JP3414220B2 - 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 for assembling a toroidal type continuously variable transmission used in a vehicle or the like.

[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 gear ratio is changed steplessly to transmit the driving force from the input shaft to the output shaft (or output gear).

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.

As shown in FIG. 21, the torque converter 53 is equipped with a lockup clutch on the input side of the toroidal type continuously variable transmission 50 and is connected 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 1R and 1L 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 1R and 1L sandwiched between and, and these power rollers 1R and 1L are tiltably and rotatably supported by trunnions (not shown). The tilting movements of the power rollers 1R and 1L are rotational movements that change 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 1R and 1L are tilted in accordance with this displacement to change the gear ratio.

In the power transmission of the toroidal type continuously variable transmission 50, the power rollers 1R and 1L arranged between the input and output disks are sandwiched with a pressing force of several tons, and the power rollers 1R and 1L are connected. 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
R and 1L transmit power without slipping between the input and output 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 connected in a rotational direction via a line 24, the line 24 is supported so as to be displaceable in a predetermined range in the axial direction. On the other hand, the output discs 21 of the first and second toroidal transmission units 51 and 52,
21A is disposed in the middle of the CVT shaft 25 so as to be relatively rotatable, and the output discs 21 and 21A are coaxially coupled to each other via an output gear 26 disposed between the rear surfaces thereof, and the output gear 26 and the output disc 21 are also coupled to each other. , 21A are rotatably supported on the casing 10 side via angular ball bearings 59, 59 provided between the output gear 26 and the output gear 26.
Also, the output disks 21 and 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 1R and 1L 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 for holding the power rollers 1R, 1L by the input / output disks 20-21A is determined, and the toroidal type stepless. 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 1R when no load is applied,
Holding 1L enables 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 1R and 1L. 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 units 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.

[0014]

However, in the method of assembling the toroidal type continuously variable transmission as described above, slippage between the power roller and the input / output disk is prevented, and power transmission is surely performed under no load. , The preload applied by the disc spring 40 needs to be set within a predetermined range.
When the cam flange 56, the first and second toroidal transmission parts 51 and 52, and the disc spring 40 are sequentially assembled to the shaft 25, the axial dimension from the cam flange 56 to the rear surface of the output disc 21A varies due to stacking of dimensional tolerances. Therefore, the preload generated by the disc spring 40 also fluctuates, and the pressing force applied to the power roller changes, which may lead to a decrease in torque transmission capacity and slippage of the power roller, resulting in deterioration in quality. Further, since the toroidal type continuously variable transmission has a large number of parts and has a complicated structure, it is difficult to constantly adjust the preload applied by the disc spring 40 to a predetermined range.

Therefore, the present invention has been made in view of the above problems, and easily and accurately adjusts the preload of a disc spring that changes due to stacking of dimensional tolerances and the like, thereby improving the quality of a toroidal type continuously variable transmission. The purpose is to maintain.

[0016]

[0017]

[0018]

A first aspect of the present invention is directed to an input shaft.
Input and output discs coaxially arranged in the
And is arranged to face each other across the input shaft, and
Freely rotate the power roller sandwiched between the input and output disks
And the trunnion that supports tilting and the input shaft
Is installed and the power roller
There is no pressing force generating means for generating a holding pressure and the input shaft.
Generates a preload that holds the power roller under load
In addition, the holding pressure generated by the pressing force generation means is supported.
Preload generating means to have and the preload generating means
Preload adjusting means for adjusting the preload disposed in the
Connected to the output disc to transmit power to the drive shaft side.
Set of toroidal type continuously variable transmission with reaching means
In the standing method, the pressing force generating means and the input disk
Pre-assemble to the input shaft and output to the transmission means
The step of assembling the transmission means for assembling the disc in advance, and the transmission
Assembling the moving means to the casing,
Insert it into the casing and connect it to the transmission means.
The temporary assembly process for assembling the lanion and power roller
After assembling the preload generation means after the temporary assembly process of
The preload generating means is activated by the preload adjusting means.
Adjust the generated preload so that it falls within the specified range.
In the adjusting step , the gear ratio is adjusted so that the preload is in a predetermined range at least in the direct connection state and the high side and the low side.

[0019]

[0020]

[0021]

[0022]

[0023]

The second aspect of the present invention is coaxial with the input shaft.
Input and output disks arranged, and the input
These are placed opposite to each other with the shaft in between and these input / output di
Power roller held between discs can be rotated and tilted freely
And a trunnion supported on the input shaft
In addition, the holding pressure of the power roller is generated according to the input torque.
When the input shaft has no load,
With the preload that holds the power roller
In addition, a pre-support for supporting the holding pressure generated by the pressing force generating means.
The load generating means and the preload generating means are provided.
Preload adjusting means for adjusting the preload by
Transmission that is connected to the force disc and transmits power to the drive shaft side
And a method of assembling a toroidal type continuously variable transmission including
In advance, the pressing force generating means and the input disk are input in advance.
The process of assembling to the shaft and the output disc to the transmission means
Assembling the transmission means to be assembled in advance, and the transmission means
Mounted on the housing, and the input shaft is
The trunnion and the transmission means.
And the temporary assembly process of assembling the power roller and this temporary assembly process
After installing the preload generation means,
The preload generated by the preload generation means
The adjustment process to adjust the load to fall within the specified range
In addition, the input shaft has two sets of input discs and output discs, and the input discs are arranged at both ends of the input shaft, respectively, while the pair of output discs sandwiches a transmission means at the center of the input shaft. Respectively, and the pressing force generating means is disposed at one end of the input shaft, while the preload generating means is disposed at the other end. In the adjusting step, the input shaft on the side of the pressing force generating means is casing. Then, the preload generating means is assembled, and then the preload is adjusted.

