JP2013204672A - Continuously variable transmission and its assembly method - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a continuously variable transmission having superior assembling performance by preventing separation of spigot-fitting of a pressure receiving member during assembling, when the pressure receiving member spigot-fitted to a driven shaft through an output gear is supported.SOLUTION: A piston 23 is spigot-fitted to a driven shaft 20 through a return spring 24, and collar 29 supporting a back face of the piston is temporarily press-fitted and fixed to the driven shaft. The collar 29 is press-fitted into the driven shaft with a greater punching load than a spring reaction force of the return spring 24. A transmission case 5c and a differential device are incorporated thereafter, next, a gear sleeve 27 is spline-fitted to the driven shaft, an output gear 27a is engaged with a ring gear 31, and a lock nut 28 is fastened.

Description

The present invention relates to a belt-type continuously variable transmission and an assembling method thereof.

Generally, in a continuously variable transmission for a vehicle, power input from an engine is transmitted to an input shaft via a torque converter, and transmitted from the input shaft to a differential device via a drive pulley, a V belt, and a driven pulley. Is driven. A hydraulic oil chamber incorporating a return spring is provided on the back surface of the movable sheave of the driven pulley, and a piston (pressure receiving member) constituting one side wall of the hydraulic oil chamber is fitted in the driven shaft with an inlay. And after fitting an output gear, a bearing, etc. to a driven shaft, the piston is fastened and fixed to the driven shaft by screwing a lock nut to the end of the driven shaft. The output gear meshes with the ring gear of the differential device, and the outer race of the bearing is supported by the transmission case.

By the way, in order to obtain a large reduction ratio, an output gear having a root diameter smaller than the outer diameter of the bearing may be used. In this case, if the piston, the output gear, and the bearing are fixed to the driven shaft first and then the differential device is assembled, the bearing interferes with the ring gear of the differential device cannot be engaged with the output gear. For this reason, the differential device is first installed in the transmission case, and then the output gear and the bearing are fixed to the driven shaft. However, in this case, the piston inlay fitting is disengaged due to the spring force of the return spring. .

FIG. 4 shows an assembly structure of the driven pulley 105 described in Patent Document 1. A cylindrical gear sleeve 101 having an output gear 101a is spline fitted to a spline portion 100a formed at one end of the driven shaft 100, and an inner race of the bearing 102 is fitted to the outer end portion of the gear sleeve 101, A lock nut 103 is fastened to a threaded portion 100 b at the shaft end of the driven shaft 100. Due to the fastening force of the lock nut 103, the back surface of the piston 104 fitted in the inlay fitting portion 100d of the driven shaft 100 via the gear sleeve 101 is pressed in the axial direction, and the piston 104 is stepped on the stepped portion 100c of the driven shaft 100. It is pressed against and fixed. The piston 104 also functions as a spring receiving member that supports one end of the return spring 106. The outer diameter of the outer race of the bearing 102 is larger than the root diameter of the output gear 101a, and is fitted and held in the transmission case 107 on one side. The output gear 101a meshes with the ring gear 108 of the differential device.

In the assembly structure of the driven pulley 105, the differential device is first assembled in the transmission case so that the bearing 102 does not interfere with the ring gear 108 when the differential device is assembled, and then the gear sleeve 101 and the lock nut 103 are connected to the driven shaft. In this case, the piston 104 comes off due to the spring force of the return spring 106. Therefore, in Patent Document 1, a sleeve-like temporary fixing member (not shown) is screwed to the driven shaft 100 so that the piston 104 does not come off, and after the intermediate transmission case 109 and the differential device are assembled, Remove the temporary fixing member. When the temporary fixing member is removed, the piston 104 is disengaged due to the spring force of the return spring 106. Instead, the support wall portion 109a of the intermediate transmission case 109 supports the back surface of the piston 104. By setting the axial clearance between the support wall portion 107a and the piston 104 to be smaller than the axial length of the spigot fitting portion 100d, the piston 104 is driven by the driven shaft before the gear sleeve 101 and the lock nut 103 are attached to the driven shaft 100. It is possible to prevent the 100 spigot fitting part 100d from falling off completely.

