KR19980063625A - Continuously variable transmission - Google Patents

Abstract

The present invention provides a simple structure for automatically controlling the speed ratio of the continuously variable transmission. The continuously variable transmission (T) is supported by the drive face 29 supported on the outer circumference of the input shaft 23 and the outer circumference of the output shaft 22. Between the driven face 30, the plurality of double cones 39 supported by the cone holders 31 and 56 and abutting the two face 29 and 30, the casing 1 and the cone holders 31 and 55. It is provided with the torque cam mechanism 33 provided in this. The torque cam mechanism 33 is installed so as to be inclined with the axis L on the inner wall of the casing 1 and the roller 36 provided on the cone holders 31 and 56, and the guide grooves to which the roller 36 engages ( 4 ₁ ), and when the input torque of the cone holders 31 and 56 changes, the cone holders 31 and 56 move in the direction of the axis L by the reaction force received by the roller 36 from the guide groove 4 ₁ . The shift ratio changes by moving.

Description

Continuously variable transmission

The present invention has a double cone composed of a first cone facing a drive face and a second cone facing a driven face, and the position of a contact point of the drive face and driven face relative to the first cone and the second cone is determined. The present invention relates to a continuously variable transmission in which a transmission ratio is changed by changing.

Such continuously variable transmissions are already known, for example, as described in Japanese Patent Application Laid-Open No. 47-447.

By the way, since the conventional continuously variable transmission controls the speed ratio by manual operation from the outside of the casing, there is a problem that the speed ratio cannot be changed automatically according to the driving state of the vehicle, and the driving operation is cumbersome. Further, if the driving state of the vehicle is detected by the sensor, and the actuator is controlled by the electronic control unit based on the driving state to control the speed ratio, there is a problem that the cost is increased due to the complicated structure.

This invention is made | formed in view of the above-mentioned situation, and an object of this invention is to automatically control the speed ratio of a continuously variable transmission with a simple structure.

1 is a longitudinal sectional view of a vehicle power unit;

2 is an enlarged view illustrating main parts of FIG. 1;

3 is a cross-sectional view taken along line 3-3 of FIG. 2;

4 is a cross-sectional view taken along line 4-4 of FIG. 2;

Fig. 5 is a view corresponding to Fig. 2 showing a second embodiment of the present invention.

6 is an enlarged view taken along line 6-6 of FIG. 5;

7 is an operation explanatory diagram of a torque cam mechanism;

8 is a graph for explaining the operation of the second embodiment.

* Description of the symbols for the main parts of the drawings *

1: Casing 4 ₁ : Guide groove

21: transmission spindle 26 ₁ : fixed cam surface

29: Drive Face 30: Driven Face

31: first cone holder (cone holder) 33: torque cam mechanism

36: roller (guide member) 37: double cone shaft

39: double cone 40: first cone

41: second cone 43 ₁ : guide groove

51: centrifugal mechanism 54 ₁ : movable cam surface

55: centrifugal weight 56: second cone holder (cone holder)

L: axis α: angle of inclination

In order to achieve the above object, the invention described in claim 1 is a casing, a drive face rotatably supported on the transmission spindle, a driven face rotatably supported on the transmission spindle, a cone holder freely movable along the transmission spindle, and a transmission spindle A double cone support shaft supported by the cone holder so as to follow the conical bus line centered at the center line, the first cone and the second corner sharing the bottom, and are rotatably supported by the double cone support shaft, and the first cone is driven. A torque cam comprising a double cone in contact with a face and a second cone in contact with a driven face, and a torque cam mechanism for moving the cone holder in the axial direction of the transmission main shaft according to the input torque of the cone holder. The mechanism includes a guide groove installed on one side of the casing and the cone holder so as to be inclined with respect to the axis, and the casing and the cone holder. It is installed on the other side characterized by having a guided member engaging the guide groove.

