JPH11108139A - Assembling method for toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To easily and accurately coordinate the relative positioning of a pair of output discs with each power roller by absorbing the dimensional tolerance. SOLUTION: Output discs 20 and 21A are installed while an output gear 26 is interposed, and the axial direction distance from the end face 28E to serve as reference for a gear housing ASSY28 to the end face of the output disc 20/21A is adjusted and the gear housing ASSY28 is assembled previously, and upon assembling the gear housing ASSY28 on a casing 10, a CVT shaft 25 is inserted and then a trunnion 3L is assembled to the casing.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

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

[0002]

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

[0003] Such a toroidal-type continuously variable transmission is disclosed in JP-A-2-163562 and JP-A-4-78.
As disclosed in, for example, Japanese Patent Publication No. 366, a double-cavity toroidal-type continuously variable transmission including two sets of half-toroidal-type transmission units is known.

As shown in FIG. 16, a torque converter 53 having a lock-up clutch and being coupled to an engine is provided on the input side of a toroidal type continuously variable transmission 50.
And a forward / reverse switching device 5 on the output side of the torque converter 53.
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 transmission 51 includes a pair of power rollers 1L and 1R sandwiched between the input disk 20 and the output disk 21. The second toroidal transmission 52 includes an input disk 20A and an output disk. 21A
And a pair of power rollers 1L and 1R sandwiched between the power rollers 1L and 1R. These power rollers 1L and 1R are supported by a trunnion (not shown) so as to be tiltable and rotatable, respectively. Note that the tilting motion of the power rollers 1L and 1R is a rotating motion that changes the contact radius with the input / output disk. Each trunnion is penetrated in the paper plane by an actuator (not shown) (axial direction of the trunnion).
And the power rollers 1L and 1R are tilted in accordance with the displacement to change the gear ratio.

Here, the power transmission of the toroidal type continuously variable transmission 50 is performed by holding the power rollers 1L, 1R arranged between the input and output disks with a pressing force of several tons, and connecting the power rollers 1L, 1R 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 slippage between the input / output disks 20 and 21A.

Therefore, the input disks 20, 20A of the first and second toroidal transmission units 51, 52 are connected to the input shaft 55.
At the two ends of the CVT shaft 25 rotationally engaged with each other, the CVT shaft 25 is coupled via the front ball splines 23 and 24 in the rotational direction, while being supported so as to be displaceable in a predetermined range in the axial direction (axial direction of the CVT shaft 25). Is done. On the other hand, the output discs 21 and 21A of the first and second toroidal transmission sections 51 and 52 are relatively rotatably disposed in the middle of the CVT shaft 25, and the output discs 21 and 21A are output gears disposed between the back surfaces of each other. 26, the output gear 26 and the output disks 21, 2
Angular ball bearings 59 provided between 1A,
159, the output gear 26 and the output disks 21, 21A and CV are rotatably supported on the casing 10 side.
The T shaft 25 is relatively rotatable.

Then, at both ends of the CVT shaft 25,
A cam roller 57 (pressing force generating means) for urging the input disks 20, 20A axially displaceable in the axial direction and a disc spring 40 (preload generating means) are provided. The biasing force causes the power rollers 1L and 1R to be held and pressed 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 55 </ b> A radially formed from the end of the input shaft 55 is circumferentially engaged with the claw 56 a of the cam flange 56. While being engaged, the cam flange 56 is supported so as to be rotatable relative to the CVT shaft 25.

The cam flange 56 is provided on the input disk 2.
A cam roller 57 that is rotatable in the circumferential direction with the back surface of the cam roller 57 is supported by a shaft (not shown) projecting in the radial direction. Then, the rear surface of the input disk 20 or the cam flange 56
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, and the CVT shaft 25
The pressing force of the input / output disks 20 to 21A for holding the power rollers 1L and 1R is determined in accordance with the relative rotation angle between the input shaft 55 and the cam flange 56, that is, the magnitude of the torque applied to the input shaft 55. The torque transmission capacity of the transmission 50 is determined by the pressing force.

The other end of the CVT shaft 25 provided with the cam roller 57 is provided with a disc spring 40 for supporting the pressing force generated by the cam roller 57 and applying the pressing force when no load is applied (hereinafter referred to as preload). The disc spring 40 presses the rear surface of the input disk 20A constituting the second toroidal transmission portion 52 in the axial direction with a predetermined urging force.
Power is transmitted by holding the 1R. The disc spring 40 is fixed to the C spring by a fastening means such as a lock nut 43 or the like.
It is fixed to the end of the VT shaft 25.

In this manner, the driving force of the engine input to the CVT shaft 25 via the cam roller 57 and the input disk 20 changes the pressing force corresponding to the input torque to the cam roller 5.
7, while the input disks 20, 20A provided at both ends of the CVT shaft 25 hold the power rollers 1R1L and the output disks 21, 21A with uniform pressing force, according to the tilt angles of the power rollers 1L, 1R. Power is transmitted from the input disks 20, 20A to the output disks 21, 21A at the changed gear ratio, and is output from the countershaft 27 to the drive shaft via the gear 27a meshing with the output gear 26.

By the way, the assembling of the toroidal type continuously variable transmission 50 is performed by first and second toroidal transmission portions 51, 52 from the cam flange 56 to the CVT shaft 25.
And the disc spring 40 are sequentially assembled and 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.

After the first and second toroidal transmission portions 51 and 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, when assembling and assembling the double-cavity toroidal type continuously variable transmission as described above, a pair of output discs 21 and 21A are required.
Of the power rollers 1L, 1R and the axial direction of the output disks 21, 21A (the axial direction of the CVT shaft 25).
The parts may be shifted due to stacking of dimensional tolerances or the like, and if such a shift occurs, the pressing force applied to the first toroidal transmission unit 51 and the second toroidal transmission unit becomes uneven, and the power with the reduced pressing force The rollers have a problem that the torque transmission capacity is reduced due to slippage, while the excessive pressing force reduces the durability of the rolling surfaces of the power roller and the input / output disk. Since a large number of parts are assembled, there is a problem that the axial positions of the power rollers 1L and 1R and the output disks 21 and 21A cannot be easily adjusted.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and has as its object 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 is provided a first toroidal transmission unit and a second toroidal transmission unit which are coaxially disposed on an input shaft and each include a pair of input disks and output disks. A trunnion that is disposed opposite to the input shaft and rotatably and tiltably supports a power roller held by each input / output disk; and a trunnion disposed on the input shaft to hold and press the power roller. Assembling of a toroidal-type continuously variable transmission including a pressing force generating means for generating a force, and a transmission means connected between output disks of the first and second toroidal transmission portions and transmitting power to a drive shaft side. A sub-assembly step of previously assembling the output disks of the first and second toroidal transmissions with the transmission means as a reference in the direction of the input shaft, and a transmission hand pre-assembled with the output disks. A step of assembling the to the casing,
Assembling the trunnion and the power roller after assembling the pressing force generating means and the input disk to the input shaft and then inserting it into the transmission means.

