JP3458673B2 - Assembly method of toroidal type continuously variable transmission - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method of assembling a toroidal type continuously variable transmission used in a vehicle or the like, and more particularly to a double cavity type.

[0002]

2. Description of the Related Art A toroidal type transmission has been conventionally known as a continuously variable transmission used in a vehicle, in which a pair of input disks and toroidal curved surfaces formed on an output disk are arranged to face each other and are coaxially arranged. The power roller is sandwiched and pressed between the input disk and the output disk, which are arranged at, and the tilt angle of the power roller (hereinafter, tilt angle)
By changing continuously, the contact radius of the input roller and the output disk and the power roller continuously changes,
The driving force is transmitted from the input shaft to the output shaft (or the output gear) while continuously changing the gear ratio.

Such toroidal type continuously variable transmissions are disclosed in Japanese Unexamined Patent Publications Nos. 2-163562 and 4-78.
As disclosed in Japanese Unexamined Patent Publication No. 366, there is known a double-cavity toroidal-type continuously variable transmission including two sets of half toroidal-type transmissions.

This is because, as shown in FIG. 16, a torque converter 53 having a lock-up clutch on the input side of the toroidal type continuously variable transmission 50 and coupled to the engine.
And the forward / reverse switching device 5 on the output side of the torque converter 53.
4, the driving force from the forward / reverse switching device 54 is input to the first toroidal transmission unit 51 and the second toroidal transmission unit 52 via the input shaft 55 and the CVT shaft 25, respectively.

The first toroidal speed change unit 51 comprises a pair of power rollers 1L and 1R sandwiched between an input disk 20 and an output disk 21, and the second toroidal speed change unit 52 includes an input disk 20A and an output disk. 21A
It is composed of a pair of power rollers 1L, 1R sandwiched between and, and these power rollers 1L, 1R are respectively rotatably and rotatably supported by a trunnion (not shown). The tilting motion of the power rollers 1L, 1R is a rotary motion that changes the contact radius with the input / output disk. Then, each trunnion is penetrated in the plane of the drawing by an actuator (not shown) (axial direction of the trunnion).
And the power rollers 1L and 1R are tilted according to this displacement to change the gear ratio.

Here, for power transmission of the toroidal type continuously variable transmission 50, the power rollers 1L and 1R arranged between the input and output disks are sandwiched by a pressing force of several tons, and the power rollers 1L and 1R are connected to each other. This is performed by the shearing force of the oil film formed between the input / output disks 20 to 21A, and the power roller 1
L and 1R transmit power without slipping between the I / O disks 20 to 21A.

Therefore, the input discs 20 and 20A of the first and second toroidal speed change units 51 and 52 have the input shaft 55.
And at both ends of the CVT shaft 25 which engages in the rotational direction, the front ball spline 23, Riaborusupu
While being coupled in the rotational direction via the line 24, the line 24 is supported so as to be displaceable in a predetermined range in the axial direction (axial direction of the CVT shaft 25). On the other hand, the output discs 21 and 21A of the first and second toroidal speed change units 51 and 52 are relatively rotatably arranged in the middle of the CVT shaft 25, and the output discs 21 and 21A are arranged between the rear faces of the output gears. Two
6 and are coaxially coupled to each other, and are rotatably supported on the casing 10 side through angular ball bearings 59 and 159 provided between the output gear 26 and the output disks 21 and 21A, respectively. The disks 21, 21A and the CVT shaft 25 are relatively rotatable.

At both ends of the CVT shaft 25,
A cam roller 57 (pressing force generating means) for urging the axially displaceable input disks 20 and 20A in the axial direction and a disc spring 40 (preload generating means) are arranged. The urging force holds and presses the power rollers 1L and 1R between the input and output disks.

Here, the CVT shaft 25 and the input shaft 55
Are engaged in the rotational direction via the cam flange 56, the cam roller 57, and the input disk 20, and the flange 55A radially formed from the end of the input shaft 55 is circumferentially aligned with the claw portion 56a of the cam flange 56. While engaged, the cam flange 56 is supported so as to be rotatable relative to the CVT shaft 25.

This cam flange 56 is used for the input disk 2
A cam roller 57, which is rollable in the circumferential direction between the rear surface of 0 and 0, is supported by a shaft (not shown) protruding in the radial direction. Then, the rear surface of the input disk 20 or the cam flange 56.
At least one of them is formed with an inclined surface (not shown) for axially displacing the input disk 20 toward the output disk 21 as the relative rotation angle between the CVT shaft 25 and the cam flange 56 increases. 25
And the relative rotation angle of the cam flange 56, that is, the magnitude of the torque applied to the input shaft 55, the pressing force with which the input / output disks 20 to 21A hold the power rollers 1L and 1R is determined. The torque transmission capacity of the transmission 50 is determined by this pressing force.

At the other end of the CVT shaft 25 provided with the cam roller 57, there is provided a disc spring 40 which supports the pressing force generated by the cam roller 57 and gives a pressing force under no load (hereinafter referred to as preload). The disc spring 40 axially presses the back surface of the input disk 20A constituting the second toroidal speed change portion 52 with a predetermined urging force so that the input / output disk is the power roller 1L when no load is applied,
Holds 1R to enable power transmission. In addition, the disc spring 40 is C by a fastening means such as a lock nut 43.
It is fixed to the end of the VT shaft 25.

In this way, the driving force of the engine input to the CVT shaft 25 via the cam roller 57 and the input disk 20 produces a pressing force corresponding to the input torque.
7 and the input discs 20 and 20A provided at both ends of the CVT shaft 25 hold the power roller 1R1L and the output discs 21 and 21A with a uniform pressing force, depending on the tilt angles of the power rollers 1L and 1R. The power is transmitted from the input discs 20, 20A to the output discs 21, 21A at the gear ratio, and is output from the counter shaft 27 to the drive shaft via the gear 27a meshing with the output gear 26.

By the way, when assembling such a toroidal type continuously variable transmission 50, the first and second toroidal transmission parts 51 and 52 are mounted on the CVT shaft 25 from the cam flange 56.
Then, the disc spring 40 is sequentially assembled, and the disc spring 40 is fastened by a fastening means such as a lock nut 43 screwed to the CVT shaft 25 on the side of the disc spring 40.

In this way, after the first and second toroidal speed change parts 51, 52 are assembled inside the casing 10, the input shaft 55, the forward / reverse switching device 54, and the torque converter 53 are sequentially assembled.

[0015]

However, in the case of assembling and assembling the double-cavity toroidal type continuously variable transmission as described above, a pair of output disks 21, 21A is used.
Since it is connected to the output gear 26 between the rear surfaces of the power rollers 1L and 1R, the mounting positions of the output shafts 21 and 21A in the axial direction (axial direction of the CVT shaft 25) are as follows.
The components may be displaced due to stacking of dimensional tolerances of each component, etc. When such a displacement occurs, the pressing force applied to the first toroidal speed change unit 51 and the second toroidal speed change unit becomes non-uniform, and the power is reduced. On the other hand, there is a problem that the roller slips to reduce the torque transmission capacity, while the excessive pressing force reduces the durability of the rolling surfaces of the power roller and the input / output disk. Since many components are assembled, there is a problem that the axial positions of the power rollers 1L, 1R and the output disks 21, 21A cannot be easily adjusted.

The present invention has been made in view of the above problems, and an object thereof is to easily and accurately position the power roller and the output disk in the axial direction for assembly.