In addition, the invention according to claim 2 includes a drive face rotatably supported on the transmission main shaft, a driven face rotatably supported on the transmission main shaft, a cone holder freely movable along the transmission main shaft, and a conical busbar centered on the transmission main shaft. And a double cone support shaft supported by the cone holder, and a first cone and a second cone sharing the bottom surface so as to be rotatably supported by the double cone support shaft, the first cone abuts the drive face and the second cone. A continuously variable transmission with a double cone in which the cone abuts the driven face and a centrifugal mechanism for moving the cone holder in the axial direction of the transmission main shaft according to the input rotational speed of the transmission spindle. The centrifugal mechanism is installed on the rear side of the drive face. A fixed cam surface which is not movable in the axial direction, and is provided to face the fixed cam surface, and simultaneously with the cone holder Characterized in that with the centrifugal weights disposed between the movable group movable cam surface in the axial direction, the both cam surfaces.

The invention as set forth in claim 3 further comprises a centrifugal mechanism for moving the cone holder in the axial direction of the transmission main shaft in accordance with the input rotational speed of the transmission main shaft in addition to the configuration of claim 1, wherein the centrifugal mechanism is a rear side of the drive face. And a fixed cam surface which is provided at a position which cannot be moved in the axial direction, a movable cam surface which is provided to face the fixed cam surface, and which is movable in the axial direction together with the cone holder, and a centrifugal weight disposed between the two cam surfaces.

The invention described in claim 4 is characterized in that, in addition to the invention of claim 1, the inclination angle of the guide groove with respect to the axis is variable.

In addition, the invention described in claim 5 is characterized in that, in addition to the configuration of claim 4, the inclination angle is changed according to the torque input to the cone holder.

In addition, the invention described in claim 6 is characterized in that, in addition to the configuration in claim 4, the inclination angle is changed by a driver's command operation.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described based on the Example of this invention shown in an accompanying drawing.

1 to 4 show a first embodiment of the present invention, FIG. 1 is a longitudinal sectional view of a vehicle power unit, FIG. 2 is an enlarged view of the main part of FIG. 1, FIG. 4 is a cross-sectional view taken along line 4-4 of FIG. 2.

As shown in FIG. 1, this power unit P is mounted on a motorcycle, and includes a casing 1 for storing the engine E and the continuously variable transmission T. As shown in FIG. The casing 1 is subdivided into a center casing 2, a left casing 3 coupled to the left side of the center casing 2, and a right casing 4 coupled to the right side of the center casing 2. The crankshaft 6 supported by the center casing 2 and the left casing 3 via the pair of ball bearings 5, 5 is likewise a cylinder block supported by the center casing 2 and the left casing 3. It is connected via the connecting rod 9 to the piston 8 slidingly fitting to (7).

The crankshaft 6 is provided with a generator 10 at the left end, which is covered by a generator cover 11 coupled to the left side of the left casing 3. The drive gear 12 is supported on the right outer periphery of the crankshaft 6 to the inside of the right casing 4, and the drive gear 12 is freely rotated relative to the right end of the crankshaft 6. The crankshaft 6 is engageable by the centrifugal clutch 13.

Referring to FIG. 2, the transmission main shaft 12 of the continuously variable transmission T is fitted to the inner output shaft 22 and the outer circumference of the output shaft 22 freely with relative rotation through the needle bearing 24. It is comprised from the input shaft 23 of a sleeve shape, and the both ends of the output side 22 are hypothesized between the left casing 3 and the right casing 4. The driven gear 25 in which the input shaft 23 meshes with the drive gear 12 is fixed. The driven gear 25 has an inner gear half 26 splined to the input shaft 23, and the inner gear half body ( A plurality of rubber dampers 28. Composed so as to be able to barely rotate relative to the outer gear half 27 is engaged with the drive gear (12). When the engine torque transmitted from the drive gear 12 to the input shaft 23 via the driven gear 25 changes, the rubber damper 28... The occurrence of shock is reduced by the deformation of.