In a third aspect based on the second aspect , the preload generating means is a single or a plurality of means interposed between the back surface of the input disk and the fastening means fastened to the input shaft. The preload adjusting means is formed of a disc spring and forms a gap between the fastening means and the back surface of the input disk, and is also a tubular member inserted between the inner periphery of the disc spring and the outer periphery of the input shaft. It

In a fourth aspect based on the third aspect , the adjusting step measures the gap between the fastening means and the input disc or the plurality of disc springs with the fastening means fastened, The axial dimension of the tubular member is selected so that the preload generated by the preload generating means falls within a predetermined range.

Further, in a fifth aspect based on the fourth aspect , the gap measurement performed in the adjusting step is interposed between the input disk and the fastening means or a plurality of disc springs, and is pressed by a holding force. This is done with a deforming gauge.

[0028] In a sixth aspect based on the fifth aspect , in the adjusting step, the fastening means once fastened is removed, the thickness of the gauge is measured as the gap, and the axis corresponding to the measurement result is measured. Reassemble preload adjusting means with directional dimensions.

[0029]

[0030]

EFFECTS OF THE INVENTION Accordingly, a first aspect of the present invention, a toroidal type continuously variable transmission in addition to the number of components, needs to be adjusted accurately set the preload input and output disks sandwiching presses the power roller However, the pressing force generating means, the input disk and the input shaft, the transmission means and the output disk are respectively preassembled, and then the transmission means is assembled to the casing, and then the input shaft is inserted into the casing and connected to the transmission means. With the trunnion and power roller assembled, in the pre-assembled state, the preload generation means is assembled, and then the preload is adjusted by the preload adjustment means.
While easily assembling a toroidal type continuously variable transmission with a large number of parts, the dimensional tolerance of each part assembled sequentially from the pressing force generating means to the input disk, power roller, output disk, transmission means and input shaft direction It is possible to set the preload applied to the power roller by the input / output disk to a constant range at all times by using the preload generation means that is installed in the preload generation means, preventing variations in preload due to stacking of dimensional tolerances, and easy quality. Can be secured.

In the adjusting step, the gear ratio is adjusted so that the preload is in a predetermined range at least in the direct connection state and the high side and the low side, so that the tilt angle of the power roller, that is, the gear ratio is adjusted. It is possible to always set the preload of the toroidal type continuously variable transmission in which the preload is changed within a certain range, and it is possible to accurately ensure quality.

[0032]

[0033]

[0034]

[0035]

[0036]

The second invention is a so-called, in which a pair of input disks are arranged at both ends of the input shaft, and a pair of output disks are arranged at the center of the input shaft with a transmission means interposed therebetween.
In the double-cavity toroidal type continuously variable transmission, the pressing force generating means is arranged at one end of the input shaft, and the preload generating means is arranged at the other end. By fixing and positioning and then assembling the preload generating means, the preload generating means can be operated similarly to the completed state, and the preload can be adjusted accurately.

According to a third aspect of the invention, the preload generating means is composed of a single or a plurality of disc springs interposed between the back surface of the input disk and the fastening means fastened to the input shaft, and the preload is further provided. The adjusting means forms a gap between the fastening means and the back surface of the input disk, and is composed of a tubular member inserted between the inner circumference of the disc spring and the outer circumference of the input shaft. The preload can be easily changed by changing the dimensions.

According to a fourth aspect of the invention, in the adjusting step, the clearance between the fastening means and the input disk or the clearance between the plurality of disc springs is measured in a state where the fastening means is fastened, and the preload is determined from the measurement result. By selecting the axial dimension of the tubular member within the range, the preload can be set accurately in the same state as the completed state.

Further, the fifth aspect of the present invention interposes a gauge (for example, a plastic gauge) which is deformed by holding pressure between the input disk and the fastening means or a plurality of disc springs, so that the clearance can be easily and accurately measured. Can be done.

According to the sixth aspect of the invention, the fastening means once fastened is removed, the thickness of the gauge is measured as a gap, and then the preload adjusting means having an axial dimension according to the measurement result is reassembled. Therefore, the preload can be set accurately in the same state as the completed state without requiring skill.

[0042]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of the present invention will be described below with reference to the accompanying drawings.