In a second aspect based on the first aspect, in the sub-assembly step, a distance from a predetermined reference position of the transmission means to an end surface of the output disk of the first and second toroidal transmission portions is determined. And an adjusting step for adjusting to a value.

In a third aspect based on the second aspect, the transmission means includes a gear or a sprocket connected between the pair of output disks, a housing for the gear or the sprocket, and a casing. A pair of bearings disposed on both sides of the gear or sprocket in the axial direction and supported by the housing, and adjusting an axial distance from a predetermined reference position of the housing to an end face of each output disk. An axial positioning means, wherein the adjusting step adjusts the axial positioning means according to the axial dimensions of the output disk and the gear or sprocket.

In a fourth aspect based on the second aspect, the transmission means includes a gear or a sprocket connected between the pair of output disks, a housing for the gear or the sprocket, and a casing. A pair of bearings disposed on both sides of the gear or sprocket in the axial direction and supported by the housing; and a bearing and an axial distance from a predetermined reference position of the housing to an end face of each output disk. An axial positioning means for adjusting both the applied preload and the adjusting step, wherein the axial distance and the preload are simultaneously adjusted by the axial positioning means according to the axial dimensions of the output disk and the gear or sprocket.

Further, the fifth invention is directed to the third or fourth embodiment.
In the invention, the predetermined reference position of the housing is:
This is the surface on which the housing is assembled to the casing.

In a sixth aspect based on the third aspect, the bearing couples the outer ring to the housing.
The inner ring is connected to the cylindrical portion of the gear fitted with the output disk, the axial positioning means is interposed between the inner ring and the output disk, and the adjusting step adjusts the axial dimension of the axial positioning means. .

In a seventh aspect based on the fourth aspect, the bearing couples the outer ring to the housing while the bearing is connected to the housing.
The inner ring is connected to the cylindrical portion of the gear fitted with the output disk, and the axial positioning means is interposed between the outer ring and the housing, and the adjusting step adjusts the axial dimension of the axial positioning means.

[0024]

Accordingly, the first aspect of the present invention is to assemble a double-cavity toroidal type continuously variable transmission including two sets of input disks and output disks coaxially arranged on an input shaft. In the sub-assembly process, the output disks of the first and second toroidal transmission units are assembled to the transmission means in advance using the transmission means as a reference in the input shaft direction, and then the transmission means is assembled to the casing. And
After the pressing force generating means and the input disk are inserted through 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 position in the axial direction is always accurately positioned, and the holding pressure applied by the pressing force generating means is evenly applied to the first and second toroidal transmission portions, thereby preventing the power roller from slipping and securing the quality. However, by assembling the output disks of the first and second toroidal transmission units to the transmission means in the sub-assembly process, there is no need to perform adjustment work or the like on the inner periphery of the casing. Productivity can be improved.

According to a second aspect of the present invention, in the sub-assembly step, the axial distance from the predetermined reference position of the transmission means to the end surfaces of the output disks of the first and second toroidal transmission portions can be adjusted to a predetermined value. For example, only by assembling the transmission means to the casing, the positioning of the power roller and the output disk can be performed with high accuracy, and the assembling work can be performed efficiently and the productivity can be improved.

According to a third aspect of the present invention, there is provided a pair of bearings disposed on both axial sides of a gear or sprocket of a transmission means and supported by a housing, and an end face of each output disk from a predetermined reference position of the housing. By adjusting the axial distance to the output disk and the axial dimension of the gear or sprocket by the axial positioning means,
The output disk can be easily and accurately positioned with respect to the reference position of the transmission means.

According to a fourth aspect of the present invention, there is provided a pair of bearings disposed on both axial sides of a gear or sprocket of a transmission means and supported by a housing, and an end face of each output disk from a predetermined reference position of the housing. The axial distance up to and the preload to the bearing are adjusted simultaneously by the axial positioning means according to the axial dimensions of the output disk and gear or sprocket, so that the output can be easily and accurately output to the reference position of the transmission means. The positioning of the disk and the setting of the preload on the bearing can be performed simultaneously.

According to the fifth aspect of the present invention, since the reference position of the housing is set to the surface of the housing assembled to the casing, the axial dimensions of the output disk and the gear or sprocket can be measured easily and accurately. Adjusting the axial position of the output disk with reference to the mounting surface on the casing, and then simply assembling the transmission means to the casing, always accurately set the axial position of the trunnion and other members mounted on the casing side and the output disk. can do.

According to the sixth aspect of the invention, the axial positioning with respect to the reference position of the output disk can be easily adjusted by the axial positioning means interposed between the inner race and the output disk.

According to a seventh aspect of the present invention, there is provided an axial positioning device for adjusting an axial position of an output disk with respect to a reference position by axial positioning means interposed between a housing and a bearing outer race.
The preload applied to the bearing can be adjusted simultaneously and easily, and the number of parts and the number of adjustment points can be reduced, thereby further improving productivity.

[0031]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the accompanying drawings.

FIGS. 1 to 12 show the same as the conventional example.
An example in which the present invention is applied to assembling a double-cavity toroidal type continuously variable transmission 50 composed of a pair of input / output disks 20, 21 and 20A, 21A is shown. And a duplicate description is omitted.

FIGS. 1 and 2 show a state in which a first toroidal transmission portion 51 composed of an input disk 20 and an output disk 21 and a second toroidal transmission portion 52 composed of an input disk 20A and an output disk 21A are assembled to a casing 10. The countershaft 27 and the input shaft 55 shown in FIG. 16 of the conventional example are not mounted, and the input shaft 55 and the input shaft 55 are rotated in the right end 25F side of the CVT shaft 25 in FIG. On the other hand, the left end 25R side in the figure is the drive shaft side. Here, the end 25F side is a front end, and the end 25R side is a rear end.