[0017]

According to a first aspect of the present invention, there are provided a first toroidal transmission unit and a second toroidal transmission unit which are coaxially arranged on an input shaft and each include a pair of an input disc and an output disc, and A trunnion that is arranged to face each other with the input shaft sandwiched therebetween and that rotatably and tiltably supports a power roller that is sandwiched between the input and output disks; and a trunnion that is disposed on the input shaft to sandwich and press the power roller. Assembly of a toroidal type continuously variable transmission including a pressing force generating means for generating a force and a transmission means connected between the output disks of the first and second toroidal speed change parts to transmit power to the drive shaft side. In the method, the output discs of the first and second toroidal speed change units are assembled in advance by using the transmission means as a reference in the input shaft direction, and at a predetermined reference position of the transmission means.
To the end faces of the output discs of the first and second toroidal transmissions.
Subassembly step including an adjusting step for adjusting the distance at a predetermined value to a predetermined value, a step of assembling the transmission means in which the output disk is previously attached to the casing, and a step of assembling the pressing force generating means and the input disk to the input shaft and then the transmission means after insertion into, saw including a step of assembling the trunnion and a power roller, the transmission means, the pair of output disks
A gear or sprocket connected between
Alternatively, the sprocket is housed and the casing is used.
Housing and the gear or sprocket
Mounted on both sides in the axial direction of the
The pair of bearings to be held and the predetermined reference position of the housing
Axial distance from each output disk to the end surface and bearing
Axial positioning means for adjusting the preload
The bearing has an outer ring coupled to the housing and an inner ring.
The wheel is connected to the cylinder of the gear fitted with the output disc,
The axial positioning means is interposed between the outer ring and the housing.
The adjusting step is performed by the output disc and the gear or the spun.
Depending on the axial dimension of the rocket, the axial positioning means
Adjust the axial dimension and adjust the axial distance and preload at the same time.
To adjust.

[0018]

[0019]

[0020]

Further, the second invention, said contact <br/> are in the first invention, the predetermined reference position of said housing is a surface housing is assembled to the casing.

[0022]

[0023]

[0024]

Therefore, the first invention is to assemble a double-cavity toroidal-type continuously variable transmission including two sets of an input disk and an output disk coaxially arranged on an input shaft, and In the sub-assembly process, the transmission means is used as a reference in the direction of the input shaft, and the output disks of the first and second toroidal speed change units are assembled to the transmission means, and then the transmission means is assembled to the casing. And
After inserting the pressing force generating means and the input disk into the transmission means and the output disk, the trunnion and the power roller are assembled to the casing, so that the output disk of the transmission means assembled to the casing and the power roller of the trunnion assembled to the casing. The axial position of the is constantly positioned with high precision, and the holding pressure applied by the pressing force generation means is evenly applied to the first and second toroidal speed change parts to prevent the power roller from slipping and ensure quality. However, by assembling the output discs of the first and second toroidal speed changers to the transmission means in the sub-assembly process, it is not necessary to perform adjustment work on the inner circumference of the casing, so that the assembly work can be performed efficiently. Productivity can be improved , and the axial direction interposed between the housing and the bearing outer ring
By the directional positioning means,
Axial positioning adjustment and adjustment of the preload applied to the bearing.
Can be performed simultaneously and easily, reducing the number of parts and
To improve productivity by reducing the number of adjustment points.
You can

Further, in the sub-assembling step, if the axial distance from the predetermined reference position of the transmission means to the end faces of the output disks of the first and second toroidal speed change parts is adjusted to a predetermined value, the transmission means is casing. Just attach it to
The power roller and the output disc can be positioned with high accuracy, and the assembling work can be efficiently performed to improve the productivity.

[0026]

In addition, a pair of bearings arranged on both sides of the gear or sprocket of the transmission means in the axial direction and supported by the housing, and an axial distance from a predetermined reference position of the housing to the end surface of each output disk. By simultaneously adjusting the preload to the bearing and the bearing by the axial positioning means according to the axial dimensions of the output disk and the gear or sprocket, the positioning and bearing of the output disk and the bearing can be easily and accurately performed with respect to the reference position of the transmission means. It becomes possible to set the preload to the same time.

Further, in the second invention, since the reference position of the housing is the surface of the housing assembled to the casing, the axial dimension of the output disk and the gear or sprocket can be measured easily and accurately, and Adjusting the axial position of the output disc based on the mounting surface to the casing and then assembling the transmission means to the casing will always set the axial position of the trunnion and other components to be mounted on the casing and the axial position of the output disc. can do.

[0029]

[0030]

[0031]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Reference examples of the present invention will be described below with reference to the accompanying drawings.

1 to 12 are similar to those of the conventional example, and
An example in which the present invention is applied to the assembly of a double-cavity toroidal type continuously variable transmission 50 composed of a set of input / output disks 20, 21 and 20A, 21A is shown. Will be attached and redundant description will be omitted.

FIGS. 1 and 2 show a state in which a first toroidal speed change portion 51 including an input disk 20 and an output disk 21 and a second toroidal speed change portion 52 including an input disk 20A and an output disk 21A are assembled in a casing 10. 16, the counter shaft 27 and the input shaft 55 shown in FIG. 16 of the conventional example are not mounted, and in FIG. 1, the input shaft 55 and the rotation direction are different from each other on the left end 25F side of the CVT shaft 25 in FIG. On the other hand, the end portion 25R on the right side in the drawing is the drive shaft side. Here, the end 25F side is the front end and the end 25R side is the rear end.

1 and 2, the first toroidal speed change portion 51 includes a pair of power rollers 1L and 1R sandwiched between a pair of input disks 20 and output disks 21 each having a toroidal groove formed on the opposite surface. Input / output disks 20, 21
The axis of the CVT shaft 25 (input shaft) = rotating shaft C ₀ is rotatably supported by the pair of trunnions 3L and 3R, which are supported by pivot shafts 2 and 2 whose base ends are supported.

The second toroidal transmission unit 52 is also constructed in the same manner as described above, and the input disc 20A and the output disc 2 are arranged.
The pair of power rollers 1L and 1R sandwiched by 1A is C
It is rotatably supported by the pivot shaft 2 whose base ends are supported by a pair of trunnions 3L and 3R arranged with the VT shaft 25 interposed therebetween.

The input discs 20 and 20A and the output discs 21 and 21A are arranged coaxially with the CVT shaft 25, and the input discs 20 and 20A are arranged on the CVT shaft 25.
And the output discs 21 and 21A, while being coupled in the rotational direction with
Penetrates the CVT shaft 25 to the inner circumference and
It is rotatably supported relative to the T-shaft 25.

The output disc 21 of the first toroidal speed change unit 51 and the output disc 21A of the second toroidal speed change unit 52 have cylindrical portions 26A, 26A protruding axially from both sides of an output gear 26 provided in the middle of both. Are fitted to the outer periphery of each and are integrally coupled.

A gear 27 that meshes with the output gear 26
The counter shaft 27 shown in FIG.
Is inserted, and power is transmitted to the drive shaft at a gear ratio according to the tilt angles of the power rollers 1L, 1R. The gear 27a is axially supported by the rear gear housing 28B via a radial bearing 75.

In this reference example , the counter shaft 2
7 is disposed below the second toroidal transmission unit 52, and includes a front gear housing 28A and a rear gear housing 28B.
The counter shaft 27 accommodated therein has a structure in which the counter shaft 27 can be attached and detached via a spline or the like. The output gear 26, the gear 27a and the output discs 21 and 21A serve as transmission means as will be described later. The gear housing assembly (ASSY) 28 is preassembled.

Next, referring to FIG. 2, the first toroidal speed change portion 51 has a rotation axis C ₀ (C
The trunnions 3L and 3R are disposed on the left and right sides of the rotation axis C ₀ in a plane orthogonal to the axis of the VT shaft 25. The trunnions 3L and 3R are coaxial with the rotation axis 3z at the upper and lower ends thereof. While forming the rotary shafts 3a and 3b, the input / output disk 20 is provided between the rotary shafts 3a and 3b.
Offset portions 3c offset by a predetermined amount in the outer peripheral direction of 21 are formed respectively, and the pivot shaft 2 is supported at the base end side by the offset portions 3c so as to be orthogonal to the rotation axis of the trunnion 3. The second toroidal transmission unit 52
Similarly, the power rollers 1L and 1R sandwiched between the input / output disks 20A and 21A are provided with pivot shafts 2 and 2 provided on the trunnions 3L and 3R, which are opposed to each other.
Supported by. Although not shown, the trunnion 3L of the first toroidal speed changer 51 has a feedback means (not shown) attached to the lower end of the rod 6b. The amount of protrusion to the side) is set to a large value.