1 to 20 are similar to the above-mentioned conventional example.
An example in which the present invention is applied to the assembly of a double-cavity toroidal type continuously variable transmission composed of a pair of input / output disks 20, 21 and 20A, 21A is shown. The duplicate description is 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 attached to a casing 10. The counter shaft 27 and the input shaft 55 shown in FIG. 21 are not mounted, and in FIG.
The T-shaft 25 engages with the input shaft 55 in the rotational direction on the left end 25F side in the figure, while the right end 25R in the figure is engaged.
The side is the drive shaft side. Here, the end 25F side is the front end and the end 25R side is the rear end.

In FIGS. 1 and 2, the first toroidal transmission unit 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 outer peripheries of cylindrical parts 26A, 26A projecting axially from an output gear 26 provided in the middle of both. Are respectively fitted and coupled together.

A gear 27 meshing 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. In addition, in the present embodiment, the counter shaft 27 serves as the second toroidal transmission unit 5.
The counter shaft 27, which is arranged below the gear 2 and is housed in the gear housings 28A and 28B, has a structure in which the counter shaft 27 can be attached and detached via a spline or the like. , 21A are gear housing assemblies (ASSY) 28 as transmission means, which will be described later, and are preassembled as described later.

Output disk 21 and output disk 21A
Through the angular ball bearings 59, 59 provided between the rear surfaces of both of them and the output gear 26.
The output disks 21, 21A and the output gear 26 are rotatably supported on the casing 10 side by being rotatably supported by A and 28B, and the gear housing 28A being fastened to the casing 10 via bolts 28C.

As shown in FIG. 9, the gear housing assembly 2
8 is preassembled in the gear housing ASSY sub-assembly step S102 and then sent to the transmission section assembly step S100. As shown in FIG. 7, the bolt 74 is fastened to connect the gear housings 28A and 28B, Output gear 26
After the gear housing ASSY 28 accommodating the gear 27a and the gear 27a has been assembled in advance, the gear shifting portion assembling step S10 of FIG.
At 0, the casing 10 is assembled as described later.

This assembled gear housing ASSY2
In FIG. 7, reference numeral 8 denotes the output disc 2 from the axial centerline of the gear housing ASSY 28 (for example, the end face of 28A).
The annular shims 72, 73 are interposed between the inner ring of the angular ball bearing 59 and the rear surface of the output disc 21, 21A so that the distances L1, L2 to the end faces of the angular ball bearing 59, 21 are equal. The annular shims 70, 71 between the outer ring of the gear and the gear housings 28A, 28B.
7, the thickness of these shims 70 to 73 (gap adjusting means) is adjusted to the axial distance L from the center line of the gear housing ASSY 28 to the output discs 21 and 21A as shown in FIG.
Adjust so that 1 and L2 are equal.

Gear housing AS so that L1 = L2
By assembling SY28 in advance, the intervals between the input and output disks of the first and second toroidal speed change parts 51 and 52 become equal, the pressing force applied in the axial direction is evenly distributed, and the first and second toroidal speed changes are performed. The torque transmission capacities of the parts 51 and 52 can be set equal.

Here, the axial distance L1 from the center line of the gear housing ASSY 28 to the output disks 21, 21A,
When L2 is not equal, as shown by the broken line in FIG. 16, the gap δ of the disc spring described later cannot be set within a predetermined range, and the imbalance of the pressing force causes the power rollers 1L, 1R to slide. If this occurs, the durability and torque transmission capacity of the toroidal type continuously variable transmission 50 will be reduced.

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 1R and 1L sandwiched between the input / output disks 20A and 21A are provided with pivot shafts 2 and 2 provided on the trunnions 3L and 3R arranged opposite 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 coupled 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.

As shown in FIG. 9, in the trunnion 3L, 3R, in the trunnion assembly subassembly step S103, as shown in FIG. 8, the rod 6b is coupled to the rotating shaft portion 3b at the lower end of the trunnion 3L, 3R, and the pivot 6b is pivoted. The shaft 2 is assembled to the offset portion 3c. Further, the pivot shaft 2 has a ball bearing 1 for supporting thrust force.
6 and the outer ring 18 and the needle bearings 19 for positioning in the radial direction are inserted, and then the power rollers 1L and 1R are respectively attached to the trunnion sub.
ASSY3LA and 3RA are assembled in advance, and in the transmission section assembling step S100 of FIG. 9, the trunnion sub-ASSY3LA and 3RA are assembled to the casing 10 as described later. The trunnion sub-ASSY3LA is an assembly of the trunnion 3L.
Is an assembly of the trunnion 3R.

On the other hand, the upper and lower rotary shaft portions 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, 3b of the trunnions 3L, 3R and the through holes 4L, 4R, 5L, 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 through 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 periphery of the casing 10. The positioning member 11 is engaged with the knock pin 9 fixed in advance on the casing 10 on the upper surface contacting the inner periphery 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 side of the rotary shaft C ₀ has the convex portion 1 fitted to the inner circumference of the upper link support 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 freely swingingly supporting the lower link 5 is fixed to the cylinder body 60 which faces the upper link support member 12 with the rotation axis 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 supporting 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 figure, and these stud bolts 33, 33 are mounted on the pedestal 60A. And through the through hole 60D provided in the cylinder body bottom 61,
Cylinder body 60 bottom surface or cylinder body bottom 61
The lower link support member 30 is fastened to the pedestal 60A by screwing the nut 33a into the end portion projecting from the lower surface of the lower link support member 30.

