JP2002106668A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the weight and cost of a pressure regulating cam mechanism, to improve an assembling property, and to make the pressure regulating cam mechanism compact along the radial direction of a transmission shaft in a continuously variable transmission transmitting the speed-variable power to a driven rotary member from a driving rotary member by the movement of a carrier supporting a speed change rotary member kept in frictional contact with the driving rotary member and the driven rotary member. SOLUTION: The pressure regulating cam mechanism 66 comprises a projection 67 integrally provided on one of the driven rotary member 28 and an output rotary member 61 and protruded to the other side and a recess 68 provided on the other of the driven rotary member 28 and the output rotary member 61 and storing the tip section of the projection 67 in contact with it.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method for transmitting variable speed power from a driving rotary member to a driven rotary member by moving a carrier that supports a variable speed rotating member that frictionally contacts the driven rotary member and the driven rotary member. It relates to a step transmission.

[0002]

2. Description of the Related Art Conventionally, such a continuously variable transmission is already known, for example, from Japanese Patent Application Laid-Open No. 9-177920.

[0003]

By the way, in such a continuously variable transmission, an output rotary member which is rotatably supported on a transmission shaft and whose movement in a direction away from the driven rotary member is regulated, A pressure regulating cam mechanism is provided between the rotating member and the pressure regulating cam mechanism. The pressure regulating cam mechanism transmits torque from the driven rotating member to the output rotating member, and the driven rotating member rotates in accordance with the relative rotation of the driven rotating member and the output rotating member. The member is pressed against the carrier.

However, in the continuously variable transmission disclosed in the above-mentioned Japanese Patent Application Laid-Open No. 9-177920, concave portions provided in a circumferential direction at a plurality of positions on the opposing surfaces of the driven rotary member and the output rotary member, respectively, The pressure adjusting cam mechanism is constituted by the spheres respectively fitted into the pair of concave portions corresponding to each other.

[0005] Such a pressure adjusting cam mechanism requires a retainer for holding each sphere, which leads to an increase in cost and an increase in weight, and cannot be said to be excellent in assemblability. In addition, since the diameter of the sphere must be set relatively large in order to perform the cam function, the size of the pressure adjusting cam mechanism along the radial direction of the transmission shaft is relatively large. There is also a problem that noise is generated due to rattling of the respective spheres in the concave portions.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and it has been made possible to reduce the weight and cost and improve the assemblability, and furthermore, the pressure regulating cam is made compact along the radial direction of the transmission shaft. It is an object to provide a continuously variable transmission having a mechanism.

[0007]

In order to achieve the above object, according to the present invention, there is provided a transmission shaft rotatably supported by a casing so that power from an engine can be input, and a transmission shaft relative to the transmission shaft. A drive rotation member that is non-rotatably coupled, a driven rotation member that is rotatably supported on the transmission shaft, a carrier that can move along the axis of the transmission shaft, and a center line that is centered on the axis of the transmission shaft. A support shaft supported by the carrier having an axis along a conical generating line, a first conical friction transmitting surface that contacts the driving rotary member, and a second conical friction that frictionally contacts the driven rotary member A transmission rotating member having a transmission surface rotatably and axially slidably supported by the support shaft, and a rotatably supported relative to the transmission shaft at a position sandwiching the driven rotation member between the carrier and the carrier; When done An output rotation member whose movement in a direction away from the driven rotation member is restricted, and which is capable of transmitting torque between the driven rotation member and the output rotation member, and has a relative position between the driven rotation member and the output rotation member. A pressure-adjusting cam mechanism that presses the driven rotating member toward the carrier according to rotation.
The pressure adjusting cam mechanism is provided integrally with one of the driven rotation member and the output rotation member and protrudes to the other side, and the pressure adjustment cam mechanism is provided on the other of the driven rotation member and the output rotation member, and And a recess for accommodating and contacting the tip of the part.