However, in the case of Patent Document 1, in addition to the spring force of the return spring 106, the hydraulic pressure supplied to the inside of the piston 104 acts on the piston 104 in the axial direction, and the pressure needs to be supported only by the lock nut 103. There is. Therefore, a heavy burden is applied to the lock nut 103 and the threaded portion 100b, and there is a possibility that the cost of the parts and the size increase may be caused, such as using a large lock nut 103 or increasing the shaft diameter of the driven shaft 100. Further, until the intermediate case 109 having the support wall portion 109a is assembled, the temporary fixing member needs to be screwed to the driven shaft 100 so that the piston 104 does not come off from the spigot fitting portion 100d. The temporary fixing member is an unnecessary part after the continuously variable transmission is finally assembled, and there is a problem that the cost increases.

JP 2006-183706 A

SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a continuously variable transmission and an assembling method thereof that can improve the assembling property when assembling the driven pulley, reduce the cost, and reduce the load on the lock nut.

In order to achieve the object, the invention according to claim 1 is provided on the back side of the movable sheave of the driven pulley, and includes a hydraulic oil chamber having a built-in return spring, and one end of the hydraulic oil chamber that supports one end of the return spring. And a pressure receiving member whose inner peripheral portion is inlay-fitted to the driven shaft of the driven pulley, and a spline fitting to the driven shaft, supporting the rear surface of the inner peripheral portion of the pressure receiving member, and an outer peripheral portion. A cylindrical gear sleeve having an output gear formed on the outer periphery of the outer periphery of the gear sleeve or a driven shaft on the shaft end side of the gear sleeve, and an outer diameter larger than the tooth root diameter of the output gear Of the differential device that meshes with the output gear, and a bearing that is screwed to the shaft end of the driven shaft and presses and supports the pressure receiving member via the gear sleeve. A continuously variable transmission provided with a transmission gear or a reduction gear, wherein a collar that supports the back surface of the pressure receiving member is pressure-bonded to the outer periphery of the driven shaft with a detachment load larger than a spring reaction force of the return spring, A continuously variable transmission is provided in which a tip end portion of the gear sleeve presses and supports the pressure receiving member via the collar.

The invention according to claim 2 is provided on the back side of the movable sheave of the driven pulley, and constitutes a hydraulic oil chamber having a built-in return spring, one end of the return spring, and one side wall of the hydraulic oil chamber. A pressure-receiving member whose inner peripheral portion is inlay-fitted to the driven shaft of the driven pulley, a collar pressure-bonded to the driven shaft to support the back surface of the pressure-receiving member, and a spline-fitted to the driven shaft, the collar A cylindrical gear sleeve having an output gear formed on an outer peripheral portion thereof, and an outer periphery of the outer end portion of the gear sleeve or a driven shaft closer to the shaft end side than the gear sleeve. A bearing having an outer diameter larger than the tooth root diameter of the gear, a tightening member that is screwed to the shaft end of the driven shaft, and that presses and supports the pressure receiving member via the gear sleeve, and the output gear A ring gear or a reduction gear of a differential gear that meshes with the continuously variable transmission, wherein the inner periphery of the pressure receiving member is fitted into the driven shaft via a return spring, The collar that presses and supports the back surface of the inner peripheral portion of the pressure receiving member to the driven shaft is fixed to the driven shaft by a pulling load larger than the spring reaction force of the return spring, and the transmission case is fixed to the collar. A step of assembling the driven shaft through the assembly, a step of incorporating a ring gear or a reduction gear of the differential device into the transmission case, and a spline fitting of the gear sleeve having the bearing attached to the driven shaft; After the sleeve is spline fitted, the bearing is fitted to the driven shaft. A step of meshing the output gear with the ring gear or the reduction gear of the differential device, a fastening member is screwed to the end of the driven shaft, and the back surface of the inner peripheral portion of the pressure receiving member is pressed through the gear sleeve And a step of supporting the continuously variable transmission.

In the continuously variable transmission according to the present invention, the collar pull-out load that is crimped to the driven shaft is set to be larger than the spring reaction force of the return spring. You can also take part of the power. Therefore, the burden on the threaded portion of the driven shaft and the fastening member can be reduced, and the durability load can be increased. The “crimping” of the present invention is not limited to the case where the collar is press-fitted and fixed to the driven shaft at room temperature, but may be shrink-fitted and refers to a state where the collar is fixed to the outer periphery of the driven shaft with a predetermined pressing force.