The inner diameter of the through hole 60D is set larger than the outer diameter of the stud bolt 33, so that the position adjustment of the lower link support member 30 described later in the X-axis direction 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 member.
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 pulleys 35 are also fitted to the rotating 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-assembling step S101 shown in FIG. 9, the cam flange 56 is attached to the end 25F side via the ball bearing 58 as shown in FIG. 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, as shown in FIGS. 5 and 6, the cam flange 56 and the first toroidal transmission unit 51 are provided with a through hole in the cam flange 56 at a predetermined position on the rear surface of the input disk 20, for example, a predetermined diameter. In the CVT shaft ASSY sub-assembly step S101 shown in FIG. 9, screw holes 20c are formed in the back surface of the input disk 20, respectively, and the bolt 91 is inserted from the end 25F side into the through holes 90, 90. It is fastened to the screw hole 20c and the relative rotation of the CVT shaft 25 and the cam flange 56 is prohibited, and the CVT shaft ASSY 25A is sent to the gear shifting section assembling step S100 in FIG.

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

On the other hand, on the rear end 25R of the CVT shaft 25, as shown in FIG. 3, the rear surface of the input disk 20A constituting the second toroidal speed change portion 52 is axially (forwardly) pressed by a predetermined urging force. Then, annular disc springs 40, 41 (preload generating means) for providing a preload for holding the power rollers 1R, 1L by the input / output disk are provided.

The disc springs 40 and 41 are mounted between the inner periphery of the disc springs 40 and 41 and the CVT shaft 25 via a cylindrical shim 42 as a preload adjusting means, and the disc springs 40 and 41 are connected to the rear end portion 25R from the C side.
The lock nut 43 screwed onto the VT shaft 25 has a shim 4
2 to the position where it abuts the stepped portion 25b, and the disc spring 4
0 and 41 are configured to give a predetermined preload.

Here, the CVT shaft 25 on the rear end portion 25R side is formed with a rear ball spline 24 for connecting the input disk 20A in the rotational direction, and a step portion is formed from the end of the rear ball spline 24 on the end portion 25R side. The outer diameter is reduced via 25b, and a screw portion 25c is formed from this step portion 25b toward the end portion 25R. The outer diameter of the end portion 25R from the end of the screw portion 25c 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. At this time, the peripheral edge portions of the disc springs 40 and 41 are brought into contact with each other so that the disc springs 40 and 41 form a gap in the axial direction on the inner peripheral side, while the inner peripheral side of the disc spring 41 is input to the input disc 20A. Abut the back of the.

In this state, the lock nut 43 screwed into the screw portion 25c is fastened, and the flange portion 43A is used to form the step portion 25.
While holding the shim 42 between b and the disc spring 40,
41 is compressed to urge the input disk 20A toward the other end.

In this state, the length L of the shim 42 is adjusted as described below so that the gap δ formed by the disc springs 40, 41 in the axial direction on the inner peripheral side falls within a predetermined range. The preload generated by the springs 40 and 41 can always be set within a predetermined range.

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
At 101, as shown in FIGS. 4 to 6, the cam flange 56, the cam roller 57, and the first toroidal transmission unit 5 are provided.
Assemble the input disk 20 of No. 1 and bolt 9
1 is fastened and the cam flange 57 is fixed to the input disc 20 at a position where the cam roller 57 is in an unloaded state, and the operation of the cam roller 57 is prohibited.
Assemble as SY25A.

Gear housing assembly subassembly step S102
Then, as shown in FIG. 7, the gear housings 28A, 28A
After assembling the output gear 26 and the gear 27a on the inner circumference of B, the bolt 74 is fastened to assemble the gear housing ASSY 28.

Then, the trunnion assembly sub-assembling step S1
In 03, as shown in FIG. 8, the rod 6b is coupled to the rotating 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 2 further includes the ball bearing 16 and the outer ring 18. After inserting the needle bearing 19 and the power roller 1L and 1R, the trunnion sub
Assemble as ASSY3LA and 3RA in advance.

Next, in the speed change portion assembling step S100, the preassembled CVT shaft ASSY 25A, gear housing ASSY 28 and four trunnion sub ASSY 3LA, 3
As will be described later, the RA is assembled to the casing 10 together with other components, and the RA springs 40, 4 are attached to the CVT shaft 25.
When 1 is assembled by the lock nut 43, the shim 42 having the length L corresponding to the dimensional tolerance of each component is adjusted so that the clearance δ of the inner circumferences of the disc springs 40 and 41 is within a predetermined range in the transmission section adjusting step S110. Select and assemble.

In this way, after assembling the first and second toroidal speed change parts 51 and 52 mainly composed of the CVT shaft 25 inside the casing 10, in the torque converter and forward / reverse switching device assembling step S120, the same as in the prior art example. The input shaft 5 that engages with the CVT shaft 25 in the rotational direction.
5, the forward / reverse switching device 54, and the torque converter 53 are sequentially assembled from the front of the casing 10, the assembly process is completed, and the process is sent to the completion inspection process S130.