[0008] According to such a configuration, the distal end of the projection integrally formed on one of the driven rotary member and the output rotary member is housed in the recess provided on the other of the driven rotary member and the output rotary member. , So that the pressure adjusting cam mechanism is formed by the contact, so that a retainer is unnecessary as compared with a conventional one in which a sphere is interposed between the driven rotary member and the output rotary member, so that cost and weight are reduced. As a result, not only the assemblability can be improved, but also the problem of noise generation due to rattling in the concave portion of the sphere can be solved. Moreover, in order to fulfill the cam function, the size of the protrusions and recesses along the circumferential direction of the transmission shaft must be secured to some extent, but the protrusions and recesses must be reduced in the direction along the radial direction of the transmission shaft. Therefore, the pressure-adjusting cam mechanism can be downsized along the radial direction of the transmission shaft.

The invention according to claim 2 is the same as the above-described claim 1.
In addition to the configuration of the invention described in the above, a cylindrical support tube portion rotatably supported by the transmission shaft is integrally formed at a central portion of a driven rotation member formed in a bowl shape with the drive rotation member side opened. The cylindrical output rotary member is provided with a bearing hole for fitting a bearing interposed between the output rotary member and the transmission shaft, and an output rotary member side end of the support cylinder portion. And a receiving hole formed with a larger diameter than the bearing hole, and the pressure regulation between an annular step provided on the output rotary member between the bearing hole and the receiving hole and an opposing surface of the support cylindrical portion. A cam mechanism is configured, and a disc spring surrounding the support cylinder portion exerts a spring force for pressing the driven rotation member against the second friction transmission surface, and is provided between the driven rotation member and the output rotation member. Features.

According to the configuration of the second aspect of the present invention, the driven rotary member and the output rotary member are arranged close to each other in the axial direction even though the pressure adjusting cam mechanism is provided therebetween. It is possible to contribute to downsizing of the step transmission, and to improve the assemblability by allowing a disc spring for applying a preload to the driven rotary member to be attached to the support cylinder portion of the driven rotary member. Can be.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described based on one embodiment of the present invention shown in the attached drawings.

1 to 5 show one embodiment of the present invention. FIG. 1 is a longitudinal sectional view showing a power transmission structure between an engine and a continuously variable transmission, and FIG. FIG. 3 is an enlarged longitudinal sectional view of the continuously variable transmission in a state of a top gear ratio, FIG. 4 is an enlarged sectional view taken along line 4-4 of FIG. 3, and FIG. FIG. 5 is an enlarged sectional view taken along line 5-5 in FIG. 2 for explaining the operation of the cam mechanism.

First, in FIG. 1, the output of an engine E mounted on a vehicle such as a motorcycle is transmitted from a crankshaft 11 of the engine E to a drive gear 12, a driven gear 13, a damper spring 14, an automatic centrifugal clutch 15, a continuously variable clutch. The output gear 17 is transmitted to an output gear 17 via a transmission 16, and a reduction gear 18 connected to a rear wheel WR which is a driving wheel is connected to the output gear 17.
To be engaged.

The driving gear 12, the driven gear 13, the damper spring 14, and the automatic centrifugal clutch 15 are housed in a first working chamber 20 formed in a casing 19 connected to a crankcase of the engine E. Step transmission 1
6, the output gear 17 and the reduction gear 18 are housed in a second working chamber 21 formed in the casing 19,
The second working chambers 20 and 21 are formed in the casing 19 on both sides of a wall 19 a provided in the casing 19.

A crankshaft 1 is provided in the first working chamber 20.
An input shaft 22 having an axis parallel to 1 is arranged, and both ends of the input shaft 22 are rotatably supported by a casing 19.

The automatic centrifugal clutch 15 is connected to the driven gear 1.
3, an input member 23 connected via a damper spring 14 and rotatably supported by an input shaft 22;
2, an output member 24 in the shape of a bowl,
A plurality of centrifugal weights 25... Supported by the input member 23 so as to be able to make frictional contact with the inner surface of the input member 23 and each centrifugal weight 25. And a biasing spring (not shown).
Is transmitted from the input member 23 to the output member 24, that is, the input shaft 22, when the rotation speed of the input member 23 becomes equal to or higher than a predetermined value.

Referring to FIGS. 2 and 3, the continuously variable transmission 16 includes a transmission shaft 26 having an axis coaxial with the input shaft 22, and a drive rotating member 27 which rotates integrally with the transmission shaft 26. A driven rotating member 28 rotatably supported on the transmission shaft 26, a carrier 29 movable along the axis of the transmission shaft 26, and a plurality of support shafts 30 supported by the carrier 29. , Which are supported by the support shafts 30, 30, respectively.