The rotating shaft portion 3b on the lower end side of the trunnion 3 is connected to the piston 6a via a rod 6b of a hydraulic cylinder 6 (actuator) which is displaceable in the axial direction of the rotating shaft 3z and rotatable about its axis. The trunnions 3L, 3R are displaced in the vertical direction in the drawing in the direction of the rotating shaft 3z in accordance with the hydraulic pressure supplied to the hydraulic cylinder 6, and the power rollers 1L, 3L, 3R are displaced along with the axial displacement of the trunnions 3L, 3R. Since the 1R is tilted, the trunnion 3 moves to the rotary shaft 3
Rotate around z. The hydraulic cylinder 6 is formed inside the cylinder body 60 and the cylinder body bottom 61 (actuator body) that are connected to the casing 10.

In the trunnion assembly sub-assembly step S103 shown in FIG. 8, the trunnions 3L and 3R connect the rod 6b to the rotary shaft portion 3b at the lower ends of the trunnions 3L and 3R, and the pivot shaft 2 as shown in FIG. Attach to the offset portion 3c. Furthermore, the pivot shaft 2
After inserting the ball bearing 16 and the outer ring 18 that support the thrust force, and the needle bearing 19 for positioning in the radial direction, the power roller 1
Assembling L and 1R respectively, trunnion sub-ASSY3
Assembled in advance as LA and 3RA, and in the transmission section assembling step S100 of FIG.
Assemble the Hetlanion Sub-ASSY 3LA, 3RA. In addition, trunnion sub-ASSY3LA is trunnion 3
The L is assembled, and the trunnion sub-ASSY3RA is
It is an assembly of the trunnion 3R.

On the other hand, the upper and lower rotary shafts 3a and 3b of the opposing trunnions 3L and 3R have upper links 4 which are swingable in a plane orthogonal to the rotary axes C ₀ of the input / output disks 20 and 21. The upper link 4 and the lower link 5 are connected to each other via a lower link 5, and the upper link 4 and the lower link 5 are attached to the pivot shafts 2 and 2.
Supports thrust force (pressing force) from L and 1R.

Here, the upper link 4 and the lower link 5
Through holes 4L, 4R and 5L, 5R are formed on both ends in the longitudinal direction at both ends and in the center.
While the trunnions 3L and 3R are respectively inserted into the rotary shafts 3a and 3b, the central through holes 4C and 5C are directed from the casing 10 and the cylinder body 60 side toward the rotary shaft C ₀ of the input / output disks 20 and 21, They are swingably supported by an upper link support member 12 and a lower link support member 30, which are provided to project in the vertical direction in the figure.

The left and right hydraulic cylinders 6, 6 are the trunnion 3
When L and 3R are synchronously driven in the opposite axial directions, the upper link 4 and the lower link 5 become trunnions 3L and 3R.
According to the axial displacement of the upper link support member 12,
The lower link support member 30 swings around the pins 14 and 31 of the lower link support member 30 as a fulcrum mainly in a plane orthogonal to the rotation axis C ₀ of the input / output disks 20 and 21.

Therefore, between the rotating shaft portions 3a and 3b of the trunnions 3L and 3R and the through holes 4L, 4R and 5L and 5R at both ends of the upper link 4 and the lower link 5,
A spherical bearing 7 and a needle bearing 8 are respectively provided to allow the inclination of the upper link 4 and the lower link 5 with respect to the trunnion 3, while the upper link 4 and the lower link 5 regulate the radial displacement of the trunnions 3L, 3R. Thus, the rotation forces 3z, 3z of the trunnion 3 are prevented from being displaced by the thrust force applied to the power rollers 1L, 1R.

A needle bearing 8 is engaged with the outer circumferences of the rotating shafts 3a, 3b of the trunnion 3, and an inner circumference of the spherical bearing 7 is engaged with the outer circumference of the needle bearing 8.
The spherical surface formed on the outer periphery of the spherical bearing 7 is formed in each through hole 4
Engages with the inner perimeter of L, 4R and 5L, 5R.

Here, the upper link support member 12, which supports the upper link 4 so as to freely swing, has a bolt 1 at one end.
It is formed of a tubular member having a through hole for inserting the through hole 5, and as shown in FIG. 2, a pair of through holes 12a for supporting the upper link 4 swingably. The pins 14 and 14 are fitted with each other, and these pins 14 are arranged parallel to the rotation axis C ₀ of the input / output disks 20 and 21, and are connected to the upper link 4 by the tips protruding from the upper link support member 12. Support swingably.

The upper link support member 12 has a bolt 1 inserted in a through hole opened at the bottom (downward in the figure).
It is fastened to the positioning member 11 via 5.

The positioning member 11 is attached to the upper surface of the inner peripheral surface of the casing 10. The positioning member 11 is engaged with a knock pin 9 fixed in advance on the casing 10 on the upper surface contacting the inner peripheral surface of the casing 10. It is positioned so as not to shift from a predetermined position. The positioning member 11 is a bolt 1 that is fastened to the casing 10 from the rotation axis C ₀ side.
It is connected to the casing by 7, 17.

On the other hand, the positioning member 11 on the rotating shaft C ₀ side has the convex portion 1 fitted to the inner circumference of the upper link supporting member 12.
1a is formed, a screw hole for screwing with the bolt 15 is formed in the convex portion 11a, and the upper link support member 12 is fixed to a predetermined position on the inner circumference of the casing 10 via the positioning member 11.

On the other hand, the lower link support member 30 for swingably supporting the lower link 5 is fixed to the cylinder body 60 which faces the upper link support member 12 with the rotary shaft C ₀ of the input / output disk interposed therebetween. The pedestal 60A is projected upward.

A recess 60C having a U-shaped cross section is provided on the upper surface of the pedestal 60A so as to accommodate the lower link support member 30, and the size of the recess 60C in the horizontal direction (X-axis direction in the drawing) is lower link. The support member 30 is set to a value that allows displacement in a predetermined range in the X-axis direction of FIG.
A predetermined gap corresponding to the amount of displacement is formed between the side surface of 0 and the inner periphery of the recess 60C.

As shown in FIG. 1, the lower link support member 30 for swingably supporting the lower link 5 has pins 31, 31 projectingly provided in parallel with the rotation axes C ₀ of the input / output disks 20, 21. Similarly to the upper link 4 side, the lower link 5 is connected to the central through hole 5C through a through hole that fits with these pins 31, 31 so that the lower link 5 can be swung by the pin 31. To support.

Here, from the lower surface of the lower link support member 30 of the lower link 5, stud bolts 33, 33 are provided so as to project in the vertical direction (Z-axis direction) in the drawing, and these stud bolts 33, 3 are mounted on the pedestal 60A. Also, the lower link support member 30 is seated by inserting the nut 33a into the through hole 60D provided in the cylinder body bottom 61 and screwing the nut 33a into the lower end of the cylinder body 60 or the lower end of the cylinder body bottom 61. Fasten to 60A.

The inner diameter of the through hole 60D is set to be larger than the outer diameter of the stud bolt 33, so that the position adjustment of the lower link support member 30, which will be described later, in the X-axis direction in the drawing becomes possible.

Then, the lower link support member 30 and the pedestal 6
The positioning of 0A is performed by the knock pin 32 protruding from the lower surface of the lower link support member 30 and the locate hole 60B provided in the pedestal 60A. Locate hole 60B is shown in Figure 1.
As shown in, the rotation axis C ₀ for the rotation axis C ₀ direction lower link support member 30 engaged with (Y-axis direction) in the knock pin 32
While positioning in the direction, as shown in FIG. 2, displacement of the knock pin 5 is allowed within a predetermined range in the longitudinal direction of the lower link 5 (X-axis direction in the figure). Therefore, the nut 33a
During the assembly of the toroidal type continuously variable transmission in which the nuts are fastened, the position of the lower link support member 30 in the X-axis direction is the nut 33.
It is set at an arbitrary position where a is fastened.

The lower link support member 30 for supporting the lower link 5 of the second toroidal speed change portion 52 is also the first link.
The configuration is similar to that of the toroidal transmission unit 51.

Further, as shown in FIG. 1, the cylinder body 60 and the cylinder body bottom 61 are provided with a knock pin 62.
After being positioned at a predetermined position by, the bolt 10 is fastened to the casing 10.

