embodiment of the present invention. The feature of this example is that the input side disks 2a and 2b, which are the inner surfaces of the first disk, and the input side inner surfaces 3, 3 of the input side disks 2a and 2b, and the output side inner surfaces of the output disks 19c and 19d, which are the inner surfaces of the second disk. 20 and 20 and the peripheral structure 29 and 29 of each power roller 22 and 22 are the points which devised the structure of the hydraulic press apparatus 30 used in order to ensure the surface pressure of the contact part. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIG. 3, the illustration and description of the equivalent parts are omitted or simplified, and the following description will focus on the characteristic parts of the present invention.
[0019]
The pressing device 30 incorporated in the toroidal type continuously variable transmission of this example includes an inner diameter side cylinder ring 31, an outer diameter side cylinder ring 32, and a preload spring 33.
Among these, the inner diameter side cylinder ring 31 is separated from the input side disk 2b, which is the first disk, at a portion near the tip of the outer peripheral surface of the input side rotation shaft 1a (which is closer to the right end in FIG. 1). In a state in which movement in the direction is prevented, the outer fitting is supported in an oil-tight manner.
[0020]
For this reason, in the case of this example, the inner diameter side cylinder ring 31 is formed into a circular ring shape with a crank-shaped section. That is, the inner diameter side cylinder ring 31 has a diameter of the circular ring portion 35 from one end portion (the right end portion in FIGS. 1 and 2) of the inner diameter side cylindrical portion 34 that can be freely fitted without looseness to the input side rotation shaft 1a. It is formed in a state that continues outward in the direction. An outer diameter side cylindrical portion 36 is formed from the outer peripheral edge portion of the annular ring portion 35 in a state of being continuous with the inner diameter side cylindrical portion 34 in the opposite direction. Furthermore, an outward flange-like locking collar portion 37 is formed on the outer peripheral surface of the front half portion (the right half portion in FIGS. 1 and 2) of the outer diameter side cylindrical portion 36. A pair of locking grooves 38 are formed on the outer peripheral surface of the input side rotating shaft 1a facing the inner peripheral surface of the inner diameter side cylindrical portion 34 in a state of being separated in the axial direction. The O-rings 39 and 39 locked to the both locking grooves 38 and 38 are elastically formed between the bottom surfaces of the both locking grooves 38 and 38 and the inner peripheral surface of the inner diameter side cylindrical portion 34. Is compressed.
[0021]
Further, another locking groove 40 is formed in a portion adjacent to the distal end side (the right end side in FIGS. 1 and 2) with respect to the inner diameter side cylindrical portion 34 on the outer peripheral surface of the input side rotating shaft 1a. And while engaging the inner diameter side half part of the cotter 41 in this latching recessed groove 40, the one side surface (left side surface of FIGS. 1-2) of this cotter 41 is made to the one side surface (FIG. 1) of the said annular ring part 35. The right inner side cylinder ring 31 is prevented from moving away from the input side disk 2b. Further, a retaining ring 42 is fitted into the outer diameter side cylindrical portion 36 of the inner diameter side cylinder ring 31, and the inner peripheral edge of the retaining ring 42 is brought into contact with or close to the outer peripheral edge of the cotter 41. The inner peripheral edge of the cotter 41 is prevented from coming out of the locking groove 40. That is, the cotter 41 is formed into an annular shape by combining a pair of elements each having a semicircular arc shape. Therefore, when no countermeasure is taken, the two elements are inadvertently displaced in the direction away from each other, and the inner peripheral edge of the cotter 41 comes out of the locking groove 40. Therefore, in the case of this example, the restraining ring 42 prevents the two elements from being displaced in a direction away from each other. Further, the retaining ring 43 locked in the vicinity of the inner peripheral surface opening of the outer diameter side cylindrical portion 36 prevents the retaining ring 42 from inadvertently coming out of the outer diameter side cylindrical portion 36.