One end of the transmission shaft 26 penetrates the wall 19a of the casing 19 in a liquid-tight and rotatable manner, and the first working chamber 2
0, and is coupled to the input shaft 22 so as not to rotate relatively. The drive rotating member 27 is formed in a ring shape with a friction contact surface 27a facing outward in the radial direction.
For example, by being formed integrally with the transmission shaft 26, it cannot rotate relative to the transmission shaft 26. Driven rotating member 2
The transmission shaft 2 is formed in a bowl shape opened to the drive rotating member 27 side and has a needle bearing 32 interposed therebetween.
The driven rotary member 28 is provided with a friction contact surface 28a that faces inward in the radial direction on the inner surface of the open end of the driven rotary member 28.

The carrier 29 has a substantially conical first carrier half 33 having a small diameter on the side of the driven rotating member 28, and a disc-shaped large-diameter end of the first carrier half 33, that is, a driven rotation. A second carrier half 34 joined to the opposite end of the member 28, the first and second carrier halves 33,
The transmission shaft 26 is rotatably and slidably supported in the axial direction via the transmission shaft 5 and 36.

The first carrier half 33 is provided with a plurality of window holes 37 equally spaced in the circumferential direction, and has an axis along a conical generatrix centered on the axis of the transmission shaft 26. Then, both ends of the plurality of support shafts 30 crossing the window holes 37 are supported by the first carrier half 33. The speed change rotating members 31 are rotatably and axially slidably supported on the support shafts 30 via a pair of needle bearings 38, 38, respectively.

The transmission rotating member 31 includes a driving rotating member 27.
And a conical second frictional transmission surface 41 that frictionally contacts the frictional contact surface 28a of the driven rotary member 28.

A shaft 42 having an axis perpendicular to the axis of the transmission shaft 26 is fixed to the outer periphery of the second carrier half 34 of the carrier 29.
Is rotatably supported. On the other hand, a U-shaped regulating member 44 extending in a direction parallel to the axis of the transmission shaft 26 is fastened to the inner surface of the casing 19, and the roller 43 is rotatably accommodated in the regulating member 44. . Therefore, the second carrier half 34, that is, the carrier 29, enables the transmission shaft 26 to move in the axial direction and the transmission shaft 2.
6 cannot be rotated around the axis, and is engaged with the casing 19.

A driven screw 45 coaxial with the transmission shaft 26 is fastened to the second carrier half 34 of the carrier 29, and the driven screw 45 is rotatably supported on the transmission shaft 26 via a ball bearing 56. Drive screw 46 is screwed.

A transmission shaft 26 is provided on the outer surface of the casing 19.
Forward / reverse rotatable electric motor 47 having an axis parallel to
Is mounted, and a speed reduction mechanism 48 is provided between the electric motor 47 and the driving screw 46.

The reduction mechanism 48 includes a drive gear 49 provided on the output shaft of the electric motor 47, a first idle gear 50 meshing with the drive gear 49, and a second idle gear integrated with the first idle gear 50. A driven gear 52 fixed to the drive screw 46 and meshing with the second idle gear 51
And the first and second idle gears 5
Reference numerals 0 and 51 are rotatably supported by an idle shaft 53 which has an axis parallel to the transmission shaft 26 and is supported by the casing 19.

When rotational power is applied to the drive screw 46 from the electric motor 47 via the speed reduction mechanism 48, the drive screw 4
6 to which a driven screw 45 screwed to 6 is fixed
9 is engaged with the casing 19 so that the transmission shaft 26 can move in the axial direction of the transmission shaft 26 and cannot rotate around the axis of the transmission shaft 26, so that the transmission shaft 9 moves in the axial direction of the transmission shaft 26.