Further, in order to synchronize the tilt angles of the trunnions 3L and 3R which face each other, pulley grooves 37 and 37 are formed below the offset portion 3c, and these pulley grooves 37 and 37 have an 8-shaped shape. Wire 36 wrapped around
The trunnions 3L, 3 that rotate in opposite directions
Synchronization of tilting of R is performed.

Further, the pulley 35 is also fitted to the rotary shaft portions 3b of the trunnions 3L and 3R.
To adjacent trunnions 3L, 3L or 3
The wire 36 is wound in a figure 8 shape in order to synchronize the tilting of R and 3R.

Next, in the CVT shaft 25, in the CVT shaft ASSY sub-assembly step S101 shown in FIG. 8, as shown in FIG. 7, the cam flange 56 is attached to the end 25F side via the ball bearing 58, and the cam flange 56 is assembled. The flange 56 is rotatably supported with respect to the CVT shaft 25, and the cam rollers 57 (pressing force generating means) are attached to the plurality of shafts 56b formed on the cam flange 56 and protruding in the radial direction. The toroidal transmission unit 51 is supported between the rear surface of the input disk 20 and the side surface of the cam flange 56 so as to be rotatable and regulate the displacement in the outer peripheral direction. Then, the input disk 20 and the CVT shaft 25
Is the front ball spline 2 provided on the end 25F side.
Insert the ball into 3 and join them in the direction of rotation.

Here, in the CVT shaft ASSY sub-assembly step S101, the relative rotation of the cam flange 56 and the input disk 20 of the first toroidal speed changer 51 is restricted. After fixing the back surface and cam flange 56, C
As the VT shaft ASSY 25A, it is sent to the transmission section assembling step S100 in FIG.

The position where the cam flange 56 is fixed to the CVT shaft 25 is the position where the input disk 20 is closest to the cam flange 56, that is, the cam roller 57.
Is set to the no-load position where the pressing force that causes

On the other hand, on the rear end 25R of the CVT shaft 25, as shown in FIG. 1, the rear surface of the input disk 20A constituting the second toroidal speed change portion 52 is axially (forwardly) pressed by a predetermined biasing force. Then, ring-shaped disc springs 40 and 41 that provide a preload for holding the power rollers 1L and 1R by the input / output disk are provided.

The disc springs 40 and 41 are mounted between the inner circumference of the CVT shaft 25 and the CVT shaft 25 through a cylindrical shim 42. As shown in FIG. 7, the CVT shaft 25 is mounted from the rear end 25R side. Lock nut 43 screwed to the screw portion 25c
Fastens the shim 42 to the position where it abuts the step 25b,
The disc springs 40, 41 are configured to provide a predetermined preload.

Here, the CVT shaft 25 on the rear end portion 25R side is formed with a rear ball spline 24 for coupling the input disk 20A only in the rotational direction, and the rear ball spline 24 is stepped from the end portion on the end portion 25R side. Part 25b
The outer diameter is reduced through the step 25b to the end 25R.
A screw portion 25c is formed toward the. The screw part 25
The outer diameter of the end portion 25R from the end of c is further reduced.

Rear ball spline 2 from the end 25R side
After assembling the ball No. 4 and the input disk 20A, a shim 42 having a predetermined length L in the axial direction is inserted into the outer periphery of the screw portion 25c, and the end portion of the shim 42 is formed on the CVT shaft 25 by a step 25b. Abut this shim 4
The ring-shaped disc springs 40 and 41 are inserted through the outer periphery of 2.

In this state, the lock nut 43 screwed into the screw portion 25c is fastened to the shim 42 between the stepped portion 25b and the lock nut 43.
And the disc springs 40 and 41 are compressed to urge the input disk 20A toward the other end.

Next, the driving force transmitted to the output discs 21 and 21A is transmitted through the output gear 26 and the gear 27a as shown in FIG.
The gear housing ASSY 28 as a transmission means for transmitting to the counter shaft 27 will be described.

As shown in FIG. 3, the output disc 21 and the output disc 21A are connected to the front gear housing 28A and the rear gear housing 28 via angular ball bearings 59 and 159 provided between the rear surfaces of both the output disc 21 and the output gear 26.
The output discs 21 and 21A and the output gear 26 are provided on the casing 10 side by being supported by B and rotatably supported, and the front gear housing 28A being fastened to the bracket 10A formed on the casing 10 via the bolt 28C. It is rotatably supported by.

Here, the angular ball bearing 5 provided between the rear surfaces of the output disks 21 and 21A and the output gear 26.
Reference numerals 9 and 159 serve to position the output disks 21 and 21A in the radial direction and to support a thrust force corresponding to the pressing force applied to the output disks 21 and 21A via the power roller 1L1R. And the output gear 26, the angular ball bearing 59 is provided between the output disk 21 of the second toroidal transmission unit 52.
While supporting the thrust force applied to A, the output disk 2
An angular ball bearing 159 provided between the rear surface of 1A and the output gear 26 supports the thrust force applied to the output disc 21 of the first toroidal transmission unit 51.

A cylindrical portion 26A is formed on each side of the output gear 26 in the axial direction (C ₀ ) of the CVT shaft 25, and the CVT shaft 15 is rotatably inserted through the inner periphery of the cylindrical portion 26A. Splines 26B and 26B are respectively formed from both ends on the outer circumference of the cylindrical portion 26A, and the output disks 21 and 21A are fitted on the inner circumference.

Then, the output disk 21 and the output gear 26
A positioning adjustment shim 72 and an inner ring 59a of an angular ball bearing 59 are interposed between the side faces of the inner ring 59a.
Both end surfaces in the axial direction of the positioning gears 72 and the output gear 2
As shown in FIG. 4, the distance from the side surface of the output gear 26 to the end surface of the output disk 21 can be set according to the thickness S ₁ of the positioning adjustment shim 72.

On the other hand, the outer ring 59b of the angular ball bearing 59 arranged on the output disk 21 side has the output gear 2
6. A flange 59c is provided so as to extend along the side surface of 6, and an axial end surface formed on the flange 59c and facing the output disk 21 side and a surface on the side surface side of the output gear 26 formed on the front gear housing 28A. The preload adjusting shim 70 is interposed between the preload adjusting shim 70 and the end face, and the angular ball bearing 5 according to the thickness S ₃ of the preload adjusting shim 70 as shown in FIG.
The preload applied to 9 (preload of bearing) can be adjusted.

Similarly, the output disk 21 and the output gear 26
A positioning adjustment shim 73 and an inner ring 159a of an angular ball bearing 159 are interposed between the side faces of the inner ring 1
59a both end faces in the axial direction abuts the side surface of the positioning adjustment shim 73 and the output gear 26, shown in Figure 4, in accordance with the positioning adjustment shim 73 thickness S _2, the output disc 21A from the side of the output gear 26 You can set the distance to the end face of. Further, a flange 159c is provided on the outer ring 159b of the angular ball bearing 159 so as to extend along the side surface of the output gear 26, and the axial end face formed on the flange 159c and facing the output disc 21A side and the rear gear housing 28B. A preload adjusting shim 71 is interposed between the end face of the output gear 26 facing the side surface,
As shown in FIG. 4, the preload applied to the angular ball bearing 159 can be adjusted according to the thickness S ₄ of the preload adjusting shim 71.

The end faces of the output discs 21 and 21A project from the end of the tubular portion 26A, and snap rings 82 and 83 are provided on the inner circumferences of the projecting output discs 21 and 21A.
Needle bearings 80 and 81 are arranged between the outer periphery of the CVT shaft 25 and the gear housing assembly 2.
8 and the CVT shaft 25 smoothly rotate relative to each other.

The gear housing ASSY 28 is preassembled in the gear housing ASSY sub-assembling step S102 shown in FIG. 9 and then sent to the gear shifting section assembling step S100. As shown in FIG. After the front gear housing 28A and the rear gear housing 28B are coupled to each other and preassembled as the gear housing ASSY 28 accommodating the output gear 26 and the gear 27a, FIG.
In the transmission section assembling step S100, the casing 10 is assembled as described later.