Here, an example of the gear shifting portion assembling step S100 and the gear shifting portion adjusting step S110 will be described in detail with reference to the flowcharts of FIGS.

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. At the time when the assembling of the first and second toroidal speed change portions 51 and 52 is almost completed. Then, the adjustment for adjusting the preload of the disc springs 40 and 41 is performed.

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.

[0095] 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).

In step S4, the gear housing ASSY 28 preassembled as shown in FIG. 7 is inserted through the bolt 28C from the gear housing 28A side as shown in FIG.
Is fastened to the casing 10.

Then, in step S5, the input disk 20A is temporarily placed on the inner periphery of the casing 10 facing the output disk 21A of the second toroidal speed changer 52, and in step S6, it is preassembled as shown in FIGS. The C
After inserting the VT shaft 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, further, the CVT shaft. 25 is inserted and the rear end portion 25R is inserted into 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-ASSYs 3LA and 3RA which are preassembled as shown in FIG. 8 are assembled to the casing 10. The power rollers 1L, 1R supported by the pivot shaft 2 are sandwiched by the input / output disks 20, 21, 20A, 21A, respectively, while inserting the upper ends of the rotating shafts 3a of the trunnions 3L, 3R into the upper links 4. Assemble. When inserting the rotating shaft portions 3a of the trunnions 3L and 3R into the upper links 4, the rotating shaft portions 3a and the through holes 4L and 4R of the upper links 4 are inserted.
A spherical bearing 7 and a needle bearing 8 are provided between the two.

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 part 3b and the rod part 6b, which are the lower parts 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 is synchronized.
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 angles 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 to be inserted into the inner circumference of the cylinder body 60, and in step S12, each trunnion 3 is inserted.
Insert the cylinder body 61, which forms the bottom of the cylinder body 60, into the rod portions 6b of L and 3R, and as shown in FIG.
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.
The piston 6a, the pulley 35, etc. are fixed.

Thus, with the CVT shaft ASSY 25A temporarily assembled, the gear housing ASSY 28, the trunnion sub-ASSYs 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, which is supported by the gear housing ASSY 28 and only has 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.

With the CVT shaft 25 positioned on the predetermined axis C ₀ , in step S14, a ball is inserted into the rear ball spline 24 to couple the input disc 20A and the CVT shaft 25 in the rotational direction, and then, In step S15, as shown in FIG.
2 is attached so as to contact the step portion 25b of the CVT shaft 25. At this time, the shim 42 to be assembled (the length in the direction of the axis C ₀ ) has a reference value L ₀ set in advance.

Next, in step S16, FIG.
And, as shown in (B), a plurality of plastic gauges 110 are arranged at predetermined positions (for example, radially) between the disc springs 40 and 41, and then the plastic gauges 110 are held while being held in step S17. After the disc springs 40 and 41 are assembled to the outer periphery of the shim 42, the lock nut 43 is temporarily tightened in step S18, and the disc springs 40 and 41 are compressed between the flange portion 43A of the lock nut 43 and the back surface of the input disc 20A. And generate a preload.

Then, the jig 100 is removed in step S19, and then the CVT shaft 25 is removed in step S20.
Is rotated in the forward and reverse directions, respectively. This CVT
The rotation of the shaft 25 is performed by, for example, an operator, and the loading cam 56 is fixed to the unloaded state by the bolt 91 as shown in FIG.
Even if the T-shaft 25 is rotated, the input disks 20, 20
A is the power roller 1 via the output disks 21, 21A
The force pressing L and 1R is only the preload of the disc springs 40 and 41.

At this assembly stage, the trunnion 3L,
Since the hydraulic pressure is not acting on the hydraulic cylinder 6 of 3R, the trunnions 3L and 3R can be displaced in the axial direction.
When the shaft 25 is rotated normally and reversely, the trunnion 3
Since L and 3R are displaced in the axial direction according to the rotation direction of the CVT shaft, the power rollers 1L and 1R are tilted until they hit a stopper (not shown) and tilted from the highest Hi gear ratio to the lowest Lo gear ratio. The rolling surfaces of the discs 20 to 21A and the power rollers 1L and 1R can be made to fit within the entire shift range.

In this way, the CVT shaft 25 is rotated in the forward and reverse directions to conform the rolling surfaces of the input / output disk and the power roller, and in step S21, as shown in FIG. 18, the gear ratio is 1, that is, the CVT. The shaft 25 and the output gear 26 are set so as to be directly connected to each other. The gear ratio is set by manually rotating the trunnions 3L and 3R.

Next, in step S22, the jig 100 is attached again to fix the front end portion 25F of the CVT shaft 25 to the casing 10 side, and in step S23,
The lock nut 43 is fastened with a predetermined torque. By fastening the lock nut 43 with a predetermined torque, the preload generated by the disc springs 40 and 41 becomes the same value as in the completed state, and at this time, the thickness of the plastic gauge 110 sandwiched between the disc springs 40 and 41 is increased. The maximum value is the Belleville spring 4
The value is equal to the inner peripheral clearance δ of 0 and 41.