A drive face 29 having an annular contact portion 29 ₁ facing radially outward is splined to the outer circumference of the input shaft 23, and an annular contact portion facing radially inward to the outer circumference of the output shaft 22. The driven face 30 provided with 30 ₁ is supported by relative rotation freely.

The first cone holder 31 formed in a roughly conical shape is supported on the outer periphery of the boss portion 30 ₂ of the driven face 30 through the needle bearing 32 so as to be relatively rotatable and axially slidable. Referring to FIG. 3, as is apparent, the torque cam mechanism 33 which stops rotation of the first cone holder 31 with respect to the casing 1 is radially inserted into the outer circumference of the first cone holder 31. A guide groove 4 ₁ formed on the inner wall surface of the pin 34, the roller 36 axially supported by the pin 34 via the ball bearing 35, and the right casing 4 for guiding the roller 36. It is composed of The direction of the guide groove 4 ₁ is inclined by the angle α with respect to the axis L of the transmission main shaft 21.

A plurality of window holes 31 ₁ formed in the first cone holder 31. A plurality of double cone support shafts 37... This hypothesis is provided, and the double cone 39 is rotatably supported by the double cone support shafts 37 through the needle bearings 38 and 38. Double cone support shaft 37... The contact portion (30 ₁₎ each of the contact portion (29 ₁₎ and driven Face 30 per are arranged in a circle memorial line to the axis (L) of the transmission main shaft (21 ₁₎ to the center line, the drive Face 29 Y I am cutting it horizontally. Each double cone 39 is composed of a first cone 40 and a second cone 41 which share a bottom surface, and the contact portion 29 ₁ of the drive face 29 corresponds to the first cone 40. At the same time as the contact, the contact portion 30 ₁ of the driven face 30 abuts on the second cone 41.

One window hole 31 ₂ is formed in the upper part of the first cone holder 31 facing the crankshaft 6.

A first cone tooth surfaces of the driven gear 25 is housed inside of the holder 31 has the window hole (31 ₂₎ to the facing, and a window hole (31 _2), the drive gear 12 and driven gear 25 via the Is matched.

The centrifugal mechanism 51 which changes the speed ratio of the continuously variable transmission T is installed in the right side of the driven gear 25 by sliding the 1st cone holder 31 in the axial direction according to the rotation speed of the input shaft 23. The centrifugal mechanism 51 includes a sleeve 52 fixed to the outer circumference of the input shaft 23, a cam member 54 which is freely fitted to the outside of the sleeve 52 through the bush 53, and the driven gear 25. forming one of the right side surface of the internal gear half 26 fixed cam surface (26 ₁₎ and a movable cam surface (54 ₁₎ a plurality of centrifugal weights (55) disposed between formation in the left side surface of the cam member 54 ... It consists of. At the right end of the first cone holder 31, the outer circumference of the second cone holder 56 covering the centrifugal mechanism 51 is fixed with a clip 57, and the inner circumference of the second cone holder 56 has a ball bearing ( It is supported by the cam member 54 through 58.

The first cone holder 31 and the second cone holder 56 cooperate with each other to define a space surrounding the transmission main shaft 21, and the driven gear 25, the drive face 29 and the centrifugal mechanism therein. 51 is accommodated. The space is provided with one window hole 31 ₂ and a double cone 39 to which the tooth surface of the driven gear 25 faces. ... Window hole 31 ₁ supporting the. It communicates with the inner space of the casing (1) through.

The color 59 of the end joint fitting the right end of the sleeve 52 is supported on the outer circumference of the right end of the output shaft 22 through the ball bearing 60, and the right side of the ball bearing 60 is coated. It is fixed to the output shaft 22 by 61. The transmission main shaft 21 composed of the output shaft 22 and the input shaft 23 is supported by the right casing 4 via a ball bearing 62 fitting to the outer circumference of the input shaft 23. A spring 64 is arranged between the spring retainer 63 supported by the ball bearing 26 and the second cone holder 56, and the second cone holder 56 is provided by the elastic force of the spring 64. And the first cone holder 31 is urged leftward.