1 and 2, a first toroidal transmission 51 includes a pair of power rollers 1L and 1R sandwiched between a pair of input disks 20 and output disks 21 having toroidal grooves formed on opposing surfaces. I / O disks 20, 21
Of CVT shaft 25 a pair of trunnions 3L the axis = disposed to sandwich a rotation axis C ₀ (input shaft) is rotatably supported by a pivot shaft 2, 2 supported a proximal to 3R.

The second toroidal transmission section 52 is also constructed in the same manner as described above.
1A, a pair of power rollers 1L, 1R
The pivot shaft 2 is rotatably supported by a pivot shaft 2 having a base end supported by a pair of trunnions 3L and 3R disposed with the VT shaft 25 interposed therebetween.

The input disks 20, 20A and the output disks 21, 21A are arranged coaxially with the CVT shaft 25, and the input disks 20, 20A are connected to the CVT shaft 25.
Output disks 21 and 21A
Penetrates the CVT shaft 25 to the inner circumference and
It is rotatably supported relative to the T shaft 25.

The output disk 21 of the first toroidal transmission portion 51 and the output disk 21A of the second toroidal transmission portion 52 are cylindrical portions 26A, 26A protruding from both sides of the output gear 26 provided in the middle between the two. Are respectively fitted to the outer circumferences and are integrally connected.

The gear 27 meshing with the output gear 26
The counter shaft 27 shown in FIG.
To transmit power to the drive shaft at a gear ratio according to the tilt angle of the power rollers 1L, 1R. The gear 27a is supported by a rear gear housing 28B via a radial bearing 75.

In the present embodiment, the counter shaft 27 is disposed below the second toroidal transmission section 52,
Front gear housing 28A, rear gear housing 2
The countershaft 27 housed in the inside 8B has a configuration in which the countershaft 27 can be attached and detached via a spline or the like. These output gears 26 and gears 27a output disks 21 and 21A are provided with transmission means as described later. The gear housing assembly (ASSY) 28 is assembled in advance.

Next, in FIG. 2, the first toroidal speed change section 51 is provided with a rotation axis C ₀ (C
In a plane perpendicular to the VT axis of the shaft 25), the trunnion 3L on the left and right sandwiching the rotation axis C _0, 3R are disposed, these trunnions 3L, the rotation axis 3z coaxially with the upper and lower ends of the 3R Are formed, while the input / output disk 20 is provided between the rotating shaft portions 3a and 3b.
Offset portions 3c are formed by a predetermined amount in the outer circumferential direction of the shaft 21 and the pivot shaft 2 is supported on 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
Are similarly constructed, and the power rollers 1L, 1R sandwiched between the input / output disks 20A, 21A are connected to the pivot shafts 2, 2 provided on the trunnions 3L, 3R arranged opposite to each other.
Supported by Although not shown, the trunnion 3L of the first toroidal transmission 51 is provided with a feedback means (not shown) at the lower end of the rod 6b, so that the trunnion 3L is lower in FIG. 1 and FIG. Side) is set large.

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

In the trunnion ASSY sub-assembly step S103 shown in FIG. 8, the trunnions 3L and 3R are connected to the rod 6b and the pivot shaft 2 to the rotating shaft 3b at the lower end of the trunnions 3L and 3R as shown in FIG. Assemble to the offset part 3c. Furthermore, pivot shaft 2
After inserting the ball bearing 16 and the outer ring 18 that support the thrust force and the needle bearing 19 that performs radial positioning, the power roller 1
Assemble L and 1R, respectively, and install trunnion subassy 3
LA and 3RA, and in a transmission unit assembling step S100 in FIG.
Assemble the Hetranon sub ASSY 3LA and 3RA. In addition, the trunnion sub ASSY3LA is a trunnion 3
L is assembled, trunnion sub ASSY3RA,
It is an assembly of the trunnion 3R.

On the other hand, trunnion 3L, rotating shaft 3a of the upper and lower ends of the 3R, 3b are pivotable upper link 4 in a plane perpendicular to the rotation axis C ₀ of the input and output discs 20, 21 opposing, The upper link 4 and the lower link 5 are connected to each other through a lower link 5, and the power roller 1 attached to the pivot shafts 2
It supports the thrust force (pressing force) from L and 1R.

Here, the upper link 4 and the lower link 5
Through holes are respectively formed at both ends and a central portion in the longitudinal direction, and the through holes 4L, 4R and 5L, 5R at both ends are formed.
In while inserting the trunnion 3L, 3R of the rotating shaft portion 3a, 3b, respectively, through hole 4C of the central portion, 5C is toward the casing 10 and the cylinder body 60 side to the rotation axis C ₀ of the input and output discs 20, 21, The upper link support member 12 and the lower link support member 30 projecting upward and downward in the drawing respectively are supported so as to be swingable.

The left and right hydraulic cylinders 6, 6 are trunnions 3
When the L and 3R are driven synchronously 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,
And the pins 14, 31 of the lower link support member 30 as a fulcrum, swings in a plane mainly perpendicular to the rotational axis C ₀ of the input and output discs 20, 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 interposed, respectively, to allow the upper link 4 and the lower link 5 to be inclined 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 shafts 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 periphery of the rotating shaft portions 3a and 3b of the trunnion 3, and an inner periphery of the spherical bearing 7 is engaged with the outer periphery of the needle bearing 8.
The spherical surface formed on the outer periphery of the spherical bearing 7
L, 4R and 5L, 5R engage the inner circumference.

Here, the upper link support member 12 that supports the upper link 4 so as to swing freely is provided with a bolt 1 at one end.
5, a pair of through-holes 12a provided on the side surface for supporting the upper link 4 in a swingable manner. The pins 14, 14 are fitted, and these pins 14 are arranged in parallel with the rotation axis C ₀ of the input / output disks 20, 21, and are connected to the upper link 4 at the tips protruding from the upper link support member 12. It is swingably supported.

The upper link support member 12 is provided with a bolt 1 inserted into a through hole opened at the bottom (lower side in the figure).
5 is fastened to the positioning member 11.

The positioning member 11 is attached to the upper surface of the inner periphery of the casing 10. The upper surface of the upper surface which is in contact with the inner periphery of the casing 10 engages with the knock pin 9 previously fixed to the casing 10, and the positioning member 11 Positioning is performed so as not to deviate from a predetermined position. The positioning member 11 is a bolt 1 fastened to the casing 10 from the rotation axis _C0 side.
It is connected to the casing by 7,17.

On the other hand, the positioning member 11 on the rotation axis C ₀ side has a convex portion 1 fitted to the inner periphery of the upper link support member 12.
1a is formed, and 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 at a predetermined position on the inner periphery of the casing 10 via the positioning member 11.