In such a continuously variable transmission 16, the distance from the contact point between the frictional contact surface 27a of the drive rotating member 27 and the first frictional transmission surface 40 to the axis of the transmission shaft 26 is A,
The distance from the contact point between the friction contact surface 27a of the drive rotation member 27 and the first friction transmission surface 40 to the axis of the support shaft 30 is B,
The distance from the contact point between the friction contact surface 28a of the driven rotation member 28 and the second friction transmission surface 41 to the axis of the support shaft 30 is C,
The distance from the contact point between the friction contact surface 28a of the driven rotation member 28 and the second friction transmission surface 41 to the axis of the transmission shaft 26 is D, the rotation speed of the drive rotation member 27 is NI, and the rotation speed of the driven rotation member 28 is NO, and the gear ratio R is R = NI / NO
Then, R = NI / NO = (B / A) × (D / C).

The electric motor 47 and the speed reduction mechanism 48
, The driven screw 45 is rotated, and the driven screw 45 and the carrier 29 are moved from the driven rotary member 28 as shown in FIG.
, The distance B increases and the distance C decreases, and since the distances A and D are constant, the speed ratio R increases, and the distance B becomes maximum and the distance C becomes minimum. The low gear ratio is obtained in the state shown in FIG.
On the other hand, when the driven screw 45 and the carrier 29 are moved in a direction away from the driven rotary member 28 as shown in FIG. 3, the distance B decreases and the distance C increases, and the distances A and D are constant. Therefore, the gear ratio R becomes smaller, the distance B becomes the minimum, and the distance C becomes the maximum in the state of FIG. 3 where the distance C becomes the maximum.

Referring also to FIG.
In the driven gear 52, a regulating protrusion 54 protruding toward the driven screw 45 side is integrally provided. Further, the restricting projection 54 is brought into contact with the driven screw 45 as the driven screw 45 approaches the driven gear 52 until the speed ratio between the driving rotary member 27 and the driven rotary member 28 reaches the top speed ratio. , A contact portion 55 to be engaged is provided integrally,
Driven screw 4 that cannot rotate around the axis of transmission shaft 26
The rotation angle of the drive screw 46, that is, the amount of movement of the carrier 29 in the axial direction is restricted by the contact and engagement of the restricting projection 54 with the contact portion 55 of No. 5.

At the center of a driven rotary member 28 formed in a bowl shape with the drive rotary member 27 open, a cylindrical support cylinder 28b is provided. A needle bearing is provided between the support cylinder 28b and the transmission shaft 26. 32 are interposed. A cylindrical output rotation member 61 is disposed at a position where the driven rotation member 28 is sandwiched between the driven rotation member 28 and the carrier 29, and the output gear 17 is fixed to the output rotation member 61.

The output rotary member 61 and the transmission shaft 26
An angular contact bearing 57 is interposed between them. The outer ring of the angular contact bearing 57 is sandwiched between the output gear 17 and a retaining ring 58 mounted on the inner periphery of the output rotating member 61. At the end of the inner ring of the angular contact bearing 57 opposite to the driven rotating member 28, a cylindrical spacer 59 inserted between the output gear 17 and the transmission shaft 26 so as to surround the transmission shaft 26 coaxially. One end of the spacer 59
Is in contact with a cotter 60 mounted on the transmission shaft 26. Therefore, the output rotation member 61 and the output gear 17
Is prevented from moving in a direction away from the driven rotary member 28 and is rotatably supported by the transmission shaft 26.

The output rotary member 61 includes the output rotary member 6.
1 and a bearing hole 62 for fitting an angular contact bearing 57 interposed between the transmission shaft 26 and the bearing hole so as to receive an end of the support cylinder portion 28b of the driven rotary member 28 on the output rotary member 61 side. A receiving hole 63 having a diameter larger than that of the bearing hole 62 is provided.
An annular step 64 facing the support cylinder 28b is provided on the output rotary member 61 between the second and the accommodation holes 63.

Referring also to FIG. 5, the driven rotary member 28
A pressure adjusting cam mechanism 66 is provided between the support cylinder portion 28b and the opposing surface of the step portion 64 of the output rotary member 61. The pressure adjusting cam mechanism 66 is integrated with the support cylindrical portion 28b of the driven rotary member 28. And a plurality of projections 67 protruding toward the output rotary member 61 and a step 64 of the output rotary member 61.
And a plurality of recesses 68 for accommodating and contacting the tips of the projections 67.