In the gear housing ASSY sub-assembling step S102 for assembling the gear housing ASSY 28, the front gear housing 28A is assembled on the basis of the end surface 28E joined to the rear gear housing 28B in FIG. 3, and the output disks 21, 21A are assembled from the end surface 28E.
The inner rings 59a, 159a of the angular ball bearings 59, 159 so that the distances L1, L2 to the end faces of the
And the annular positioning adjustment shims 72 and 73 provided between the rear surfaces of the output disks 21 and 21A and the outer rings 59b and 159b of the angular ball bearings 59 and 159.
Angular ball bearing 59 by previously adjusted projected flanges 59c, 159c and the front gear housing 28A, an annular preload adjusting shims 70 and 71 interposed between the axial end faces of the rear gear housing 28B from,
The preload applied to 159 is adjusted in advance. The outer rings 59b and 159b are flanges 59c and 159c.
It abuts only on the end faces of the front gear housing 28A and the rear gear housing 28B via, and forms a gap with the side face of the output gear 26.

Then, in the gear shifting section assembling step S100, as shown in FIG. 5, the gear housing ASSY 28 assembled in advance so that L1 = L2, the end surface 28E of the front gear housing 28A, and the casing 10 of the casing 10 are shown in the upper part of the drawing. After abutting against the end surface of the bracket 10A protruding on the inner circumference, the through hole 28 provided in the front gear housing 28A
The gear housing ASSY 28 is assembled to the casing 10 by fastening the bolt 28C inserted through D to the bracket 10A.

Here, in the casing 10, the axial distance between the end surface of the bracket 10A to which the gear housing ASSY 28 is attached and the trunnions 3L and 3R of the first toroidal speed changer 51 is set to a predetermined value L3 in advance. Similarly, the end surface of the bracket 10A and the rotating shaft 3 of the trunnions 3L and 3R of the second toroidal transmission unit 52 are processed.
It is processed in advance so that the axial distance to z is L4 and L3 = L4.

Then, with reference to the end face 28E, L1 = L
Gear housing assembly pre-assembled to 2
By connecting 28 to the bracket 10A, the positional relationship between the output disks 21 and 21A and the trunnions 3L and 3R in the axial direction, that is, the positional relationship between the output rollers 21 and 21A and the axis of the power rollers 1L and 1R is L3-L1 = L4-L2. You can
The intervals between the input and output disks of the first and second toroidal speed change parts 51 and 52 become equal, and the pressing force applied in the axial direction is evenly distributed, so that the first and second toroidal speed change parts 51 and 5 are formed.
The two torque transmission capacities can be set equal.

Here, when the axial distances L1 and L2 from the center line of the output gear 26 to the output disks 21 and 22A are not equal, as shown by the broken line in FIG. The preload applied by the device deviates from a predetermined range, imbalance occurs in the pressing force applied to the first and second toroidal transmission units 51 and 52, and slippage occurs in the power rollers 1L and 1R, resulting in a toroidal-type continuously variable transmission. Although the torque transmission capacity and durability of 50 will be reduced, as will be described later, the positioning adjustment shim 7
2, 73 and the preload adjusting shims 70, 71 in the gear housing ASSY sub-assembly step S102 of FIG.
By previously adjusting L1 = L2 with reference to, and assembling into the casing 10, as shown by the solid line in FIG. 13, the pressing force or preload by the cam roller 57 or the disc springs 40 and 41 is adjusted to the first and second toroidal shapes. The power rollers 1L, 1R are evenly distributed to the speed change units 51, 52.
Therefore, the performance and quality of the toroidal-type continuously variable transmission 50 can be maintained constant at all times by preventing the slippage of the toroidal type.

The overall procedure for assembling the toroidal type continuously variable transmission 50 having the above-described structure will be described with reference to the block diagram of FIG.

First, the CVT shaft assembly subassembly process S
101, as shown in FIG. 7 above, the cam flange 5
6, the cam roller 57 and the input disk 20 of the first toroidal speed changer 51 are assembled, and the cam flange 56 is fixed to the input disk 20 at a position where the cam roller 57 is in an unloaded state via a bolt or the like, and the CVT shaft
Assemble as ASSY25A.

In the trunnion ASSY sub-assembling step S103, as shown in FIG. 8, the rod 6b is coupled to the rotary shaft portions 3b at the lower ends of the trunnions 3L and 3R, the pivot shaft 2 is assembled to the offset portion 3c, and the pivot shaft 3c is further attached. 2 ball bearing 16 and outer ring 18
After inserting the needle bearing 19 with the power roller 1L and 1R, the trunnion sub-ASSY3
Assemble in advance as LA and 3RA.

Then, in the gear housing assembly subassembly step S102, as shown in FIG. 3, after the angular ball bearings 59, 159 are assembled to the output gear 26, the front gear housing 28A and the rear gear housing 28B are assembled.
The output gear 26 and the gear 27a are assembled on the inner periphery of the front gear housing 28A and the rear gear based on the end face E while the preload adjusting shims 70 and 71 are attached to the outer ring flanges 59c and 159c. The housing 28B is coupled. Furthermore, the positioning adjustment shims 72, 7 are provided on both ends of the tubular portion 26A of the output gear 26.
The output discs 21 and 21A are coupled to each other via 3 and assembled as a gear housing ASSY 28.

In the gear housing ASSY sub-assembly step S102, the positioning adjustment shims 72, 73 and the preload adjustment shims 70, 71 are selected as will be described later, and as shown in FIGS. Axial distance L from the end surface E of 28A to the output disks 21, 21A
Adjust so that 1 and L2 are equal.

Next, in the gear shifting assembly step S100, the gear housing ASSY 28 is fastened to the bracket 10A projecting from the inner periphery of the casing 10, and then the preassembled CVT shaft ASSY 25A is inserted into the inner periphery of the tubular portion 26A. In addition, the input disk 2 of the second toroidal transmission unit 52
Assemble 0A. And four trunnion sub-ASSY
When 3LA and 3RA are assembled to the casing 10 together with other components, and then the disc springs 40 and 41 are assembled to the rear end 25R of the CVT shaft 25 by the lock nut 43, the disc springs 40 and 41 will not be included in the gear shift portion adjusting step S110. The preload is adjusted by selecting the shim 42 having a length corresponding to the dimensional tolerance of each component so that the circumferential clearance is within a predetermined range.

After assembling the first and second toroidal speed change parts 51 and 52 mainly composed of the CVT shaft 25 inside the casing 10 with reference to the gear housing ASSY 28, in the torque converter and forward / reverse switching device assembling step S120. Similarly to the conventional example, the input shaft 55, the forward / reverse switching device 54, and the torque converter 53, which engage with the CVT shaft 25 in the rotational direction, are sequentially assembled from the front of the casing 10 to complete the assembly process, and the completion inspection process S1.
It is sent to 30.

Here, an example of the procedure for assembling each part and adjusting each axial dimension performed in the gear housing ASSY sub-assembly step S102 of FIG. 8 will be described in detail below with reference to the flowchart of FIG. 9 and FIG. To do.

First, in step S20 of FIG. 9, the gear 27a of the counter shaft is added to the rear gear housing 28B.
The radial bearing 75 for supporting the is assembled.

In step S21, the pair of angular ball bearings 59, 159 are attached to the tubular portion 26A of the output gear 26 with the flanges 59c, 159c facing the side surfaces of the output gear 26.

Next, in step S22, as shown in FIG. 4, the axial distance A1 from the end surface 28E of the front gear housing 28A to the end surface of the front gear housing 28A that contacts the preload adjusting shim 70 is measured.

Similarly, in step S23, the preload adjusting shim 71 is moved from the end surface 28F of the rear gear housing 28B joined to the end surface 28E of the front gear housing 28A.
The axial distance A2 to the end surface of the rear gear housing 28B that comes into contact with is measured.

In step S24, the axial dimension B between the end faces of the flanges 59c and 159c projecting from the angular ball bearings 59 and 159 assembled to the output gear 26 is measured.

Then, in step S25, the distances A1, A2 from the joint end faces 28E, 28F of the front and rear housings 28A, 28B obtained in steps S22, S23 to the end faces abutting the preload adjusting shims 70, 71.
And the preload adjustment shim obtained in step S24 is 7
From the axial dimension B of the end faces of the flanges 59c, 159c that abut the 0, 71, the preload adjusting shim 7
The thicknesses S ₃ and S ₄ of 0 and 71 are calculated and selected.