In the present invention, the pressure receiving member that supports the return spring is fitted in the driven shaft with an inlay, and the back surface of the pressure receiving member is supported by the collar that is pressure-bonded to the driven shaft. The collar load is set to be larger than the spring reaction force of the return spring, so that the pressure receiving member does not fall off during assembly, and when assembling the intermediate transmission case or differential device, or when the gear sleeve, bearing and When fixing the fastening member to the driven shaft, it is not necessary to support the pressure receiving member. This eliminates the need for the support wall portion and temporary fixing member of the transmission case that supports the back surface of the pressure receiving member as in the prior art, and realizes a continuously variable transmission that is low in cost and excellent in assemblability.

The bearing in the present invention may be a roller bearing or a ball bearing. The bearing may be fitted and fixed to the gear sleeve, or may be directly fitted and fixed to the driven shaft. In particular, when a ball bearing is used, the inner race needs to be press-fitted and fitted, so it is desirable to pre-fit and fix it to the outside of the gear sleeve. In this case, compared with the case where the ball bearing is directly fixed to the driven shaft, the impact force when the inner race is press-fitted is not applied to the other end side of the driven shaft, but the bearing provided on the other end side of the driven shaft. Axial load is not applied.

The continuously variable transmission of the present invention is not limited to a structure in which the output gear is directly meshed with the ring gear of the differential device, but may be a structure in which a reduction gear is interposed between the output gear and the ring gear of the differential device. Also in this case, the output gear can be easily meshed with the reduction gear by spline-fitting the gear sleeve to the driven shaft later on the driven shaft, differential device and reduction gear incorporated on one side of the transmission case. Can do.

As described above, according to the present invention, the pressure receiving member that supports the return spring is fitted in the driven shaft with the inlay, and the collar that supports the back surface of the pressure receiving member is fixed to the driven shaft with a larger load than the spring reaction force of the return spring. Therefore, the collar can take part of the reaction force of the hydraulic pressure in addition to the spring reaction force of the return spring, and the burden on the fastening member and the screw portion fastened to the driven shaft can be reduced. Further, the use of the collar eliminates the need for the support wall portion of the transmission case that supports the back surface of the pressure receiving member and the temporary fixing member as in the prior art, and can realize an assembly method that is easy to assemble at low cost.

It is a skeleton figure of an example of a continuously variable transmission concerning the present invention. It is an expanded sectional view which shows the support structure of a driven pulley. It is process drawing which shows the assembly method of a driven pulley. It is sectional drawing which shows the support structure of the driven pulley in the conventional continuously variable transmission.

(First embodiment)
FIG. 1 shows a schematic configuration of an example of a continuously variable transmission according to the present invention.
The continuously variable transmission of this embodiment is an FF horizontal type automotive transmission, which is roughly switched between forward and reverse rotation of the input shaft 3 driven by the engine output shaft 1 via the torque converter 2 and the input shaft 3. The forward / reverse switching device 4 that transmits to the drive shaft 10, the continuously variable transmission A comprising the drive pulley 11, the driven pulley 21, and the V belt 15 wound between both pulleys, the power of the driven shaft 20 is output shaft 32. And a differential device 30 that transmits to the terminal. The input shaft 3 and the drive shaft 10 are arranged on the same axis, and the driven shaft 20 and the output shaft 32 of the differential device 30 are arranged parallel to the input shaft 3 and non-coaxially. Therefore, this continuously variable transmission has a three-axis configuration as a whole. The V belt 15 used in this embodiment is a known metal belt composed of a pair of endless tension bands and a large number of blocks supported by these tension bands.

The forward / reverse switching device 4 includes a planetary gear mechanism 40, a forward brake 50, and a reverse clutch 51. A sun gear 41 of the planetary gear mechanism 40 is connected to an input shaft 3 as an input member, and a ring gear 42 is an output member. Is connected to the drive shaft 10. The planetary gear mechanism 40 is a single pinion system, the forward brake 50 is provided between the carrier 44 supporting the pinion gear 43 and the transmission case 5, and the reverse clutch 51 is provided between the carrier 44 and the sun gear 41. ing. When the reverse clutch 51 is released and the forward brake 50 is engaged, the rotation of the input shaft 3 is reversed, decelerated, and transmitted to the drive shaft 10. Conversely, when the forward brake 50 is released and the reverse clutch 51 is engaged, the carrier 44 and the sun gear 41 of the planetary gear mechanism 40 rotate together, so that the input shaft 3 and the drive shaft 10 are directly connected. The planetary gear mechanism 40 is not limited to a single pinion system, and may be a known double pinion system.