When the rotation speed of the input shaft 23 increases, the centrifugal weight 55... Since to the radial movement outwardly to both the cam surface (26 _{1), (54: 1)} forcing the cap member 54 is moved against the spring force of the spring 64 to the right, and the cam member (54 ), The second cone holder 56 and the first cone holder 31 connected to each other via the ball bearing 58 slide in the right direction.

An adjustment pressure cam mechanism 67 is provided between the right end of the output gear 66 which is splined to the left end of the output shaft 22 and fixed by the coater 65 and the left end of the driven face 30. As is apparent from Fig. 4, the pressure regulating cam mechanism 67 is provided with a plurality of recesses 66 ₁ formed at the right end of the output gear 66; And a plurality of concave portions 30 ₃ formed at the left end of the driven face 30. Ball 68 between. Is sandwiched between the output gear 66 and the driven face 30, and the disc spring 69 is mounted to give a load that biases the driven face 30 in the right direction. When a torque acts on the driven face 30 and a relative rotation occurs between the output gear 66, the direction in which the driven face 30 is separated from the output gear 66 by the pressure adjustment cam mechanism 67 (right direction) Is taxed).

Returning to FIG. 1, the third reduction gear 71 is rotatably supported by the left casing 3 via the ball bearing 70, and the needle bearing 72 and the ball bearing are supported by the third reduction gear 71. The left end of the output shaft 22 is supported coaxially through 73. Reduction shaft 75 is supported by the left casing 3 and the center casing 2 through the ball bearings 74 and 74 of the upper limit, and the 1st reduction gear 76 provided in the reduction shaft 75 is provided. And a second reduction gear 77 mesh with the output gear 66 and the third reduction gear 71, respectively. A drive sprocket 79 is formed in which the endless chain 78 is wound around the shaft end of the third reduction gear 71 protruding outward from the left casing 4. Therefore, the rotation of the output side 22 is the output gear 66, the first reduction gear 76, the second reduction gear 77, the third reduction gear 71, the drive sprocket 79 and the endless chain 78. It is transmitted to the driving wheel through.

The oil passage 4 ₂ laid inside the right casing 4 communicates with the oil passage 22 ₁ penetrating the inside of the output shaft 22 in the axial direction, and in this oil passage 22 ₁ the first cone is connected. Each part of the continuously variable transmission T is lubricated by oil supplied to the inner space of the holder 31 and the second cone holder 56.

Next, the operation of the embodiment of the present invention having the above-described configuration will be described.

As shown in FIG. 2, the distance A of the contact portion 29 ₁ of the drive face 29 measured at the axis L of the transmission main shaft 21 is a constant value, and the double cone support shaft 37 is provided. The distance B of the abutment portion 29 ₁ of the drive face 29 measured at is a variable value B _L , B _T. In addition, the distance C of the contact portion 30 ₁ of the driven face 30 measured by the double cone support shaft 37 becomes a variable value C _L , C _T , and the axis line of the transmission main shaft 21 ( The distance D of the contact part 30 ₁ of the driven face 30 measured by L) becomes a fixed value.

If the rotational speed of the drive face 29 is N _DR and the rotational speed of the driven face 30 is N _DN , and the transmission ratio R is defined as R = N _DR / N _DN , the transmission ratio R is R = N _DR. / N _DN = (B / A) x (D / C).

In addition, as shown in the upper half of FIG. 2, since the rotation speed of the driven gear 25 driven by the drive gear 12 is low at the low speed rotation of the engine E, the centrifugal weight 51 of the centrifugal mechanism 51 55)... The centrifugal force acting on the surface becomes small, and the second cone holder 56 and the first cone holder 31 move leftward by the elastic force of the spring 64. When the first cone holder 31 moves leftward, the contact portion 29 ₁ of the drive face 29 moves to the bottom surface side of the first cone 40 of the double cone 39 so that the distance B is the maximum value. While increasing to (B _L ), the contact portion 30 ₁ of the driven face 30 moves to the apex side of the second cone 41 of the double cone 39 so that the distance C is the minimum value C _L. Decreases.