After the lock nut 43 is fastened with a predetermined torque, the lock nut 43 is removed in steps S24 and S25, and then the disc springs 40 and 41 are removed.
At 26, the maximum thickness of the plastic gauge 110 compressed according to the gap δ equal to the completed state is measured, and this thickness is measured as the gap δ between the disc springs 40 and 41 when the gear ratio = 1.
_Let it be _C.

Then, in step S27, the measured gap δ _C is, as shown in FIG.
It is determined whether or not it is within δ1, and if it is within the setting range,
On the other hand, when the process goes to step S29 of 2 and is outside the setting range,
In step S28, after the shim 42 having the length L so that the clearance δ _C is within the set range is replaced, the step S1 is performed again.
Returning to step 5, the gap δ is measured again.

In step S42, a large number of shims 42 having different lengths L at a predetermined pitch are prepared, and the measured gap δ _C is set between the maximum value δ1 and the minimum value δ0 of the set range. Select the one that is closest to the dimension L,
Assemble in step S15.

On the other hand, if the gap δ _C when the gear ratio is 1 is within the set range, the process proceeds to steps S29 to S41 of FIG. 12, and similarly to steps S15 to S27, the disc when the gear ratio is Lo is set. The gap δ _L between the springs 40 and 41 is measured, and in step S41 it is determined whether this gap δ _L is within the set range.

Here, when the gear ratio is Lo, the power rollers 1R and 1L are tilted as shown in FIG. 19, and the power rollers 1R and 1L are in contact with each other on the inner peripheral side of the input disks 20 and 20A. , And the output discs 21 and 21A are in contact with each other on the outer peripheral side, the deflection of the input and output discs due to the preload of the disc springs 40 and 41 has a rigidity lower than that of the output discs 21 and 21A. While the amount of bending increases on the outer peripheral side of the input disk 20, 2 with high rigidity
The amount of bending on the inner peripheral side of 0A is reduced.

Therefore, the gap δ when the gear ratio = Lo
_L is increased by the increase in the deflection on the output disk side, as shown in FIG.
As shown in FIG. 6, it is larger than the clearance δ _C when the gear ratio = 1.

Therefore, in FIG. 16, even when the gap δ _C when the gear ratio = 1 is in the set range as in the case where the length L of the shim 42 is small, the gap δ _L when the gear ratio = Lo is set. May exceed the setting range δ0 to δ1,
When it exceeds, the routine proceeds to step S42, where the gear ratio = Lo
After replacing with the shim 42 having the length L such that the clearance δ _{L at} the time of and the clearance δ _{C at} the speed ratio = 1 are within the setting range,
Returning again to step S15, the gap δ _C when the gear ratio = 1 and the gap δ _L when the gear ratio = Lo are measured again. The measured gear ratio on the Lo side is a preset value or a maximum gear ratio that can be set.

On the other hand, if the gap δ _C when the gear ratio = 1 and the gap δ _L when the gear ratio = Lo are within the set range, steps S43 to S55 of FIG. 13 and steps S29 to S29 of FIG. Similarly to S41, the gap δH between the disc springs 40 and 41 when the gear ratio is Hi is measured, and the step S5
At 5 , it is determined whether this gap δ _H is within the set range.

Here, when the gear ratio is Hi, the power rollers 1R and 1L are tilted as shown in FIG. 20, and the power rollers 1R and 1L are in contact with the outer peripheral side of the input disks 20 and 20A. Since the output discs 21 and 21A come into contact with each other on the inner peripheral side, the deflection of the input / output discs due to the preload of the disc springs 40 and 41 has a lower rigidity than the input discs 20 and 20A when the gear ratio = 1. While the amount of bending increases on the outer peripheral side of the output discs 21, 2 with high rigidity
The amount of bending on the inner peripheral side of 1A is reduced.

Therefore, as in the case of the gear ratio = Lo, the gap δH when the gear ratio = Hi is equal to the gap when the gear ratio = 1 as shown in FIG. It is larger than δ _C.

Therefore, the gap δ when the gear ratio = Hi
_{If H} exceeds the setting range δ0 to δ1, the process proceeds to step S56, and the gap δ _L when the gear ratio = Lo, the gap δ _C when the gear ratio = 1, and the gap when the gear ratio = Hi. A shim 42 having a length L such that δ _H is within the setting range
After the replacement, the process returns to step S15 and the gap δ _C when the gear ratio = 1, the gap δ _L when the gear ratio = Lo, and the gap δ _H when the gear ratio = Hi are measured again. The measured gear ratio on the Hi side is a preset value or a settable minimum gear ratio.

If the gap δ _H when the gear ratio = Hi is within the set range in step S55, all the gaps δ _C , δ _L and δ _{H of} each gear ratio are set as shown by the solid line in FIG. This means that the shim 42 within the range is selected, and the assembling of the shim 42 is performed after step S57 in FIG. 14 to complete the assembly of the first and second toroidal transmission units 51 and 52.

That is, in step S57, as shown in FIG. 3, the selected shim 42 is assembled so as to abut the step portion 25b of the CVT shaft 25, and then step S57.
At 58, the peripheral edges of the disc spring 40 and the disc spring 41 are aligned and assembled to the outer periphery of the shim 42, and then at step S59, the lock nut 43 is fastened with a predetermined torque.