[0022]
Further, in the illustrated example, a plurality of screw holes 44, 44 penetrating the holding ring 42 in the axial direction are formed in a part of the holding ring 42. These screw holes 44, 44 are used when the retaining ring 42 is extracted from the inside of the outer diameter side cylindrical portion 36. That is, when the retaining ring 42 is removed from the outer cylindrical portion 36 for disassembly or repair, a bolt (not shown) is attached to each of the screw holes 44 and 44 with the retaining ring 43 removed. The bolt is abutted, and the front end surface of the bolt is abutted against one side surface of the annular portion 35. And as this reaction, the said restraining ring 42 is displaced to the opening side of the said outer diameter side cylindrical part 36, and is extracted from this outer diameter side cylindrical part 36 inside. When the fitting strength of the holding ring 42 with respect to the outer diameter side cylindrical portion 36 is low, the bolt is used as a clue in a state where the tip end portion of the bolt is screwed into the screw holes 44, 44. An operation of simply pulling out the retaining ring 42 from the outer diameter side cylindrical portion 36 may be performed.
[0023]
The outer diameter side cylinder ring 32 is stretched between the inner diameter side cylinder ring 31 and the input side disk 2b. That is, the inner peripheral edge of the outer diameter side cylinder ring 32 is moved in the axial direction on the outer peripheral surface of the base half part (the left half part in FIGS. 1 and 2) of the outer diameter side cylindrical part 36 constituting the inner diameter side cylinder ring 31. Is supported in an oil-tight manner in a possible state. Therefore, in the case of this example, the seal ring 46 locked in the locking groove 45 formed on the outer peripheral surface of the base half of the outer diameter side cylindrical portion 36 is connected to the inner peripheral edge of the outer diameter side cylinder ring 32. In sliding contact.
[0024]
Further, a cylinder tube portion 47 is formed on the outer peripheral edge portion of the outer diameter side cylinder ring 32 so as to be bent toward the input side disk 2b (left side in FIGS. 1 and 2). The cylinder tube portion 47 is oil-tightly fitted to the input side disk 2b in a state where relative movement in the axial direction is possible. For this reason, in the case of this example, a seal ring 49 locked in a locking groove 48 formed on the outer peripheral surface of the input side disk 2b is brought into sliding contact with the inner peripheral surface of the cylinder tube portion 47. .
[0025]
The pressure oil can be supplied and discharged freely in a cylinder space 50 surrounded by the input side disk 2b, the inner diameter side cylinder ring 31 and the outer diameter side cylinder rings 32. Therefore, in the case of this example, a part of the inner diameter side cylindrical portion 34 provided at the inner peripheral edge of the inner diameter side cylinder ring 31 is located between the pair of O-rings 39 and 39 and the inner diameter side. An oil passage hole 51 is formed to allow communication between the inner and outer peripheral surfaces of the cylinder ring 31. The oil passage hole 51 is communicated with a hydraulic source (not shown) through an oil passage 52 provided at the center of the input side rotating shaft 1a.
[0026]
The preload spring 33 is for pressing the outer diameter side cylinder ring 32 toward the input side disk 2b. For this purpose, the preload spring 33, which is a disc spring, is configured so that the outer peripheral side cylinder ring is supported by the engagement flange 37 formed on the outer peripheral surface of the inner diameter side cylinder ring 31. 32, the side opposite to the input side disk 2b is pressed.
[0027]
In the case of this example having the above-described configuration, the input-side disk 2b is the second disk when the pressing device 30 is in an inoperative state by changing the thickness dimension of the cotter 41 in the axial direction. The axial length ΔL that can be displaced in the direction away from the output side disk 19d is adjustable. Thus, the reason why the input side disk 2b can be displaced in the direction away from the output side disk 19d in the non-operating state of the pressing device 30 is as follows.
[0028]
If there is no manufacturing error or assembly error in each component of the toroidal-type continuously variable transmission, the trunnion 23 is oscillated and displaced about the pivots provided at both ends thereof in order to change the gear ratio. Even when the contact position between the peripheral surface 29 of the power roller 22 supported on the input side and the input side inner surface 3 of the input side disk 2b is changed, it is not necessary to displace the input side disk 2b in the axial direction. However, since it is almost impossible to make each of the errors completely zero, it is necessary to configure the input side disk 2b to be displaced in the axial direction in accordance with the change of the gear ratio. Therefore, when adopting the structure of this example, it is necessary to interpose the gap ΔL between the outer diameter side cylinder ring 32 and the locking collar portion 37 when the pressing device 30 is not in operation. There is.