On the other hand, a lower link support member 30 for swingably supporting the lower link 5 is fixed to a cylinder body 60 facing the upper link support member 12 with the rotation axis C ₀ of the input / output disk interposed therebetween. The pedestal 60A protrudes upward.

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

[0054] lower link support member 30 to swing freely supports the lower link 5, as shown in FIG. 1, a pin 31 projecting in parallel with the rotational axis C ₀ of the input and output discs 20, 21 Like the upper link 4 side, the lower link 5 is coupled to the center through hole 5C of the lower link 5 through a through hole that is fitted with the pins 31 and 31 so that the lower link 5 can swing freely by the pin 31. To support.

Here, stud bolts 33 protrude from the lower surface of the lower link support member 30 of the lower link 5 in the vertical direction (Z-axis direction) in the figure, and these stud bolts 33 are connected to the pedestal 60A. The lower link support member 30 is inserted into a through hole 60D provided in the cylinder body bottom portion 61 and screwed with a nut 33a at an end protruding from the lower surface of the cylinder body 60 or the lower surface of the cylinder body bottom portion 61, thereby connecting the lower link support member 30 to the base. 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 of the lower link support member 30 described later in the X-axis direction can be adjusted.

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. Locating hole 60B is shown in FIG.
As shown in the figure, the rotation axis C ₀ of the lower link support member 30 is fitted to the knock pin 32 in the rotation axis C ₀ direction (Y-axis direction).
2, the displacement of the knock pin 5 is allowed within a predetermined range in the longitudinal direction (X-axis direction in the figure) of the lower link 5, as shown in FIG. For this reason, the nut 33a
During the assembly of the toroidal-type continuously variable transmission, the position of the lower link support member 30 in the X-axis direction is
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 transmission portion 52 is also provided with the first link member.
The configuration is the same as that of the toroidal transmission unit 51.

Further, as shown in FIG. 1, the cylinder body 60 and the cylinder body bottom 61 are
After being positioned at a predetermined position, the casing 10 is fastened to the casing 10 by bolts 64.

In order to synchronize the tilt angles of the opposing trunnions 3L, 3R, pulley grooves 37, 37 are formed below the offset portion 3c. Wire 36 wrapped around
The trunnions 3L, 3 rotating in opposite directions to each other
Synchronization of the tilt of R is performed.

Further, a pulley 35 is also fitted to the rotating shaft 3b of the trunnions 3L, 3R.
Has a trunnion 3L, 3L or 3
In order to synchronize the tilt of R and 3R, the wire 36 is wound in a figure eight shape.

Next, in the CVT shaft ASSY sub-assembly step S101 shown in FIG. 8, the cam flange 56 is attached to the end portion 25F side via the ball bearing 58 as shown in FIG. The flange 56 is supported rotatably relative to the CVT shaft 25, and a cam roller 57 (pressing force generating means) is assembled to a plurality of shafts 56b formed on the cam flange 56 and protruding in the radial direction. The toroidal transmission portion 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 restrict 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 portion 25F side.
The ball is inserted into 3 and connected in the rotation direction.

Here, in the CVT shaft assembly sub-assembly step S101, the relative rotation between the cam flange 56 and the input disk 20 of the first toroidal transmission portion 51 is regulated. After fixing the back and cam flange 56, C
The VT shaft ASSY 25A 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 at which the pressure occurs becomes minimum.

On the other hand, as shown in FIG. 1, the rear surface of the input disk 20A constituting the second toroidal transmission portion 52 is pressed against the rear end 25R of the CVT shaft 25 in the axial direction (front side) by a predetermined urging force. Then, annular disc springs 40 and 41 for applying a preload in which the input / output disk sandwiches the power rollers 1L and 1R are provided.

The disc springs 40 and 41 are mounted between the inner periphery thereof and the CVT shaft 25 via a cylindrical shim 42. As shown in FIG. 7, the CVT shaft 25 is moved from the rear end 25R side. Lock nut 43 screwed into screw portion 25c
Is fastened to the position where the shim 42 contacts the step 25b,
The disc springs 40 and 41 are configured to apply a predetermined preload.

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

From the end 25R side, the rear ball spline 2
After assembling the ball 4 and the input disk 20A, a shim 42 having a predetermined length L in the axial direction is inserted through the outer periphery of the screw portion 25c, and an end of the shim 42 is formed on the step 25b formed on the CVT shaft 25. 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, and the shim 42 is inserted between the lock nut 43 and the step portion 25b.
, And compress the disc springs 40 and 41 to urge the input disk 20A toward the other end.

Next, the driving force transmitted to the output disks 21 and 21A is transmitted via 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 disk 21 and the output disk 21A are connected to the front gear housing 28A and the rear gear housing 28 via angular ball bearings 59, 159 provided between the rear surfaces of the output disk 21 and the output gear 26.
B, and the front gear housing 28A is fastened to a bracket 10A formed on the casing 10 via a bolt 28C so that the output disks 21, 21A and the output gear 26 are connected to the casing 10 side. Is supported rotatably.

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

The output gear 26 has cylindrical portions 26A formed on both sides in the direction of the axis (C ₀ ) of the CVT shaft 25. The CVT shaft 15 is inserted through the inner periphery of the cylindrical portion 26A so as to be relatively rotatable. Splines 26B, 26B are respectively formed from both ends on the outer periphery of the cylindrical portion 26A, and the output disks 21, 21A are fitted on the inner periphery.

Then, the output disk 21 and the output gear 26
The positioning adjustment shim 72 and the inner ring 59a of the angular ball bearing 59 are interposed between the side surfaces of the inner ring 59a.
The both ends in the axial direction are positioning adjustment shim 72 and output gear 2
In contact with the sixth aspect of, as shown in FIG. 4, it is possible in accordance with the positioning adjustment shim 72 thickness S _1, setting the distance to the end surface of the output disk 21 from the side of the output gear 26.

On the other hand, the output gear 2 is attached to the outer ring 59b of the angular ball bearing 59 disposed on the output disk 21 side.
6, a flange 59c protrudes along the side surface of the output gear 26, and an axial end surface formed on the flange 59c and facing the output disk 21 and a side surface of the output gear 26 formed on the front gear housing 28A. is preload adjusting shim 70 is interposed between the end surfaces, as shown in FIG. 4, the angular ball bearing 5 according to the thickness S ₃ of the preload adjusting shims 70
9, the preload (bearing preload) applied 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.
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 Can be set to the end face of. Further, a flange 159c protrudes from the outer ring 159b of the angular ball bearing 159 along the side surface of the output gear 26, and an axial end face formed on the flange 159c and facing the output disk 21A side, and a rear gear housing 28B And a preload adjusting shim 71 is interposed between the output gear 26 and the end face facing the side face of the output gear 26,
As shown in FIG. 4, it is possible to adjust the preload applied to the angular ball bearing 159 according to the thickness S ₄ of the preload adjusting shim 71.