On the other hand, between the driven rotary member 28 and the output rotary member 61, a spring force for pressing the friction contact surface 28 a of the driven rotary member 28 against the second friction transmitting surface 40 of the speed change rotary member 31 is exerted. A disc spring 69 for applying a preload to the driven rotary member 28 in a direction away from the output rotary member 61
And a washer 70 are provided so as to surround the support cylinder 28b.

When a torque is applied to the driven rotary member 28 to cause relative rotation between the pressure adjusting cam mechanism 66 and the output rotary member 61, the pressure-adjusting cam mechanism 66 rotates as shown in FIG. The rotational power is transmitted from the driven rotary member 28 to the output rotary member 61 while urging the member 28 in a direction to separate the output rotary member 61 from the output rotary member 61. This urging force cooperates with the urging force of the disc spring 69 to form the frictional contact surface 27a of the driving rotary member 27.
And a surface pressure for pressing the friction contact surface 28 a of the driven rotary member 28 against the second friction transmission surface 41.

In the neutral state where no torque acts on the driven rotary member 28 and no relative rotation occurs between the driven rotary member 28 and the output rotary member 61, as shown in FIG. Are in contact with the center of
7 do not rattle in the recesses 68.

First carrier half 3 in carrier 29
3, a thrust bearing 71 is mounted on the inner peripheral portion of the driven member 28 and the carrier 29 at a low speed ratio.
Interposed in between.

The other end of the transmission shaft 26 is rotatably supported by the casing 19 via a ball bearing 72. The other end of the transmission shaft 26 is connected to an oil pump P, which is a trochoid pump. . On the other hand, a filter 74 facing the lower part in the second working chamber 21 is attached to the casing 19, and the casing 19 is provided with a suction oil passage 73 connecting the filter 74 and the oil pump P,
The transmission shaft 26 is provided coaxially with a lubricating oil passage 75 for guiding oil from the oil pump P, and has a plurality of inner ends connected to the lubricating oil passage 75 and an outer end opened to the outer surface of the transmission shaft 26. Oil absorption holes 76 are continuously variable transmission 1
6 is provided.

Further, another filter 77 is attached to the casing 19 corresponding to a lower portion in the first working chamber 20, and the oil purified by the filter 77 is supplied to the casing 19 by another oil pump (not shown). The oil is supplied to each lubricating portion of the engine E via an oil supply passage 78 provided in the engine E.

Next, the operation of this embodiment will be described. The driven screw 45 is fixed to the carrier 29 engaged with the casing 19 so that it cannot rotate around the axis of the transmission shaft 26, and the axis of the transmission shaft 26 is fixed. A drive screw 46, which is rotatable around and is supported on the casing 19, is screwed onto said driven screw 45, and
A speed reduction mechanism 48 is provided between the electric motor 47 and the drive screw 46 supported by 9.

Therefore, when the drive screw 46 is rotated in response to the operation of the electric motor 47, the driven screw 45, that is, the carrier 29 moves in the direction along the axis of the transmission shaft 26, and the speed of the continuously variable transmission 16 is changed. The ratio can be changed freely. In addition, the casing 19 receives the rotational reaction force acting on the carrier 29 from the speed change rotating member 31 via the support shaft 30, and the electric motor 47 does not bear the rotation reaction force. It is only necessary to exert the power to move in the direction along the axis, and the size of the electric motor 47 can be reduced. Further, since the reduction ratio of the reduction mechanism 48 does not need to be set large, the speed change speed does not decrease.

In order to determine the position of the carrier 29 at the top speed ratio, the driven gear 5 constituting a part of a speed reduction mechanism 48 provided between the electric motor 47 and the drive screw 46
2 is provided integrally with the regulating protrusion 54, and the driven screw 45 fixed to the carrier 29 is integrally provided with the contacting portion 55 which makes contact with and engages with the regulating protrusion 54 at the top speed ratio. In comparison with the case in which the stopper bolt is fixed to the casing 19, the casing 19 does not need to be processed and the assembling work to the casing 19 is unnecessary, so that the workability and the assemblability can be reduced while reducing the number of parts. Can be improved. In addition, since it is unnecessary to secure the rigidity of the casing 19 by increasing the thickness, the weight can be reduced.