At this time, since the distances (A) and (D) are constant values, when the distance (B) increases to the maximum value (B _L ), and the distance (C) decreases to the minimum value (C _L ), the transmission (R) Is increased to shift to LOW ratio.

On the other hand, as shown in the lower half of FIG. 2, since the rotation speed of the driven gear 25 driven by the drive gear 12 is high at the time of high speed rotation of the engine E, the centrifugal weight of the centrifugal mechanism 51 55)... The centrifugal force acting on the centrifugal force increases, and the second cone holder 56 and the first cone holder 31 move radially outward with the centrifugal force. By the action of the spring 64 to move in the right direction to resist the elastic force. When the first cone holder 31 moves in the right direction, the contact portion 29 ₁ of the drive face 29 moves to the apex side of the first cone 40 of the double cone 39 so that the distance B is the minimum value. While decreasing to (B _T ), the contact portion 30 ₁ of the driven face 30 moves to the bottom side of the second cone 41 of the double cone 39 so that the distance C is the maximum value C _T. To increase.

At this time, since the distances A and D are constant values, when the distance B decreases to the minimum value B _T , and the distance C increases to the maximum value C _T , the speed ratio R is small. It shifts to TOP ratio.

The speed ratio of the continuously variable transmission T can be changed steplessly between the (LOW) and (TOP) sides in accordance with the rotation speed of the engine E. FIG. In addition, since the speed ratio control is automatically performed by the centrifugal mechanism 51, compared with the case of installing a shift control apparatus which performs shift shifting manually by the exterior of the casing 1 or an electronic shift control apparatus. It is possible to reduce the cost and miniaturize the continuously variable transmission T by simplifying the structure.

As described above, the drive face 29 is rotated by the double cone 39... It is transmitted to the driven face 30 at a predetermined speed ratio R, and the rotation of the driven face 30 is transmitted to the output gear 66 through the pressure control cam mechanism 67. At this time, when relative rotation occurs between the output gear 66 with the torque acting on the driven face 30, the driven face mechanism 30 moves away from the output gear 66 by the pressure adjustment cam mechanism 67. Is taxed. This subordinate force cooperates with the subordinate force by the plate spring 69 to press the contact portion 29 ₁ of the drive face 29 to the first cone 40 of the double cone 39, and the driven face ( The surface pressure which press-contacts the contact part 30 ₁ of 30) with the 2nd cone 41 of the double cone 39 is produced | generated.

By the way, the biasing force by the said pressure cam mechanism 67 presses the output gear 66 to the left direction, but since the left end of the output gear 66 is fixed to the left end of the output shaft 22 by the coater 65, The pressure in the left direction is transmitted to the output shaft 22. Further, the biasing force by the pressure adjusting cam mechanism 67 presses the driven face 30 in the right direction, and the pressing force is applied to the double cone 39... At the driven face 30. To the right end of the output shaft 22 through the drive face 29, the inner gear half 26, the sleeve 52, the ball bearing 62, the collar 59, the ball bearing 60 and the coater 61. do.

Therefore, the load in which the pressure regulating cam mechanism 67 presses the output gear 66 and the driven face 30 in the horizontal direction acts as a tensile load of the output shaft 22, and the tensile load is an internal stress of the output shaft 22. Is canceled by, and the pressure load of the pressure adjustment cam mechanism 67 is not transmitted to the casing 1. Thereby, it is not necessary to reinforce the strength of the casing 1 to withstand the pressing load, thereby contributing to the weight reduction of the continuously variable transmission T. In addition, since both the drive face 29 and the driven face 30 are urged by one pressure cam mechanism 67, the drive face 29 and the driven face 30 are respectively separated by a separate pressure cam mechanism 67. Part scores and costs can be reduced compared to the case of tax.