The end faces of the output disks 21, 21A protrude from the end of the cylindrical portion 26A, and snap rings 82, 83 are formed on the inner circumferences of the protruding output disks 21, 21A.
Needle bearings 80 and 81 are disposed between the CVT shaft 25 and the outer periphery of the CVT shaft 25 through the gear housing ASSY2.
8 and the CVT shaft 25 rotate smoothly.

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

In the gear housing ASSY sub-assembly step S102 for assembling the gear housing ASSY 28, in FIG. 3, the front gear housing 28A is assembled with reference to the end face 28E joined to the rear gear housing 28B.
Inner rings 59a, 159a of the angular ball bearings 59, 159 such that the distances L1, L2 to the end faces of the
And the annular positioning adjustment shims 72, 73 provided between the rear surfaces of the output disks 21, 21A and the outer rings 59b, 159b of the angular ball bearings 59, 159.
The preload applied to the angular ball bearings 59, 159 by adjusting the annular preload adjustment shims 70, 71 interposed between the flanges 59c, 159c protruding from the front and the axial end surfaces of the front gear housing 28A and the rear gear housing 28B. Is adjusted in advance. The outer ring 5
9b and 159b are front gear housing 28A and rear gear housing 28 via flanges 59c and 159c.
B is in contact with only the end face of B and forms a gap between the side face of the output gear 26.

Then, in the transmission section assembling step S100, as shown in FIG. 5, the gear housing ASSY 28 previously assembled so that L1 = L2, the end face 28E of the front gear housing 28A is After being brought into contact with the end face of the bracket 10A protruding from the inner periphery, a through hole 28 formed in the front gear housing 28A is formed.
The gear housing ASSY 28 is assembled to the casing 10 by fastening the bolt 28C inserted through D to the bracket 10A.

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

Then, L1 = L based on the end face 28E.
Gear housing assembly pre-assembled to be 2
28 is connected to the bracket 10A, the positional relationship between the output disks 21, 21A and the trunnions 3L, 3R in the axial direction, that is, the positional relationship with the axis of the power rollers 1L, 1R is L3-L1 = L4-L2. Can be
The intervals between the input and output disks of the first and second toroidal transmission units 51 and 52 are equal, the pressing force applied in the axial direction is evenly distributed, and the first and second toroidal transmission units 51 and 52 are
2 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. Is deviated 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 the positioning adjustment shim 7 will be reduced, the positioning adjustment shim 7 will be described later.
8, 73 and the preload adjusting shims 70, 71 in the gear housing ASSY sub-assembly step S102 of FIG.
13 is adjusted in advance to L1 = L2 and then assembled to the casing 10, so that the pressing force or preload by the cam roller 57 or the disc springs 40, 41 is reduced by the first and second toroids as shown by the solid line in FIG. The power rollers 1L, 1R are evenly distributed to the speed change sections 51, 52.
, And the performance and quality of the toroidal-type continuously variable transmission 50 can be constantly maintained at a constant level.

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

First, the CVT shaft ASSY sub-assembly step S
At 101, as shown in FIG.
6. Attach the cam roller 57 and the input disk 20 of the first toroidal transmission portion 51, and fix the cam flange 56 to the input disk 20 at a position where the cam roller 57 is in a no-load state via a bolt or the like, and fix the CVT shaft.
Assemble as ASSY25A.

In the trunnion assembly sub-assembly step S103, as shown in FIG. 8, the rod 6b is connected to the rotating shaft 3b at the lower end of the trunnions 3L, 3R, the pivot shaft 2 is assembled to the offset portion 3c, and the pivot shaft 2 includes a ball bearing 16 and an outer ring 18
After inserting the needle bearings 19 and the power rollers 1L and 1R, the trunnion subassembly 3 is assembled.
It is assembled in advance as LA and 3RA.

In the gear housing ASSY sub-assembly step S102, as shown in FIG. 3, the angular ball bearings 59 and 159 are assembled to the output gear 26, and then the front gear housing 28A and the rear gear housing 28B
The output gear 26 and the gear 27a are assembled on the inner periphery of the outer ring, and the preload adjusting shims 70, 71 are attached to the outer ring flanges 59c, 159c, and then the bolt 74 is fastened. The housing 28B is connected. Further, positioning adjustment shims 72, 7 are provided at both ends of the cylindrical portion 26A of the output gear 26.
Then, the output disks 21 and 21A are connected to each other via 3 and assembled as a gear housing ASSY28.

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

Next, in the transmission section assembling step S100, the gear housing ASSY 28 is fastened to the bracket 10A protruding from the inner periphery of the casing 10, and then the pre-assembled CVT shaft ASSY 25A is inserted through the inner periphery of the cylindrical portion 26A. And the input disk 2 of the second toroidal transmission unit 52
Assemble OA. And four trunnion sub assemblies
After assembling the 3LA and 3RA with the casing 10 together with other parts, if the disc springs 40 and 41 are assembled to the rear end 25R of the CVT shaft 25 with the lock nut 43, the inside of the disc springs 40 and 41 in the transmission portion adjusting step S110. The preload is adjusted by selecting a shim 42 having a length corresponding to the dimensional tolerance of each component so that the circumferential gap is within a predetermined range.

After assembling the first and second toroidal transmission portions 51 and 52 mainly including the CVT shaft 25 inside the casing 10 based on the gear housing ASSY 28 in the torque converter and forward / reverse switching device assembling step S120. Similarly, the input shaft 55, the forward / reverse switching device 54, and the torque converter 53, which are rotationally engaged with the CVT shaft 25 in the same manner as in the conventional example, are sequentially assembled from the front of the casing 10, and the assembly process is completed.
It is sent to 30.

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

First, in step S20 in FIG. 9, the countershaft gear 27a is inserted into the rear gear housing 28B.
Is mounted in advance.

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

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

Similarly, in step S23, the preload adjusting shim 71 is moved from the end face 28F of the rear gear housing 28B joined to the end face 28E of the front gear housing 28A.
Is measured in the axial direction A2 to the end face of the rear gear housing 28B that contacts the rear gear housing 28B.