Further, the regulating protrusion 54 and the contact portion 55
Since the driven gear 52 and the driven screw 45 are provided integrally with each other, the regulating projection 54 and the abutting portion 55 are provided.
The position of the carrier 29 in the axial direction when is engaged and abutted can be accurately determined.

In addition, when the restricting projection of the driven gear 52 is brought into contact with and engaged with the stopper bolt fixed to the casing 19, the rotation range of the driven gear 52 is restricted to less than 360 degrees. The contact protrusion 55 of the driven screw 45 is brought into contact with and engaged with the contact portion 55 of the driven screw 45. It is also possible to extend the angle to 360 degrees or more, so that the degree of freedom in designing the speed reduction mechanism 48 can be improved.

An output rotary member 61 rotatably supported on the transmission shaft 26 at a position where the driven rotary member 28 is sandwiched between the carrier 29 and the driven rotary member 28, the movement of which is restricted from moving away from the driven rotary member 28; The pressure adjusting cam mechanism 66 provided between the driven rotary member 28 and the driven rotary member 28
A plurality of projections 67 provided integrally with the output rotation member 61 and projecting toward the output rotation member 61, and recesses 68 provided on the output rotation member 61 to receive and contact the tips of the projections 67. Have been.

Therefore, as compared with the conventional pressure adjusting cam mechanism in which a sphere is interposed between the driven rotary member 28 and the output rotary member 61, a retainer for holding the sphere is unnecessary, so that cost and weight can be reduced. As a result, not only the assemblability of the pressure adjusting cam mechanism 66 is improved, but also the problem of noise generation due to rattling in the concave portion of the sphere can be solved. Moreover, in order to perform the cam function, the protrusions 67 and the recesses 68 along the circumferential direction of the transmission shaft 26 must have a certain size, but in the direction along the radial direction of the transmission shaft 26, Since the protrusions 67 and the recesses 68 can be reduced, the pressure adjustment cam mechanism 66 can be made compact along the radial direction of the transmission shaft 26.

Further, a cylindrical supporting cylinder 28b is integrally provided at the center of a driven rotating member 28 formed in a bowl shape with the driving rotating member 27 side opened, and the cylindrical output rotating member 6 is provided.
1, a bearing hole 62 for fitting a needle bearing 32 interposed between the output rotary member 61 and the transmission shaft 26, and a bearing hole for receiving an end of the support cylinder 28b on the output rotary member 61 side. A receiving hole 63 having a diameter larger than that of the receiving hole 63 is provided.
Between the annular step 64 provided on the output rotary member 61 and the opposing surface of the support cylinder 28b.
6 are constituted. Accordingly, despite the provision of the pressure adjusting cam mechanism 66 therebetween, the driven rotary member 28 and the output rotary member 61 can be arranged close to each other in the axial direction, thereby contributing to downsizing of the continuously variable transmission 16. Becomes

Further, a disc spring 69 surrounding the support cylinder 28b.
Is provided between the driven rotary member 28 and the output rotary member 61 by exerting a spring force for pressing the friction contact surface 28a of the driven rotary member 28 against the second friction transmission surface 41 of the speed change rotary member 31. The disc spring 69 is attached to the driven rotating member 28.
Can be assembled to the supporting cylindrical portion 28b, and assemblability can be improved.

The embodiments of the present invention have been described above. However, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the present invention described in the appended claims. It is possible.

[0050]

As described above, according to the first aspect of the present invention, the cost can be reduced as compared with the prior art in which the ball is interposed between the driven rotary member and the output rotary member to constitute the pressure adjusting mechanism. In addition, the weight can be reduced, and not only the assemblability can be improved, but also the problem of noise generation due to rattling in the concave portion of the sphere can be solved. Moreover, it is possible to make the pressure adjusting cam mechanism compact along the radial direction of the transmission shaft.

According to the second aspect of the present invention, the driven rotary member and the output rotary member are disposed close to each other in the axial direction.
A coned disk spring that can contribute to the compactness of the continuously variable transmission and applies a preload to the driven rotating member,
The assemblability can be improved by being able to be attached to the support cylinder of the driven rotary member.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a power transmission structure between an engine and a continuously variable transmission.