As shown in FIG. 1, the drive pulley 11 of the continuously variable transmission A includes a fixed sheave 11a formed integrally on a drive shaft (pulley shaft) 10 and an axially movable and integrally rotated on the drive shaft 10. The movable sheave 11b is supported, and the hydraulic oil chamber 12 is provided between the back surface of the movable sheave 11b and the cylinder 13 fixed to the drive shaft 10. Shift control is performed by controlling the hydraulic pressure to the oil chamber 12.

Similarly, the driven pulley 21 includes a fixed sheave 21a formed integrally on a driven shaft (pulley shaft) 20, a movable sheave 21b supported on the driven shaft 20 so as to be axially movable and integrally rotatable, and a movable sheave. And a hydraulic oil chamber 22 provided between a back surface of 21 b and a piston (pressure receiving member) 23 fixed to the driven shaft 20. By controlling the oil pressure in the oil chamber 22, a belt thrust necessary for torque transmission is applied. Note that a return spring 24 for providing an initial thrust is disposed in the hydraulic oil chamber 22.

One end of the driven shaft 20 extends toward the engine, and an output gear 27a is provided at this one end. The output gear 27a meshes with the ring gear 31 of the differential device 30, and power is transmitted from the differential device 30 to the output shaft 32 extending left and right to drive the wheels.

FIG. 2 is a detailed view of the driven pulley 21 portion of the continuously variable transmission. The transmission case 5 is composed of three parts: a rear (non-engine side) case 5a, a front (engine side) case (converter housing) 5b, and an intermediate case 5c. The rear (opposite engine) end of the driven shaft 20 is rotatably supported by a rear transmission case 5a via a ball bearing 25, and the front (engine side) end supports a ball bearing 26. Via the front transmission case 5b. The inner ring of the ball bearing 25 is fixed to the rear end of the driven shaft 20 by a lock nut 35, and the outer ring is fixed to the transmission case 5a by a bolt 36 and a bearing retainer 37.

The piston 23 (pressure receiving member) is in-fitted to the in-row fitting portion 20f of the driven shaft 20, and a ring-shaped metal collar 29 is press-fitted to the press-fitting fitting portion 20c on the engine side from the in-row fitting portion 20f. Has been. The collar 29 may be any one that can be press-fitted with a force greater than the spring reaction force of the return spring 24, and there is no restriction on the shape. By press-fitting the collar 29, the inner peripheral side surface of the piston 23 is pressed against the stepped portion 20 d of the driven shaft 20 via the washer 38. The washer 38 also functions as a stopper when the movable sheave 21b is fully opened. The piston 23 receives the spring reaction force of the return spring 24 disposed in the hydraulic oil chamber 22, but the back surface is supported by the collar 29 press-fitted and fitted to the press-fitting fitting portion 20c. Absent. Furthermore, since the outer diameter of the collar 29 is larger than the outer diameter of a cylindrical portion 27c of the gear sleeve 27 described later, the back surface of the piston 23 can be supported over a wide area, and deformation of the piston 23 can be suppressed. In addition, although the pull-out load of the collar 29 is set to be higher than at least the spring reaction force of the return spring 24, it may be less than the reaction force due to the maximum hydraulic pressure supplied to the oil chamber 22. The collar 29 may be press-fitted into the press-fitting fitting portion 20c at room temperature. However, in order to increase the pull-out load of the collar 29, for example, the collar 29 is fitted into the press-fitting fitting portion 20c with heat expansion (shrink fitting). May be.

As shown in FIG. 2, the output gear 27 a is formed on the outer periphery of the substantially central portion of the cylindrical gear sleeve 27. A cylindrical extension portion 27b having no gear portion is formed at the axial front end portion (engine side end portion) of the gear sleeve 27, and the inner race 26a of the ball bearing 26 is fitted and fixed to the outer periphery of the extension portion 27b by press fitting. Has been. The outer race 26b of the ball bearing 26 has an outer diameter D4 that is larger than the root diameter D1 of the output gear 27a. Here, the outer diameter D2 of the extension 27b is substantially the same as the root diameter D1 of the output gear 27a, but may be larger or smaller than D1. The outer diameter D4 of the outer race 26b of the ball bearing 26 is larger than the tooth tip diameter D3 of the output gear 27a, but may be smaller than D3 and at least larger than the tooth root diameter D1. A cylindrical portion 27 c that does not have an output gear is formed at the axial rear end of the gear sleeve 27.