[0029]
However, when the size ΔL of the gap becomes excessive, the outer diameter side cylinder ring with respect to the inner diameter side cylinder ring 31 in a state where the pressing force generated by the pressing device 30 exceeds the elasticity of the preload spring 33. The amount of displacement of 32 becomes excessive. Then, the seal ring 46 may be disengaged from the portion of the inner peripheral surface of the outer diameter side cylinder ring 32 where the seal ring 46 should be slidably contacted, and the sealability of the portion may be poor. Further, when the pressing force increases and the amount of elastic deformation of the input side disk 2b increases, the pressing device 30 moves the input side disk 2b to the output side disk in order to compensate for the elastic deformation. Displace toward 19d. In this case, if the ΔL is excessive, the seal ring 49 is disengaged from the portion of the inner peripheral surface of the cylinder cylinder 47 where the seal ring 49 should be slidably contacted, and the sealing performance of the portion is poor. There is a possibility. Increasing the axial length of the portion where the seal rings 46 and 49 should be brought into sliding contact with each other is difficult in terms of reducing the size and weight while preventing interference between the portions. Considering these matters, the value ΔL needs to be regulated with a high accuracy to a minute amount of 0.1 mm.
[0030]
Therefore, in the case of this example, the thickness T suitable for the cotter 41 is measured while measuring the dimensions of each part as described below.₄₁The size ΔL of the gap is regulated by selecting and using the one having the. In order to regulate this ΔL, first, a distance L from an appropriately selected reference plane (for example, the inner surface of the casing housing the toroidal-type continuously variable transmission) to the outer diameter side portion of the outer diameter side cylinder ring 32.₁ And the same distance L to the locking collar 37₂ And measure. In addition, the thickness T of the locking collar portion 37₃₇And a step L between the outer diameter side portion and the inner diameter side portion of the outer diameter side cylinder ring 32.₃₂Is measured in advance. The value of the gap ΔL is obtained from these measured values by the following equation.
ΔL = (L₁ -L₃₂)-(L₂ + T₃₇)
[0031]
Among the measured values, the distance L from the reference surface to the locking collar portion 37₂ Is the thickness T of the cotter 41₄₁It depends on. On the other hand, the distance L from the reference plane to the outer diameter side portion of the outer diameter side cylinder ring 32₁ Is the thickness T of the cotter 41₄₁It will not change even if you change slightly. The reason is that the outer diameter side cylinder ring 32 is elastically pressed by the preload spring 33. Therefore, the appropriate thickness T₄₁By selectively using the cotter 41 having the above, the value of the gap ΔL is regulated to an appropriate value.
[0032]
In the case of the toroidal type continuously variable transmission of this example configured as described above, the thrust for pressing the input side disk 2b toward the output side disk 19d by changing the hydraulic pressure introduced into the cylinder space 50. The load can be arbitrarily adjusted independently of the transmission torque. For this reason, the control which further improves the transmission efficiency and durability of a toroidal type continuously variable transmission is attained. In addition, since the preload spring 33 can be viewed from the outside after the assembly of the pressing device 30, the amount of compression of the preload spring 33 can be strictly regulated. Furthermore, the retraction amount of the input side disk 2b can be properly regulated.
[0033]
【The invention's effect】
Since the present invention is configured and operates as described above, the axial dimension of the portion related to the pressing device can be strictly regulated, and the transmission of the toroidal type continuously variable transmission incorporating this pressing device can be performed. Improve performance with a focus on efficiency and durability.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing an example of an embodiment of the present invention.
FIG. 2 is an enlarged view of a portion A in FIG.
FIG. 3 is a cross-sectional view of a portion where a phase in the circumferential direction is shifted by 90 degrees from FIG. 1, showing an example of a basic configuration of a conventionally known toroidal continuously variable transmission.