S ₃ = S ₄ = (A1 + A2-B + K) / 2 (1) where K is the interference and is a preset design value.

Thus, by selecting the preload adjusting shims 70 and 71 having the thicknesses S ₃ and S ₄ obtained by the above equation (1),
The preload of the angular ball bearings 59, 159 can be set to a predetermined value by absorbing the error due to the stacking of the dimensional tolerances of the respective parts. In step S26, the selected preload adjusting shims 70, 71 are attached to the end faces of the flanges 59c, 159c. Attach to.

Then, in step S27, the output gear 26 in which the angular ball bearings 59, 159 and the preload adjusting shims 70, 71 are attached is attached to the rear gear housing 28B, and the counter shaft gear 27a is attached.
Is assembled to the radial bearing 75 of the rear gear housing 28B.

In step S28, the end surface 28E of the front gear housing 28A and the rear gear housing 28B are connected.
End face 28F of the bolt 7 inserted into the rear gear housing 28B through a screw hole formed in the upper portion of the front gear housing 28A as shown in FIG.
4, the front gear housing 28A and the rear gear housing 28B are integrally connected to house the output gear 26 and the gear 27a inside.

In step S29, it is confirmed whether the preload of the angular ball bearings 59, 159 of the output gear 26 accommodated is appropriate. That is, it is confirmed whether or not the output gear 26 has looseness in the axial direction, and whether or not the output gear 26 smoothly rotates. If the preload is appropriate, the process proceeds to step S30. Step S
Return to 22.

Next, in step S30, as shown in FIG. 4, the end face 28 of the front gear housing 28A protruding from the upper part of the gear housing ASSY 28 integrally connected in the drawing is shown.
The axial distance C1 from E to the end surface of the inner ring 59a of the angular ball bearing 59, and the angular ball bearing 59,
The axial distance C between the end faces of the inner rings 59a, 159a of 159
Measure 2.

Further, in step S31, the axial distances D1 and D2 between the end surfaces and the back surfaces of the output disks 21 and 21A are measured, respectively.

Then, in step S32, the inner ring 5 is
9a, the axial distance C1, C2 of 159a, the axial distance D1, D2 of the output disks 21, 21A, the thickness S ₁ of the positioning adjustment shim 72 by the following equation, the thickness S ₂ of the positioning adjustment shims 73 Each is calculated and selected.

S ₁ = L1-D1-C1 (2) S ₂ = L2- (C2-C1) -D2 (3) Note that L1 and L2 are preset design values.

In this way, after the positioning adjustment shims 72 and 73 having the thicknesses S ₁ and S ₂ selected by the equations (2) and (3) are assembled to the outer periphery of the cylindrical portion 26A of the output gear 26 in step S33, In S34, as shown in FIG. 3, the output disc 2 is added to the splines 26B and 26B of the tubular portion 26A.
1, 21A are fitted and assembled, and needle bearings 80, 81 are assembled on the inner circumferences of the output disks 21, 21A via snap rings 82, 83, and the gear housing ASSY sub-assembly step S102 is completed.

The gear housing ASSY 28 assembled in the above steps S20 to S34 is output from the end surface 28E of the front gear housing 28A which serves as a reference of the gear housing ASSY 28 in a state where a predetermined preload is applied to the angular ball bearings 59, 159. The axial distance to the end surfaces of the disks 21 and 21A is set to a predetermined design value L1 = L2 and sent to the transmission section assembling step S100 in FIG.

Next, an example of the shifting portion assembling step S100 and the shifting portion adjusting step S110 will be described in detail with reference to the flowchart of FIG.

Steps S1 to S12 of FIG. 10 are the speed change portion assembling step S100, and step S13 and subsequent steps are the speed change portion adjusting step S110.

First, in step S1, the casing 10 is placed on a bed or the like for assembly work. At this time, in order to perform the work smoothly, the casing 10 is placed with the upper part of FIG. 1 on the bed side, and the unillustrated oil pan side (lower part of FIG. 1) facing upward.

[0112] Next, in step S2, S3, assembled together to fasten the upper link support member 12 to the inner periphery of the casing 10, opposite trunnions 3L, the upper link 4 that connects an upper portion of the trunnion 3R. It should be noted that these assembling operations are performed by the first and second toroidal transmission units 5.
1 and 52 respectively (the same applies hereinafter).

Next, in step S4, the above step S
As shown in FIG. 5, the gear housing ASSY 28 preassembled in 20 to S34 as shown in FIG. 3 is attached to the end surface of the bracket 10A projecting from the inner periphery of the casing 10 so as to project from the upper portion of the gear housing ASSY 28. The gear housing ASSY 28 is coupled to the casing 10 by contacting the end surface 28E of 28A and then fastening the bolt 28C.

At this time, the gear housing ASSY 28 is assembled in the casing 10 because the axial distances from the end surface 28E to the output disks 21 and 21A are set to the predetermined values L1 and L2 in the gear housing ASSY sub-assembly step S102. The relationship between the axial lines 3z and 3z of the trunnions 3L and 3R of the first and second toroidal speed change units 51 and 52 and the axial distances L3 and L4 between the end faces 28E does not require any special adjustment, and L3-L1 = L4-L2 (4), the relationship between the output disks 21 and 21A and the axes of the power rollers 1L and 1R of the first and second toroidal speed change units 51 and 52 is always a uniform value. As in the conventional example, the distribution of the pressing force becomes non-uniform, and the power roller 1L,
It is possible to prevent the 1R from slipping.

Then, in step S5, the gear housing
After temporarily placing the input disk 20A on the inner circumference of the casing 10 facing the output disk 21A of the second toroidal speed changer 52 attached to the ASSY 28, step S6
Then, the CVT shaft preassembled as shown in FIG.
After inserting the ASSY 25A from the front side of the casing 10 (the left side in FIG. 1) and inserting the rear end portion 25R into the cylindrical portion 26A of the output gear 26 and the inner circumferences of the output discs 21 and 21A, the CVT shaft 25 is further attached. The rear end 25R is inserted and inserted through the inner circumference of the temporarily placed input disk 20A, and the inner circumference of the input disk 20A is engaged at the position of the rear ball spline 24.

Next, in step S7, the trunnion sub-assemblies 3LA and 3RA preassembled as shown in FIG. 6 are assembled to the casing 10.

Trunnion 3L, 3R Rotating shaft portion 3 at the upper end
While inserting a and 3a into the upper link 4, the power rollers 1L and 1R supported by the pivot shaft 2 are assembled so as to be sandwiched by the input / output disks 20, 21, 20A and 21A, respectively. These trunnions 3L, 3R
When inserting the rotating shaft portion 3a of the above into the upper link 4,
Each rotation shaft portion 3a and each through hole 4L, 4 of the upper link 4
A spherical bearing 7 and a needle bearing 8 are interposed between R.

In this way, with the upper ends of the trunnions 3L, 3R positioned by the upper links 4, various parts are assembled to the rotating shaft portion and the rod portion 6b constituting the lower portions of the trunnion sub-ASSYs 3LA, 3RA.

That is, in step S8, in order to synchronize the tilt angles of the trunnions 3L and 3R facing each other, the pulley groove 37 provided in the offset portion 3c of the trunnions 3L and 3R.
The wire 36 is wound in a figure-eight shape.

Next, in step S9, the trunnion 3
After assembling the lower link 5 to the lower rotating shaft 3b of the L and 3R, the lower side of the rotating shaft 3b engaged with the lower link 5
The pulleys 35 are respectively press-fitted into the cylinder body 60 , and the cylinder body 60 is inserted into the rod portions 6b of the four trunnions, so that the lower link 5 is connected to the lower link support member 30 and is swingably supported.

Then, in step S10, the wire 36 for synchronizing the tilt angle is wound around the trunnions 3L, 3L and 3R, 3R adjacent to each other in the first and second toroidal speed change parts 51, 52 in a figure eight shape.