An inner spline 27 d that fits with an outer spline 20 a formed on the outer periphery on one end side of the driven shaft 20 is formed on the inner periphery of the gear sleeve 27. A lock nut (clamping member) 28 is fastened to the threaded portion 20b formed at the shaft end of the driven shaft 20. The gear sleeve 27 is pressed in the axial direction by the lock nut 28, and the cylindrical portion 27c of the gear sleeve 27 is pressed. The end surface is pressed against the back surface of the collar 29. The inner side surface of the lock nut 28 is in contact with the side surface of the inner race 26a of the ball bearing 26, but may be in contact with the end surface of the extension portion 27b. The outer race 26b of the ball bearing 26 is fitted and held in a recess 5b1 formed in the front transmission case 5b.

As described above, by press-fitting the collar 29 into the driven shaft 20, it is possible to achieve rotation prevention of the piston 23 and prevention of the return spring 24 from coming off against the spring reaction force. In addition, when the driven shaft 20 is deflected due to a belt-shaft force or a gear reaction force, a relative inclination is generated between the driven shaft 20 and the collar 29. However, the inclination is greater than the unloading load caused by the press-fit of the collar 29. Can be expected. Furthermore, since the collar 29 can take part of the hydraulic reaction force acting on the piston 23, the burden on the lock nut 28 can be reduced. Therefore, even if the lock nut 28 and the screw portion 20b having the same size as the conventional one are used, the durability load can be increased.

In Patent Document 1, a support wall portion close to the back surface of the piston 23 is provided on the inner wall of the intermediate transmission case 5c, and a temporary fixing member that supports the piston 23 is screwed to the driven shaft 20 during assembly. However, in the continuously variable transmission according to the present invention, it is not necessary to provide such a support wall portion, and a temporary fixing member is not necessary. This is because, when the driven pulley 21 is assembled, once the collar 29 is press-fitted into the driven shaft 20, the piston 23 does not come off due to the spring reaction force of the return spring 24.

Here, a method of assembling the driven shaft 20 and the differential device 30 will be described with reference to FIG. Before assembling the driven shaft 20 to the transmission case, as shown in FIG. 3A, first, the piston 23 is fitted into the spigot fitting portion 20f of the driven shaft 20 and the back surface of the inner peripheral portion of the piston 23 is pressed. The collar 29 to be supported is press-fitted into the press-fitting fitting portion 20 c of the driven shaft 20. By press-fitting the collar 29, the piston 23 is pressed against the stepped portion 20d of the driven shaft 20 via the washer 38, and the piston 23 is prevented from being detached from the spigot fitting portion 20f by the return spring 24. Next, the rear end portion of the driven shaft 20 is assembled to the rear transmission case 5 a via the ball bearing 25. In FIG. 3, the driven shaft 20 is shown in a horizontal state, but actually, the driven shaft 20 is vertically lowered with the transmission case 5 a positioned upward.

Next, as shown in FIG. 3B, the intermediate case 5c and the differential device 30 are assembled in order from the lower side. When the differential device 30 is assembled, nothing is mounted on the front end portion of the driven shaft 20, so that the ring gear 31 can be easily assembled without interference. Next, the gear sleeve 27 in which the ball bearing 26 is press-fitted and fitted in advance is spline-fitted to the driven shaft 20. At this time, the output gear 27 a is engaged with the ring gear 31 of the differential device 30. Since the large-diameter ball bearing 26 is located behind the output gear 27a, the gear sleeve 27 can be smoothly inserted without the ball bearing 26 and the ring gear 31 interfering with each other.

After the gear sleeve 27 is inserted, the lock nut 28 is fastened to the threaded portion 20b of the shaft end of the driven shaft 20 as shown in FIG. The gear sleeve 27 is pressed in the axial direction by the tightening force of the lock nut 28, and the end surface of the cylindrical portion 27 c presses the back surface of the collar 29. The tightening force of the lock nut 28 terminates at the stepped portion 20d of the driven shaft 20 and does not reach the front ball bearing 25, so that an extra load is not applied to the ball bearing 25. Finally, the recess 5b1 of the front transmission case 5b is fitted into the outer race of the ball bearing 26, thereby completing the assembly.