FIG. 2 is an enlarged vertical sectional view of the continuously variable transmission in a state of a low gear ratio.

FIG. 3 is an enlarged vertical sectional view of the continuously variable transmission in a state of a top speed ratio.

FIG. 4 is an enlarged sectional view taken along line 4-4 in FIG. 3;

FIG. 5 is a view 5 of FIG. 2 for explaining the operation of the pressure adjusting cam mechanism.
It is an expanded sectional view which follows a -5 line.

[Explanation of symbols]

 E: engine 16: continuously variable transmission 19: casing 26: transmission shaft 27: driving rotary member 28: driven rotary member 28b: support cylinder 29: carrier Reference Signs List 30 support shaft 31 speed change rotating member 32 needle bearing as bearing 40 first friction transmission surface 41 second friction transmission surface 61 output rotation member 62・ Bearing hole 63 ・ ・ ・ Accommodation hole 64 ・ ・ ・ Step 66 ・ ・ ・ Pressure adjusting cam mechanism 67 ・ ・ ・ Protrusion 68 ・ ・ ・ Recess 69 ・ ・ ・ Disc spring

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Kazuhiko Nakamura 1-4-1 Chuo, Wako-shi, Saitama F-term in Honda R & D Co., Ltd. (Reference) 3J051 AA03 BA05 BB08 BC03 BD02 BE05 CA03 CB05 EA01 EA05 EC04 FA03

Claims (2)

[Claims] 1. A transmission shaft (26) rotatably supported by a casing (19) to receive power from an engine (E), and a drive rotation coupled to the transmission shaft (26) so as to be relatively non-rotatable. Member (27) and the transmission shaft (2
A driven rotating member (28) supported to be rotatable relative to 6);
A carrier (29) movable along the axis of the transmission shaft (26); and a carrier (2) having an axis along a conical generatrix centered on the axis of the transmission shaft (26).
9), a conical first frictional transmission surface (40) in contact with the drive rotary member (27), and a conical first frictional contact surface in frictional contact with the driven rotary member (28). (2) a speed change rotating member (31) having a friction transmitting surface (41) and rotatably and axially slidably supported on the support shaft (30); and the driven rotation member (28) is connected to the carrier (29). ) Is rotatably supported on the transmission shaft (26) at a position sandwiched between the driven rotation member (2) and the driven rotation member (2).
8) The output rotating member (61) whose movement in the direction away from the output rotating member (61) is regulated, and the driven rotating member (28) and the output rotating member (61) are capable of transmitting torque and the driven rotating member (28). ) And the output rotating member (6)
A pressure adjusting cam mechanism (66) for pressing the driven rotation member (28) toward the carrier (29) in accordance with the relative rotation of 1).
Wherein the pressure-adjusting cam mechanism (6)
6) a projection (67) integrally provided on one of the driven rotation member (28) and the output rotation member (61) and protruding to the other side, and the driven rotation member (28) and the output rotation A continuously variable transmission, comprising: a recess (68) provided on the other side of the member (61) to receive and contact the tip of the projection (67). 2. A cylindrical member rotatably supported by the transmission shaft (26) at the center of a driven rotary member (28) formed in a bowl shape with the drive rotary member (27) side open. A support cylinder (28b) is provided integrally, and a bearing (32) interposed between the output rotary member (61) and the transmission shaft (26) is fitted to the cylindrical output rotary member (61). The bearing hole (62) to be fitted and the support cylinder (28b)
The receiving hole (6) formed to have a larger diameter than the bearing hole (62) so as to receive the end of the output rotating member (61).
3) are provided, and the bearing hole (62) and the accommodation hole (6) are provided.
The pressure adjusting cam mechanism (66) is formed between an opposing surface of the annular step (64) provided on the output rotary member (61) and the support cylinder (28b), and the support cylinder ( 2
8b) and a disc spring (69) surrounding the driven rotary member (2).
2. The device according to claim 1, wherein the second rotary member is provided between the driven rotary member and the output rotary member by exerting a spring force for pressing the second rotary member against the second friction transmission surface. Step transmission.