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.

In step S25, distances A1 and A2 from the joining end surfaces 28E and 28F of the front and rear housings 28A and 28B determined in steps S22 and S23 to the end surfaces where the preload adjusting shims come into contact with 70 and 71, respectively.
And the preload adjustment shim obtained in step S24 is 7
From the axial dimension B between the end faces of the flanges 59c and 159c abutting on the preload adjusting shims 7 by the following formula,
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 a closing margin and 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 each part. In step S26, the selected preload adjusting shims 70, 71 are connected to the end faces of the flanges 59c, 159c. Assemble to.

In step S27, the output gear 26 with the angular ball bearings 59 and 159 and the preload adjusting shims 70 and 71 assembled is mounted on the rear gear housing 28B, and the countershaft gear 27a
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
3 and a bolt 7 inserted into the rear gear housing 28B through a screw hole formed in the upper part 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 each other to house the output gear 26 and the gear 27a therein.

In step S29, it is confirmed whether or not the preload of the angular ball bearings 59 and 159 of the accommodated output gear 26 is appropriate. That is, the output gear 26 is checked for play in the axial direction, and the output gear 26 is checked for smooth rotation. 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 surface 28 of the front gear housing 28A projecting from the upper part of the integrally-assembled gear housing ASSY 28 in the drawing.
An axial distance C1 from E to the end face of the inner ring 59a of the angular ball bearing 59;
159, the axial distance C between the end faces of the inner rings 59a, 159a
Measure 2.

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.

In step S32, the inner ring 5
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.

After the positioning shims 72 and 73 having the thicknesses S ₁ and S ₂ selected in the above equations (2) and (3) are assembled on 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 disk 2 is
1, 21A are fitted and assembled, and the needle bearings 80, 81 are assembled via the snap rings 82, 83 on the inner circumference of the output disks 21, 21A, thereby completing the gear housing ASSY sub-assembly step S102.

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

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

Steps S1 to S12 in FIG. 10 correspond to the transmission section assembling step S100, and step S13 and subsequent steps correspond to the transmission section adjusting step S110.

First, in step S1, the casing 10 is placed on a bed or the like on which an assembling operation is performed. At this time, in order to carry out the operation smoothly, the casing 10 is placed with the upper part of FIG. 1 on the bed side, and the oil pan side (not shown) (the lower part of FIG. 1) facing upward.

Next, in steps S2 and S3, the upper link support member 12 is fastened to the inner periphery of the casing 10, and the opposing trunnion 3L and upper link 3R
The upper link 4 that connects the upper parts of the two is assembled. These assembling operations are performed by the first and second toroidal transmission units 51 and 52, respectively (the same applies hereinafter).

Next, in step S4, the above-mentioned step S
As shown in FIG. 5, a front gear housing protruding from the upper part of the gear housing ASSY 28 on the end face of the bracket 10A protruding from the inner periphery of the casing 10 as shown in FIG. The gear housing ASSY28 is connected to the casing 10 by fastening the bolt 28C after the end surface 28E of the 28A is brought into contact.

At this time, since the axial distance from the end face 28E to the output disks 21 and 21A is set to the predetermined values L1 and L2 in the gear housing ASSY sub-assembly step S102, the gear housing ASSY 28 is assembled to the casing 10. The relationship between the axial lines 3z, 3z of the trunnions 3L, 3R of the first and second toroidal transmission portions 51, 52 and the axial distances L3, L4 between the end surfaces 28E does not require any special adjustment, and L3-L1 = L4−L2 (4), and 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 transmission units 51 and 52 always becomes a uniform value. As in the conventional example, the distribution of the pressing force becomes uneven and the power roller 1L,
Slip can be prevented from occurring in the 1R.

Then, in step S5, the gear housing
After the input disk 20A is temporarily placed on the inner periphery of the casing 10 facing the output disk 21A of the second toroidal transmission unit 52 attached to the ASSY 28, step S6
Now, the pre-assembled CVT shaft as shown in FIG.
The ASSY 25A is inserted from the front side (the left side in FIG. 1) of the casing 10, and the rear end 25R is inserted into the cylindrical portion 26A of the output gear 26 and the inner circumference of the output disks 21 and 21A. The rear end 25 </ b> R is inserted and inserted into the inner periphery of the input disk 20 </ b> A on which the input disk 20 </ b> A is temporarily placed, and the inner periphery of the input disk 20 </ b> A is engaged with the rear ball spline 24.

Next, in step S7, the trunnion sub assemblies 3LA and 3RA assembled in advance as shown in FIG.

Rotation shaft 3 at the upper end of trunnions 3L and 3R
The power rollers 1L, 1R supported by the pivot shaft 2 are assembled so that the input / output disks 20, 21, 20A, 21A respectively hold the power rollers 1L, 1R while inserting the power rollers 1a, 3a into the upper link 4. These trunnions 3L, 3R
When inserting the rotary shaft portion 3a into the upper link 4,
Each rotary shaft 3a and each through hole 4L 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 and 3R being positioned by the upper link 4, various components are assembled to the rotating shaft and the rod 6b that form the lower part of the trunnion sub ASSYs 3LA and 3RA.

That is, in step S8, in order to synchronize the tilt angles of the opposing trunnions 3L and 3R, the pulley grooves 37 provided in the offset portions 3c of the trunnions 3L and 3R are used.
Is wound around the wire 36 in a figure eight shape.

Next, at step S9, the trunnion 3
After assembling the lower link 5 to the rotary shaft 3b below the L, 3R, the cylinder body 60 is inserted into each rod 6b of the four trunnions, and the lower link 5 is connected to the lower link support member 30 to swing. Make it movably supported.

In step S10, the pulleys 35 are respectively press-fitted below the rotating shaft 3b engaged with the lower link 5, and the first and second toroidal transmissions 5
3L, 3L and 3 of trunnions adjacent at 1, 52
A wire 36 for synchronizing the tilt angle with R and 3R is wound 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 periphery of the cylinder body 60, and then in step S12, each trunnion 3
The cylinder body 61 constituting the bottom of the cylinder body 60 is inserted into 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 bolts 64, and nuts 65 (see FIG. 1) are fastened to the ends of the rod portions 6b, respectively. 35 etc. are fixed.

In this way, with the CVT shaft ASSY 25A temporarily assembled, the first and second toroidal transmission parts 51 and 52 are completed by assembling the respective parts while assembling the gear housing ASSY 28 and the trunnion sub ASSYs 3LA and 3RA. After step S13, the disc springs 40, 41
The adjustment process of the shim 42 for determining the preload of is performed.