The present invention is not limited to the above embodiment. For example, in the embodiment, the output gear 27a is provided at the center of the gear sleeve 27, the extension 27b is provided at one end in the axial direction, and the inner race of the bearing 26 is fitted to the extension 27b. The inner race of the bearing 26 may be directly fitted to the shaft end portion of the driven shaft 20. In this case, the gear sleeve 27 and the bearing 26 are arranged in series on the driven shaft 20.

Furthermore, in the said Example, although the pressure receiving member which supports the end of a return spring and comprises the one side wall of a hydraulic oil chamber was shown as the piston 23, the cylinder may be sufficient. Moreover, although the example in which the ring gear 31 of the differential device is directly meshed with the output gear 27a has been shown, the output gear 27a may be meshed with the ring gear 31 via the reduction gear.

11 drive pulley 15 V belt 20 driven shaft 20a outer spline 20b threaded portion 20c press fit fitting portion 20f spigot fitting portion 21 driven pulley 22 hydraulic oil chamber 23 piston (pressure receiving member)
24 return spring 26 ball bearing 27 gear sleeve 27a output gear 28 lock nut (tightening member)
29 Color 30 Differential device 31 Ring gear

Claims (2)

A hydraulic oil chamber provided on the back side of the movable sheave of the driven pulley and having a return spring built therein, supports one end of the return spring and constitutes one side wall of the hydraulic oil chamber, and an inner peripheral portion is driven by the driven pulley. A pressure-receiving member fitted in a shaft with an inlay, a cylindrical gear sleeve that is spline-fitted to the driven shaft, supports an inner peripheral rear surface of the pressure-receiving member, and has an output gear formed on an outer peripheral portion; Mounted on the outer periphery of the outer end of the gear sleeve or on the driven shaft on the shaft end side of the gear sleeve, and screwed to the shaft end of the driven shaft and a bearing having an outer diameter larger than the root diameter of the output gear. A stepless variable member comprising: a tightening member that presses and supports the pressure receiving member via the gear sleeve; and a ring gear or a reduction gear of a differential device that meshes with the output gear. A machine,
A collar that supports the back surface of the pressure receiving member is pressure-bonded to the outer periphery of the driven shaft with a larger load than the spring reaction force of the return spring, and the tip of the gear sleeve presses the pressure receiving member through the collar. A continuously variable transmission characterized by being supported. A hydraulic oil chamber provided on the back side of the movable sheave of the driven pulley and having a return spring built therein, supports one end of the return spring and constitutes one side wall of the hydraulic oil chamber, and an inner peripheral portion is driven by the driven pulley. A pressure receiving member fitted in-slot to the shaft, a collar crimped to the driven shaft to support the back surface of the pressure receiving member, and a spline fitted to the driven shaft to support the back surface of the collar and to the outer peripheral portion A cylindrical gear sleeve in which an output gear is formed, and an outer diameter of the outer end of the gear sleeve or a driven shaft closer to the shaft end side than the gear sleeve, and having an outer diameter larger than the tooth root diameter of the output gear. A bearing having a clamping member that is screwed onto the shaft end of the driven shaft and presses and supports the pressure receiving member via the gear sleeve, and a differential that meshes with the output gear. A ring gear or reduction gear of location, a method of assembling a continuously variable transmission having a,
A step of fitting the inner periphery of the pressure receiving member into the driven shaft via a return spring;
A step of pressing and fixing a collar that presses and supports the back surface of the inner peripheral portion of the pressure receiving member to the driven shaft to the driven shaft with a larger load than a spring reaction force of the return spring;
Assembling a transmission case through a driven shaft having the collar fixed thereto;
Incorporating the ring gear or the reduction gear of the differential device into the transmission case;
The gear sleeve having the bearing attached to the driven shaft is spline-fitted, or after the gear sleeve is spline-fitted, the bearing is fitted to the driven shaft, and the output gear is connected to the differential device. Engaging with a ring gear or a reduction gear;
A step of assembling the continuously variable transmission, comprising: screwing a tightening member onto an end of the driven shaft and pressing and supporting the back surface of the inner peripheral portion of the pressure receiving member via the gear sleeve.

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