In step S11, the piston 6a is press-fitted from the lower end of each rod 6b and inserted into the inner circumference of the cylinder body 60. Then, in step S12, each trunnion 3 is inserted.
The cylinder body 61 forming the bottom of the cylinder body 60 is inserted through the rod portions 6b of L and 3R, and step S12 is performed.
Then, as shown in FIG. 2, the cylinder bodies 61 and 60 are fastened to the casing by the bolts 64, and the nuts 65 (see FIG. 1) are fastened to the end portions of the rod portions 6b, respectively. Fix 35 etc.

In this way, with the CVT shaft ASSY 25A temporarily assembled, the gear housing ASSY 28, the trunnion sub ASSY 3LA, 3RA are assembled, and the respective parts are assembled to complete the first and second toroidal speed change parts 51, 52. After step S13, the disc springs 40, 41
The shim 42 adjustment process for determining the preload of the s.

First, in step S13, the CVT shaft 25 supported by the gear housing ASSY 28 and having only the input disc 20A inserted through the rear end portion 25R is shown in FIG.
As shown in FIG. 5, the jig 100 is supported and the axis of the CVT shaft 25 is positioned at the axis C ₀ on the casing 10 side.

The jig 100 engages with the front end portion 25F of the CVT shaft 25 to position it on the axis C _0.
03 and an arm portion 101 for fixing the support portion 103 to the casing 10, and by fastening a bolt 102 inserted into a predetermined position of the arm portion 101 to a predetermined screw hole of the casing 10, the CVT shaft 25 The front end portion 25F is positioned by the jig 100 on the axis C ₀ , and the central portion is positioned by the output gear 26.

Therefore, the CVT shaft 25 is located at a predetermined axial position on the axis C ₀ in the casing 10, and the input / output discs 2 of the first and second toroidal speed change parts 51 and 52.
0 to 21A are evenly positioned so as to hold the power rollers 1L and 1R.

After positioning the CVT shaft 25 on the predetermined axis C ₀ , the ball is inserted into the rear ball spline 24 in step S14, and the input disc 20 is inserted.
After connecting A and the CVT shaft 25 in the rotational direction, in step S15, the shim 42 is attached so as to abut the step portion 25b of the CVT shaft 25, and then the disc spring 40,
After inserting 41 into the outer periphery of the shim 42, lock nut 43
Is fastened to measure the axial gap between the inner circumferences of the disc springs 40 and 41, and the shim 42 is selected so that the gap falls within a predetermined range. In addition, the measurement of this gap, for example,
The gear ratio, which is performed by a plastic gauge or the like held in advance by the disc springs 40 and 41, and which measures the gap is
In consideration of the bending of the input / output disk, the axial dimension of the shim 42 is set so that the gap measured at the gear ratio = 1 shown in FIG. Select.

Thus, when there is no load, the power roller 1L,
Shim 4 so that the preload that holds 1R becomes a predetermined value
After adjusting 2, the shim 42 and the disc springs 40 and 41 are assembled to the rear end 25R of the CVT shaft 25 in step S16, and the lock nut 43 is fastened in step S17 to complete the assembly of the transmission unit.

First and second toroidal speed change parts 51, 52
After the assembling is completed, the jig 100 fixing the front end 25F of the CVT shaft 25 is removed in step S19, and the cam flange 56 is attached to the CVT shaft 2.
The bolt (not shown) fixed to No. 5 is removed to make the cam flange 56 rotatable relative to the CVT shaft 25, and then the transmission section assembling step S100 and the transmission section adjusting step S110 are completed.

As described above, the axial distance L3 from the end surface of the bracket 10A to which the gear housing ASSY 28 is attached to the rotation shafts 3z of the trunnions 3L and 3R of the first toroidal speed changer 51, and the second distance from the end surface of the bracket 10A to the second axis. The casing 10 is processed in advance so that the axial distance L4 of the toroidal transmissions 52 to the rotating shafts 3z of the trunnions 3L and 3R is L3 = L4, and the first and second toroidal transmissions 51 and 52 are assembled. Gear Ha
In the housing assembly subassembly step S102 , the gear housing assembly 28 is assembled based on the end surface 28E of the front gear housing 28A, and the angular ball bearing 5
Preload adjustment shim 7 so that the preload of 9, 159 becomes a predetermined value.
0 and 71 are adjusted, and the axial distance from the end face 28E to the end faces of the output disks 21 and 21A is a predetermined value L1.
Since the positioning is adjusted so that the shims 72 and 73 are adjusted so that L = 2, the gear housing assembly 28
If the end surface 28E of is connected to the end surface of the bracket 10A,
The axial distances L3 and L4 from the trunnions 3L and 3R to the end surface 28E are set to be equal, and in the trunnion ASSY sub-assembly step S103, the axial distance from the end surface 28E to the end surfaces of the output disks 21 and 21A is L1 = L2. Is set so that the output disks 21, 2
1A and the positional relationship of the axial lines of the power rollers 1L and 1R pivotally supported by the trunnions 3L and 3R can be set equally in the first and second toroidal speed change units 51 and 52, and the same as in the prior art example And the second toroidal transmission units 51, 5
An imbalance occurs in the pressing force applied to 2 and slippage occurs in the power rollers 1L, 1R, and the toroidal type continuously variable transmission 5
The torque transmission capacity of 0 and the durability can be reliably prevented from decreasing, and the relationship between the output disks 21 and 21A and the end surface 28E which is the reference position for assembly is determined by the gear housing ASSY.
Since it is performed separately in the sub-assembling step S102, it is possible to position the power roller and the output disc in the axial direction easily and with high accuracy without requiring a work requiring skill such as an adjustment work inside the casing 10. Therefore, it is possible to achieve both improvement in productivity and quality assurance of the double-cavity toroidal type continuously variable transmission 50.

14 and 15 show the first embodiment,
The positioning adjustment shims 72 and 73 interposed between the output housings 21 and 21A and the angular ball bearings 59 and 159 from the gear housing assembly 28 of the reference example are eliminated, and only the preload adjustment shims 70 and 71 are used for the angular ball bearing 5.
9, 159 preload adjustment and front gear housing 2
The axial distance from the end face of 8A to the output disks 21 and 21A is adjusted to L1 = L2, and other configurations are the same as those of the reference example .

In FIG. 14, the angular ball bearings 59, 159 that axially support the output gear 26 are arranged on the outer periphery of the cylindrical portion 26A between the output gear 26 and the output disks 21, 21A, and the angular ball bearings 59, 159 of the angular ball bearings 59, 159 are arranged. Inner ring 59
a and 159a are in direct contact with the back surfaces of the output disks 21 and 21A.

On the other hand, angular ball bearings 59, 159
Outer rings 59b and 159b are provided with flanges 59c and 159c projecting along the side surface of the output gear 26. The flanges 59c and 159c are formed on the axial end surfaces of the flanges 59c and 159c, the front gear housing 28A and the rear gear housing 28B. Preload adjusting shims 70, 71 are provided between the output gear 26 and the end surface facing the side surface, and by adjusting the thicknesses S ₃ , S ₄ of these preload adjusting shims 70, 71 as described later, The preload (bearing preload) applied to the angular ball bearings 59, 159 and the front gear housing 28
The axial distance from A to the end faces of the output disks 21 and 21A can be adjusted to L1 = L2.

Next, an example of the procedure for assembling each component and adjusting each axial dimension performed in the gear housing ASSY sub-assembly step S102 of FIG. 8 will be described in detail below with reference to the flowchart of FIG. 15 and FIG. To do.

First, in step S40 of FIG.
As shown in FIG. 3 of the reference example , the rear gear housing 28
The radial bearing 75 for supporting the gear 27a of the counter shaft is assembled to B.

In step S41, the pair of angular ball bearings 59, 159 are attached to the tubular portion 26A of the output gear 26 with the flanges 59c, 159c facing the side surfaces of the output gear 26, respectively.

Next, in step S42, as shown in FIG. 4, the axial distance A1 from the end surface 28E of the front gear housing 28A to the end surface of the front gear housing 28A that contacts the preload adjusting shim 70 is measured.

Similarly, in step S43, the preload adjusting shim 71 is moved from the end surface 28F of the rear gear housing 28B joined to the end surface 28E of the front gear housing 28A.
The axial distance A2 to the end surface of the rear gear housing 28B that comes into contact with is measured.