First, in step S13, the CVT shaft 25, which is supported by the gear housing ASSY 28 and only has the input disk 20A inserted through the rear end 25R, is moved to the position shown in FIG.
As shown in, and supported by the jig 100, to position the axis of the CVT shaft 25 the axis C ₀ of the casing 10 side.

[0125] jig 100 engages the front end portion 25F of the CVT shaft 25, a support portion 1 for positioning the axis C ₀
03, and an arm portion 101 for fixing the support portion 103 to the casing 10. The bolt 102 inserted into a predetermined position of the arm portion 101 is fastened to a predetermined screw hole of the casing 10 so that the CVT shaft 25 the on the axis C ₀ the front end portion 25F in the jig 100 is positioned a central portion by the output gear 26.

Therefore, the CVT shaft 25 is positioned at a predetermined axial position on the axis C ₀ in the casing 10, and the input / output disks 2 of the first and second toroidal transmission portions 51, 52.
Positions 0 to 21A are equally positioned to sandwich the power rollers 1L and 1R.

After positioning the CVT shaft 25 on the predetermined axis C ₀ , in step S 14, a ball is inserted into the rear ball spline 24 and the input disk 20
After the A and the CVT shaft 25 are coupled in the rotational direction, in step S15, the shim 42 is assembled so as to contact the step 25b of the CVT shaft 25, and then the disc spring 40,
41 is inserted through the outer periphery of the shim 42 and then the lock nut 43
To measure the axial gap between the inner circumferences of the disc springs 40 and 41, and select a shim 42 such that the gap is within a predetermined range. In addition, the measurement of this gap, for example,
The speed ratio, which is measured by a plastic gauge or the like previously held between the disc springs 40 and 41 and further measures the gap, is as follows:
In consideration of the bending of the input / output disk, the axial ratio of the shim 42 is set such that the gear ratio = 1 shown in FIG. Select

Thus, when no load is applied, the power roller 1L,
Shim 4 so that the preload holding the 1R becomes the specified 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.

First and second toroidal transmission sections 51, 52
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 connected to the CVT shaft 2 in step S19.
After removing the bolt (not shown) fixed to 5 and allowing the cam flange 56 to be able to rotate relatively to the CVT shaft 25, the transmission section assembling step S100 and the transmission section adjusting step S110 are terminated.

As described above, the axial distance L3 from the end face of the bracket 10A to which the gear housing ASSY 28 is attached to the rotating shaft 3z of the trunnions 3L and 3R of the first toroidal transmission 51 and the second face from the end face of the bracket 10A. The casing 10 is processed in advance so that the axial distance L4 of the trunnions 3L and 3R of the toroidal transmission unit 52 to the rotation shaft 3z is L3 = L4, and is used for assembling the first and second toroidal transmission units 51 and 52. First, in the trunnion assembly sub-assembly step S103, the gear housing ASSY is connected to the end surface 28 of the front gear housing 28A.
Assemble on the basis of E, angular contact ball bearings 59, 1
The preload adjusting shims 70 and 7 are set so that the preload 59 becomes a predetermined value.
1 and adjust the output disc 2 from the end face 28E.
The axial distance to the end face of 1, 21A is a predetermined value L1 = L2
Since the shims 72 and 73 are adjusted so that the end position of the gear housing ASSY 28 is connected to the end surface of the bracket 10A, the axial distance between each of the trunnions 3L and 3R and the end surface 28E is adjusted. L3,
L4 is set to be equal, and in the trunnion ASSY sub-assembly step S103, the output disk 2
The axial distances to the end faces of the output disks 21 and 21A are set so that L1 = L2.
And power roller 1 supported by each trunnion 3L, 3R
The positional relationship between the axes L and 1R can be set equal in the first and second toroidal transmission units 51 and 52, and the pressing force applied to the first and second toroidal transmission units 51 and 52 as in the above-described conventional example can be reduced. Unbalance occurs and the power roller 1
L, 1R can reliably prevent the torque transmission capacity and durability of the toroidal-type continuously variable transmission 50 from being reduced due to slippage, and the end surfaces 28E serving as reference positions for assembling with the output disks 21, 21A. Since the relationship is separately performed in the gear housing ASSY sub-assembly step S102, the casing 10
This eliminates the need for skilled work such as internal adjustment work, making it possible to easily and accurately position the power roller and the output disk in the axial direction. The quality assurance of the toroidal type continuously variable transmission 50 can be compatible.

FIGS. 14 and 15 show the second embodiment.
The output disks 21, 21A and the angular ball bearings 59, 15 from the gear housing ASSY 28 of the first embodiment are described.
9 is eliminated, the preload of the angular ball bearings 59 and 159 is adjusted only by the preload adjustment shims 70 and 71, and the output disks 21 and 21A from the end face of the front gear housing 28A. The axial distance up to L1 is adjusted to L1 = L2, and the other configuration is the same as that of the first embodiment.

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

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

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

First, in step S40 of FIG. 15, as shown in FIG. 3 of the first embodiment, a radial bearing 75 for supporting the gear 27a of the counter shaft is assembled to the rear gear housing 28B.

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

Next, in step S42, as shown in FIG. 4, the axial distance A1 from the end face 28E of the front gear housing 28A to the end face of the front gear housing 28A which comes into contact with the preload adjustment shim 70 is measured.

Similarly, in step S43, the preload adjusting shim 71 is moved from the end face 28F of the rear gear housing 28B joined to the end face 28E of the front gear housing 28A.
Is measured in the axial direction A2 to the end face of the rear gear housing 28B that contacts the rear gear housing 28B.

In step S44, the flange 159c protruding from the end surface of the inner ring 59a of the angular ball bearing 59 of the first toroidal transmission portion 51 attached to the output gear 26 to the angular ball bearing 159 of the second toroidal transmission portion 52. The axial distance E1 to the end surface of the second toroidal transmission portion 52 is measured in the same manner as described above.
The axial distance E2 to the end face of the flange 59c of the angular ball bearing 59 on the side of the toroidal transmission portion 51 is measured.

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

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

S ₃ = L2-D2-E2 + A1 + (K / 2) (5) S ₄ = L1-D1-E1 + A2 + (K / 2) (6) where K is a closing allowance, and Set design values L1, L2
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), errors due to the stacking of the dimensional tolerances of the respective parts are absorbed. The preload of the angular ball bearings 59, 159 is set to a predetermined value, and the axial distance from the end face 28E of the front gear housing 28A, which is the reference of the gear housing ASSY 28, to the end face of the output disks 21, 21A is:
The predetermined design value L1 is set to L2.