Then, in step S60, the jig 100 is removed, and then in step S61, the bolts 91 that have fixed the cam flange 56 to the CVT shaft 25 are removed, and the cam flange 56 is moved relative to the CVT shaft 25. The assembly is completed by making it rotatable.

As described above, the gear ratio is directly connected to Lo, Hi,
The gap δ between the coned disc springs 40 and 41 is measured with the plastic gauge 110, and the length L of the shim 42 is selected so that the gap δ is within a predetermined range at each gear ratio. When assembling the toroidal type continuously variable transmission 50 in which the fluctuation of the preload is surely absorbed and the preload of the disc springs 40 and 41 changes according to the gear ratio,
The disc springs 40 and 41 are the first and second toroidal speed change parts 5.
It is possible to always set the preload applied to Nos. 1 and 52 within a certain range, prevent variations in preload due to stacking of dimensional tolerances, and ensure quality. Further, the gap δ is measured by plastic. Gauge 11
Since it is sufficient to crush 0 with compressed disc springs 40 and 41 and measure the maximum value of its thickness, it requires special skill to assemble a toroidal type continuously variable transmission that has many parts and is difficult to adjust. It can be done easily and can improve productivity and quality.

In the above embodiment, the case where a plurality of disc springs for providing a preload are formed is shown. However, as shown in FIG. 21 of the conventional example, a single disc spring 40 is directly attached to the rear surface of the input disk 20A. In the configuration of pressing, the gap δ is measured by sandwiching the plastic gauge 110 between the back side of the disc spring 40 and the input disc 20A, and the gap δ between the disc spring 40 and the input disc 20A falls within a predetermined range. Should be selected.

Further, in the above-mentioned embodiment, an example in which a gear is used as the transmission means has been shown, but although not shown, it may be constituted by a sprocket and a chain or the like.

Further, in the above embodiment, when assembling the CVT shaft ASSY 25A, the relative rotation of the cam flange 56 with respect to the CVT shaft 25 is prohibited by the bolt 91 inserted through the cam flange 56 and fastened to the input disk 20. The cam flange 56 may be temporarily coupled to the input shaft front end portion 25 side to prohibit relative rotation, or the rotation of the cam roller 57 may be prohibited to prohibit relative rotation.

In the above embodiment, the case of assembling the double-cavity toroidal type continuously variable transmission has been described, but although not shown, the single-cavity toroidal type continuously variable transmission including a pair of input / output disks and power rollers. The present invention can be applied to the case of assembling.

[Brief description of 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 half cross-sectional view of a disc spring, a shim, a lock nut and an input disc, also showing the rear end portion of the CVT shaft.

FIG. 4 is a sectional view of a CVT shaft ASSY.

FIG. 5 is a front view of a cam flange that also constitutes the CVT shaft ASSY.

FIG. 6 also shows the front end portion of the CVT shaft ASSY, and is a half cross-sectional view taken along the line BB of FIG. 5, showing the relationship between the cam flange and the bolt that prohibits relative rotation of the CVT shaft.

FIG. 7 is a sectional view of the gear housing ASSY.

FIG. 8 is a sectional view of a trunnion sub-ASSY.

FIG. 9 is a process drawing showing the outline of the assembly of a toroidal type continuously variable transmission.

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 flow chart showing an example of an assembling process and an adjusting process of a transmission unit that also constitutes the toroidal type continuously variable transmission, and shows an adjusting process of a gear ratio = 1.

FIG. 12 is a flow chart showing an example of an assembling process and an adjusting process of a transmission unit that also constitutes the toroidal type continuously variable transmission, and shows an adjusting process of the gear ratio = Lo.

FIG. 13 is a flow chart showing an example of an assembling process and an adjusting process of a transmission unit that also constitutes the toroidal type continuously variable transmission, and shows an adjusting process of a gear ratio = Hi.

FIG. 14 is a flow chart showing an example of an assembling process and an adjusting process of the speed change portion which also constitutes the toroidal type continuously variable transmission, and shows a final assembling process.

15A and 15B show an arrangement of a plastic gauge for measuring a gap between disc springs, FIG. 15A being a perspective view and FIG. 15B being a front view.

FIG. 16 is a graph showing a relationship between a gap δ between disc springs and a gear ratio.

FIG. 17 is a sectional view of a toroidal type continuously variable transmission showing a relationship between a CVT shaft, a casing, and a jig.

FIG. 18 is a cross-sectional view of the toroidal-type continuously variable transmission showing how the power roller tilts when the gear ratio = 1.

FIG. 19 is a cross-sectional view of a toroidal-type continuously variable transmission showing how the power roller tilts when a gear ratio = Lo.

FIG. 20 is a cross-sectional view of a toroidal type continuously variable transmission showing a state of tilting of a power roller when a gear ratio = Hi.