In step S44, a flange 159c protruding from the end surface of the inner ring 59a of the angular ball bearing 59 on the side of the first toroidal transmission unit 51 mounted on the output gear 26 to the angular ball bearing 159 on the side of the second toroidal transmission unit 52. Is measured from the end surface of the inner ring 159a of the angular ball bearing 159 on the second toroidal speed changer 52 side to the first distance E1.
The axial distance E2 to the end surface of the flange 59c of the angular ball bearing 59 on the toroidal transmission 51 side is measured.

In step S45, the axial distances D1 and D2 between the end surfaces and the back surfaces of the output disks 21 and 21A are measured, respectively.

Then, in step S46, the thicknesses S ₃ and S ₄ of the preload adjusting shims 70 and 71 are calculated based on the above axial distances and the following equations, and the thickness preload adjustment according to the calculation result is performed. Select shims 70, 71.

S ₃ = L2-D2-E2 + A1 + (K / 2) ...... (5) S ₄ = L1-D1-E1 + A2 + (K / 2) …… (6) However, K is the tightening allowance in advance. Design values L1 and L2 set
Is a preset design value.

In this way, by selecting the preload adjusting shims 70 and 71 having the thicknesses S ₃ and S ₄ obtained by the above equations (5) and (6), the error due to the stacking of the dimensional tolerance of each component is absorbed. The preload of the angular ball bearings 59, 159 is set to a predetermined value, and the axial distance from the end surface 28E of the front gear housing 28A, which is the reference of the gear housing ASSY 28, to the end surfaces of the output disks 21, 21A is
The predetermined design value L1 = L2 is set.

In step S47, the above step S46 is performed.
The preload adjusting shims 70 and 71 selected in
Attach to the end face of 159c.

Then, in step S48, the output gear 26 in which the angular ball bearings 59, 159 and the preload adjusting shims 70, 71 are attached is attached to the rear gear housing 28B, and the gear 27a of the counter shaft is attached.
Is assembled to the radial bearing 75 of the rear gear housing 28B.

In step S49, the end surface 28E of the front gear housing 28A and the rear gear housing 28B are connected.
End face 28F of the bolt 7 inserted into the rear gear housing 28B through a screw hole formed in the upper portion of the front gear housing 28A as shown in FIG.
4, the front gear housing 28A and the rear gear housing 28B are integrally connected to house the output gear 26 and the gear 27a inside.

Then, in step S50, the tubular portion 26A
Output discs 21, 21 to the splines 26B, 26B
A is fitted and assembled, and output disc 2
Assemble the needle bearings 80 and 81 on the inner circumference of the gear housing AS through the snap rings 82 and 83.
The SY sub-assembly step S102 ends.

The gear housing assembly 28 assembled in the above steps S40 to S50 is provided with the preload adjusting shim 70,
Only by adjusting 71, the angular ball bearing 59,
The adjustment of the preload of 159 and the end surface 28E of the front gear housing 28A which is the reference position of the gear housing ASSY 28.
Output axial distance to the end face of the disc 21, 21A, can be set to a predetermined design value L1 = L2, in addition to the effect of the reference example from the positioning adjustment shims 72 and 73
By omitting, it is possible to reduce the number of parts and the process of selecting shims, and it is possible to secure the quality of the toroidal type continuously variable transmission while further improving the productivity.

In the above embodiment, the output gear 2
Although the bearings that support 6 and the output disks 21 and 21A are angular ball bearings, they may be tapered roller bearings (not shown).

Further, in the above embodiment, an example in which a gear is used as a transmission means from the output disks 21, 21A to the counter shaft 27 is shown, but although not shown,
It may be composed of a sprocket and a chain.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a toroidal type continuously variable transmission showing a reference example of the present invention.

FIG. 2 is a vertical cross-sectional view taken along the line AA of FIG.

FIG. 3 is a sectional view of the gear housing ASSY.

FIG. 4 is also a half cross-sectional view of the gear housing ASSY, showing the relationship of each dimension to be measured in order to select the thickness of the shim.

FIG. 5 is a cross-sectional view showing how the toroidal type continuously variable transmission is assembled.

FIG. 6 is a sectional view of a trunnion sub-ASSY.

FIG. 7 is a sectional view of a CVT shaft ASSY.

FIG. 8 is a process diagram showing an outline of assembly of a toroidal type continuously variable transmission.

FIG. 9 is a flowchart showing an example of a gear housing assembly subassembly process.

FIG. 10 is a flowchart showing an example of an assembly process and an adjustment process of the toroidal continuously variable transmission, showing the assembly process.

FIG. 11 is a sectional view of a toroidal-type continuously variable transmission showing a relationship between a CVT shaft, a casing, and a jig.

FIG. 12 is a cross-sectional view of the toroidal type continuously variable transmission showing how the power roller tilts when the gear ratio = 1.

FIG. 13 is a graph showing the relationship between the gear ratio and the preload of disc springs.

FIG. 14 shows the first embodiment, and a gear housing assembly
FIG.

FIG. 15 is a flowchart showing an example of a gear housing assembly subassembly process.

FIG. 16 is a schematic configuration diagram showing a toroidal type continuously variable transmission having a double cavity.

[Explanation of symbols]

1L, 1R Power roller 2 pivot shaft 3L, 3R trunnion 3LA, 3RA Trunnion Sub-ASSY 3z rotation axis 6 hydraulic cylinder 10 casing 10A bracket 20, 20A input disk 21, 21A output disc 23 Front Ball Spline 24 Rear Ball Spline 25 CVT shaft 25b step 25A CVT shaft assembly 26 output gears 26A tube 26B spline 27a gear 27 counter shaft 28 Gear housing assembly 28A front gear housing 28B rear gear housing 28C bolt 28D through hole 28E, 28F End surface 40, 41 Disc spring 42 Sim 43 Lock nut 50 toroidal type continuously variable transmission 51 1st toroidal transmission 52 Second toroidal transmission 53 Torque converter 54 Forward / reverse switching device 56 cam flange 56a claw 56b shaft 57 Cam roller 58 ball bearing 59,159 Angular Ball Bearing 59a, 159a Inner ring 59b, 159b Outer ring 59c, 159c Flange 70,71 Preload adjustment shim 72, 73 Positioning adjustment shims 74 volts 75 radial bearing 100 jigs 101 Arm 102 volts 103 support

Claims (2)

(57) [Claims] 1. A first toroidal transmission unit and a second toroidal transmission unit, which are coaxially arranged on an input shaft and respectively include a pair of input disks and output disks, and are arranged to face each other with the input shaft interposed therebetween. A trunnion that rotatably and tiltably supports a power roller held between the input and output disks; a pressing force generating unit that is disposed on the input shaft and generates a force for holding and pressing the power roller; A method for assembling a toroidal type continuously variable transmission, comprising: a transmission unit that is connected between output disks of the first and second toroidal transmission units and that transmits power to a drive shaft side. The output discs of the first and second toroidal speed change parts are assembled in advance as a reference of, and the output discs of the first and second toroidal speed change parts are set from the predetermined reference position of the transmission means. Sub-assembly process including adjustment process to adjust the distance to the end face to a predetermined value, process of assembling the transmission means with this output disc pre-assembled to the casing, and transmission of after the pressing force generation means and the input disc are assembled to the input shaft. A step of assembling the trunnion and the power roller after being inserted into the means, wherein the transmission means accommodates the gear or sprocket and the gear or sprocket connected between the pair of output disks and the casing. Housing, a pair of bearings arranged on both sides of the gear or sprocket in the axial direction and supported by the housing, and the axial distance from the predetermined reference position of the housing to the end surface of each output disk and the bearing. And an axial positioning means for adjusting the preload applied together, The receiver couples the outer ring to the housing, while coupling the inner ring to the tubular portion of the gear fitted with the output disc, the axial positioning means is interposed between the outer ring and the housing, and the adjusting step includes the output disc. And a method for assembling a toroidal type continuously variable transmission, wherein the axial distance of the axial positioning means is adjusted according to the axial dimension of the gear or sprocket to adjust the axial distance and the preload at the same time. 2. The method for assembling a toroidal type continuously variable transmission according to claim 1, wherein the predetermined reference position of the housing is a surface on which the housing is assembled to the casing.