In step S47, step S46 is performed.
The preload adjustment shims 70, 71 selected in
159c.

In step S48, the output gear 26, to which the angular ball bearings 59, 159 and the preload adjusting shims 70, 71 are assembled, is assembled to the rear gear housing 28B, and the countershaft gear 27a
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
3 and a bolt 7 inserted into the rear gear housing 28B through a screw hole formed in the upper part 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 each other to house the output gear 26 and the gear 27a therein.

Then, in step S50, the cylindrical portion 26A
Output disks 21, 21 to splines 26B, 26B of
A and the output disk 2
Needle bearings 80 and 81 are attached to the inner periphery of the gear housing 1 and 21A via snap rings 82 and 83, and the gear housing AS
The SY sub-assembly step S102 ends.

The gear housing ASSY 28 assembled in the above steps S40 to S50 has a preload adjusting shim 70,
Only by the adjustment of 71, the angular ball bearing 59,
159 and the end surface 28E of the front gear housing 28A which is the reference position of the gear housing ASSY 28.
Can be set to a predetermined design value L1 = L2, and the positioning adjustment shim 7 can be set in addition to the effects of the first embodiment.
By omitting 2, 73, the number of parts and the step of selecting shims can be reduced, and the quality of the toroidal-type continuously variable transmission can be ensured while further improving the productivity.

Note that, in the above embodiment, the output gear 2
6 and the output disks 21 and 21A are angular ball bearings, but may be tapered roller bearings (not shown).

Further, in the above embodiment, an example was shown in which gears were used as transmission means from the output disks 21 and 21A to the counter shaft 27.
You may comprise a sprocket, a chain, etc.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of a toroidal type continuously variable transmission showing an embodiment 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 sectional view of the gear housing ASSY, showing a relationship between dimensions measured to select a thickness of a 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 assembly.

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

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

FIG. 9 is a flowchart showing an example of a gear housing ASSY sub-assembly process.

FIG. 10 is a flowchart illustrating an example of an assembling process and an adjusting process of the toroidal-type continuously variable transmission, and illustrates an assembling process.

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

FIG. 12 is a cross-sectional view of the toroidal-type continuously variable transmission, showing a state of tilting of the power roller when the speed ratio is 1;

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

FIG. 14 shows the second embodiment, and shows a gear housing ASSY.
FIG.

FIG. 15 is a flowchart showing an example of a gear housing ASSY sub-assembly 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 assembly 3z Rotary shaft 6 Hydraulic cylinder 10 Casing 10A Bracket 20, 20A Input disk 21, 21A Output disk 23 Front ball spline 24 Rear ball spline 25 CVT shaft 25b Step 25A CVT shaft ASSY 26 Output gear 26A Cylindrical part 26B Spline 27a Gear 27 Counter shaft 28 Gear housing ASSY 28A Front gear housing 28B Rear gear housing 28C Bolt 28D Through hole 28E, 28F End face 40, 41 Disc spring 42 Shim 43 Lock nut 50 Toroidal-type continuously variable transmission 51 First toroidal transmission unit 52 Second toroidal transmission unit 53 Torque converter 54 Front and rear Advance switching device 56 Cam flange 56a Claw portion 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 shim 74 Bolt 75 Radial Bearing 100 Jig 101 Arm part 102 Bolt 103 Support part

Claims (7)

[Claims] 1. A first toroidal transmission unit and a second toroidal transmission unit which are coaxially arranged on an input shaft and have a pair of input disks and output disks, respectively, and are opposed to each other with the input shaft interposed therebetween. A trunnion for rotatably and tiltably supporting a power roller held by each input / output disk, and a pressing force generating means disposed on the input shaft for generating a force for holding and pressing the power roller; A transmission means connected between output disks of the first and second toroidal transmission units and transmitting power to a drive shaft side, wherein the transmission means is arranged in an input axial direction. A sub-assembly step of previously assembling the output disks of the first and second toroidal transmission units, and assembling the transmission means in which the output disks have been previously assembled to the casing. Degree and, after assembling the pressing force generating unit and the input disc to the input shaft after insertion into the transmission means, the assembly method of the toroidal type continuously variable transmission which comprises a step of assembling the trunnion and a power roller. 2. The sub-assembly step includes an adjustment step of adjusting a distance from a predetermined reference position of the transmission means to an end surface of an output disk of each of the first and second toroidal transmission units to a predetermined value. A method for assembling the toroidal-type continuously variable transmission according to claim 1. 3. The transmission means includes a gear or sprocket connected between the pair of output disks, a housing for accommodating the gear or sprocket and being assembled to the casing, and an axial direction of the gear or sprocket. A pair of bearings provided on both sides and supported by the housing, and an axial positioning means for adjusting an axial distance from a predetermined reference position of the housing to an end face of each output disk, the adjusting step includes: 3. The method of assembling a toroidal-type continuously variable transmission according to claim 2, wherein the axial positioning means is adjusted according to the axial dimensions of the output disk and the gear or sprocket. 4. The transmission means includes a gear or sprocket connected between the pair of output disks, a housing for accommodating the gear or sprocket and being assembled to the casing, and a gear or sprocket in an axial direction of the gear or sprocket. A pair of bearings disposed on both sides and supported by the housing, and axial positioning means for adjusting both an axial distance from a predetermined reference position of the housing to an end surface of each output disk and a preload applied to the bearing. 3. The toroidal mold according to claim 2, wherein in the adjusting step, the axial distance and the preload are simultaneously adjusted by an axial positioning means in accordance with an axial dimension of the output disk and the gear or the sprocket. 3. How to assemble a step transmission. 5. The assembling method of the toroidal type continuously variable transmission according to claim 3, wherein the predetermined reference position of the housing is a surface on which the housing is assembled to the casing. 6. The bearing couples an outer ring to a housing while coupling an inner ring to a cylindrical portion of a gear fitted with an output disk, wherein the axial positioning means is interposed between the inner ring and the output disk. 4. The method according to claim 3, wherein the adjusting step adjusts an axial dimension of the axial positioning means. 7. The bearing couples an outer ring to a housing, and couples an inner ring to a cylindrical portion of a gear fitted with an output disk, and the axial positioning means is interposed between the outer ring and the housing. The assembling method of the toroidal-type continuously variable transmission according to claim 4, wherein the adjusting step adjusts an axial dimension of the axial positioning means.