[Explanation of symbols]
1, 1a Rotating shaft on the input side
2a, 2b Input side disk
3 Input side inner surface
4 Ball spline
5 Male spline groove
6 Female spline groove
7 balls
8 Rolling bearing
9 Pressing device
10 Cam plate
11 Drive shaft
12 Loading nut
13 Disc spring
14 Bulkhead
15 through holes
16 sleeve
17 Rolling bearing
18 Output gear
19a, 19b, 19c, 19d Output side disk
20 Output side inner surface
21 Needle bearing
22 Power Roller
23 Trunnion
24 Displacement axis
25 radial needle bearings
26 Thrust ball bearing
27 Thrust Needle Bearing
28 Preload spring
29 circumference
30 Pressing device
31 Inner diameter side cylinder ring
32 Outer diameter side cylinder ring
33 Preload spring
34 Inner diameter side cylindrical part
35 torus
36 Outer diameter side cylindrical part
37 Locking collar
38 Locking groove
39 0 ring
40 Locking groove
41 cotters
42 Retaining ring
43 Retaining Ring
44 Screw hole
45 Locking groove
46 Seal Ring
47 Cylinder cylinder
48 Locking groove
49 Seal ring
50 cylinder space
51 Oil passage hole
52 Oil passage

Claims (2)

A rotating shaft, a first disk supported around the rotating shaft so as to freely displace the rotating shaft in the axial direction, and a rotation that is arranged concentrically with the first disk and independent of the first disk. And a plurality of support members which are provided between the first and second discs and swing about a pivot which is twisted with respect to the central axis of both discs. Each of the support members sandwiched between the inner surfaces of the two discs in a state of being rotatably supported by the displacement shafts, one for each of the support members. Each having a power roller, and a hydraulic pressing device that is provided between the rotating shaft and the first disk and presses the first disk toward the second disk by feeding pressure oil. Toroidal type continuously variable transmission In this pressing device comprises a fitted supported inner diameter side cylinder ring oil-tightly to the outer circumferential surface of the rotary shaft, an outer diameter which is stretched between the inner diameter side cylinder ring and the first disc A side cylinder ring and a preload spring for pressing the outer diameter side cylinder ring toward the first disk, and the inner diameter side cylinder ring is an inner diameter side cylinder that can be externally fitted to the rotating shaft. An annular part is formed from one end of the part continuously in the radially outward direction, and further, an outer diameter side cylindrical part is continued from the outer peripheral edge part of the annular part in a direction opposite to the inner diameter side cylindrical part. By forming it in a state, the whole is formed in an annular shape with a cross-sectional crank type, and the inner diameter side cylindrical portion is oil-tightly fitted to the rotating shaft, and the outer diameter side cylinder ring inner peripheral edge to the outer peripheral surface of the outer diameter side cylindrical portion of the inner diameter side cylinder ring, variable axial movement The cylinder cylinder part formed in a state of being bent to the side of the first disk on the outer peripheral edge of the outer diameter side cylinder ring is axially attached to the first disk. It is fitted in an oil-tight manner in a state where relative movement is possible, and pressure oil can be supplied and discharged freely in a cylinder space surrounded by the first disk and the inner and outer cylinder rings. preload spring is in a state in which the inner peripheral edge portion is supported on the outer peripheral surface of the outer diameter side cylindrical portion of the inner diameter side cylinder ring, and presses the opposite side with the first disk of the outer diameter side cylinder ring The inner diameter side cylinder ring is prevented from being displaced in a direction away from the first disk by a cotter locked in a locking groove formed on the outer peripheral surface of the rotating shaft. The inner edge of the retaining ring locked to the A toroidal continuously variable transmission characterized in that the inner peripheral edge of the cotter is prevented from slipping out of the locking groove by contacting or in close proximity to the outer peripheral edge of the rotor . Suppressing rings are fitted on the outer diameter side cylindrical portion of the inner diameter side cylinder ring, on a part of the restraining ring, screw holes through the restraining ring in the axial direction are formed, according to claim 1 Toroidal continuously variable transmission.

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