FIG. 21 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 4 upper links 5 Lower Link 6 hydraulic cylinder 10 casing 11 Positioning member 11a convex part 12 Upper link support member 16 ball bearing 19 needle bearing 20, 20A input disk 21, 21A output disc 23 Front Ball Spline 24 Rear Ball Spline 25 CVT shaft 25b step 25c screw part 25A CVT shaft assembly 26 output gears 26A tube 27a gear 28 Gear housing assembly 28A, 28B gear housing 28C bolt 30 Lower link support member 35 pulley 36 wires 37 pulley groove 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 55 1st input shaft 55A flange 56 cam flange 57 Cam roller 58 ball bearing 59 Angular Ball Bearing 60, 61 cylinder body 70-73 shims 74 volts 90 through holes 91 volt 100 jigs 101 Arm 102 volts 103 support 110 plastic gauge

─────────────────────────────────────────────────── --Continued from the front page (56) Reference JP-A-1-229158 (JP, A) JP-A-4-69439 (JP, A) JP-A-5-39834 (JP, A) JP-A-7- 158712 (JP, A) (58) Fields investigated (Int.Cl. ⁷ , DB name) F16H 15/38 B23P 21/00 303

Claims (6)

(57) [Claims] 1. An input disc and an output disc coaxially arranged on an input shaft, and a power roller sandwiched between the input shaft and the input disc sandwiched between the input and output discs. A trunnion that rotatably supports, a pressing force generation unit that is disposed on the input shaft and that generates a holding pressure of the power roller according to an input torque, and a power roller when the input shaft is unloaded. Preload generating means for generating a holding preload and supporting the holding pressure generated by the pressing force generating means, preload adjusting means arranged in the preload generating means for adjusting the preload, and connected to the output disk is the method of assembling the toroidal-type continuously variable transmission that includes a transmission means for transmitting power to the drive shaft side, the pressing force generating means and input data Set in advance the input shaft of the disk
And a transmission means for preliminarily assembling the output disk to the transmission means.
Assembling process, assembling the transmission means to the casing, and
Insert the input shaft into the casing and connect it to the transmission means,
Temporary assembly process for assembling the trunnion and power roller
And, after this temporary assembly process, attach the preload generation means,
By the preload adjusting means, the preload generating means
Adjust the generated preload so that it falls within the specified range.
The adjustment process includes the adjustment process.
Both are directly connected and the preload is on the high side and the low side.
Toro characterized by adjusting to a predetermined range
Assembly method for idal type continuously variable transmission. 2. An input disc and an output disc coaxially arranged on an input shaft, and a power roller sandwiched between the input and output discs and opposed to each other with the input shaft sandwiched therebetween. A trunnion that rotatably supports, a pressing force generation unit that is disposed on the input shaft and that generates a holding pressure of the power roller according to an input torque, and a power roller when the input shaft is unloaded. Preload generating means for generating a holding preload and supporting the holding pressure generated by the pressing force generating means, preload adjusting means arranged in the preload generating means for adjusting the preload, and connected to the output disk And a transmission means for transmitting power to the drive shaft side, the method for assembling a toroidal type continuously variable transmission, comprising: A step of assembling in advance the input shaft disk, and transmission means assembly process of assembling the output disk in advance to the transmission means, together with assembling the transmission means to the casing, the input shaft is linked to a transmission means is inserted into the casing,
A temporary assembling step of assembling the trunnion and the power roller, and a preload generating means after the temporary assembling step,
Look including an adjusting step of adjusting the preload preload generating means for generating by said preload adjusting means so that the predetermined range, the said input shaft 2 pairs of input disks and output disks
The input discs are placed at both ends of the input shaft.
While each is arranged, a transmission means is placed in the center of the input shaft.
And a pair of output discs are placed on each
While the force generating means is arranged at one end of the input shaft, the other end is
A preload generating means is provided, and in the adjusting step,
Position the input shaft on the side of the pressing force generator by fixing it to the casing.
After making the decision, assemble the preload generation means,
A method for assembling a toroidal-type continuously variable transmission characterized by adjusting a preload thereafter . 3. The preload generating means is an input disk
Is interposed between the rear surface of the and the fastening means fastened to the input shaft.
Preload consisting of single or multiple disc springs
The adjusting means creates a gap between the fastening means and the back surface of the input disc.
And the inner circumference of the disc spring and the outer circumference of the input shaft.
The assembling method of the toroidal type continuously variable transmission according to claim 2, wherein the assembling method is made up of a tubular member inserted between them . 4. The adjusting step is a state in which fastening means is fastened.
In fastening means that it was or the gap between the input disc is between the plurality of disc springs
Of the preload generated by the preload generation means.
Axial dimension of tubular member so that the load is within the specified range
The method for assembling the toroidal-type continuously variable transmission according to claim 3, wherein: 5. The gap measurement performed in the adjusting step is
Interposed between the force disc and the fastening means or disc springs
And do what you do with a gauge that deforms when pinched
The assembling method of the toroidal type continuously variable transmission according to claim 4 . 6. In the adjusting step, the fastening means once fastened is used.
Remove and measure the thickness of the gauge as the gap
The preload with axial dimensions according to the measurement results.
6. The drive adjusting means is reassembled.
The method for assembling the toroidal type continuously variable transmission according to.