In addition, when the continuously variable transmission T shifts, the first cone holder 31 tries to rotate around the transmission spindle 21 by the transmission torque reaction force of the drive face 29, and the transmission torque reaction force is the first. The roller 36 of the torque cam mechanism 33 supported by the cone holder 31 is prevented by engaging the right groove 4 with the guide groove 4 ₁ between the formations, and the first cone holder 31 does not rotate. Can axially slide without pressure.

In addition, when the engine torque is rapidly increased while attempting to accelerate while the vehicle is running, the transmission torque reaction force acting on the first cone holder 31 also increases as the engine torque increases. As a result, as shown in FIG. 3, the roller 36 is press-contacted to the wall surface of the inclined guide groove 4 ₁ with the load F, and the component of the load F in the direction of the guide groove 4 ₁ . The first cone holder 31 is biased to the left side (LOW ratio side) of FIG. 2 by F ₁ . That is, since the transmission ratio automatically changes to the LOW ratio side by the action of the torque cam mechanism 33, the so-called kick-down effect is exerted to effectively accelerate the vehicle.

In addition, since the transmission cam mechanism 33 performs the shift ratio control at the time of the kick-down automatically according to the change of the engine torque, without providing a special shift control device, the cost reduction and the continuously variable transmission are made by the reduction of the structure. Miniaturization of (T) can be achieved. Moreover, the change characteristic of a transmission ratio can be easily adjusted only by changing the shape of the guide groove 4 ₁ of the torque cam mechanism 33. FIG.

Further, the lower portions of the first cone holder 31 and the second cone holder 56 of the continuously variable transmission T are immersed in coin oil at the bottom of the casing 1, and the double cone 39... ... Window hole 31 ₁ supporting the. And the window hole 32 ₂ facing the tooth surface of the driven gear 25 is at a position higher than the oil surface OL of the oil (see FIG. 2), so that the first cone holder 31 and the second cone holder 56 are located. A large amount of oil does not penetrate into the inner space of the bottom of the casing (1). Moreover, even if lubricating oil is supplied to the inner space of the 1st cone holder 31 and the 2nd cone holder 56 in the oil passage 22 ₁ which penetrates the inside of the output shaft 22, the oil will be driven gear 25 Since it is thrown out by the centrifugal force by the rotation of the), only the minimum oil necessary for lubrication is maintained in the inner space of the first cone holder 31 and the second cone holder 56.

The driven gear 25 only stirs a small amount of oil, and can minimize power loss due to unnecessary oil agitation. In addition, since the oil is blocked by the first cone holder 31 and the second cone holder 56, there is no need to provide a special oil blocking member, and the number of parts is reduced.

As described above, by arranging the driven gear 25 in the space defined by the first cone holder 31 and the second cone holder 56, the driven gear 25 is arranged out of the space. Not only can the oil agitation resistance be reduced, but also the drive face 29 and the centrifugal mechanism 51 are disposed on the left and right sides of the driven gear 25 so that the continuously variable transmission T can be effectively utilized. It can be made compact.

5 to 8 show a second embodiment of the present invention, FIG. 5 is a view corresponding to FIG. 2, FIG. 6 is an enlarged view of line 6-6 of FIG. 5, and FIG. 7 is a torque cam. Fig. 8 is a graph for explaining the operation of the mechanism.

The second embodiment adds an improvement to the torque cam mechanism 33 of the first embodiment. As is apparent from Figs. 5 and 6, the torque cam mechanism 33 of the second embodiment is formed on the bottom wall of the right casing 4; It is provided with the guide member 43 slidably supported by the pin 42 extended in an up-down direction. Guide member 43 is provided with a pin 42, the arm (43 ₂₎ sheathed and at the same time provided with a roller groove (43 ₁₎ of the U-cuts that once the roller 36 is engaged with the side insert, the other end of the , a spring 44, 44 is provided with a pair between a spring seat _{(42), (42)} formed at a front end and a right casing (4) of the arm (43 _2). When no torque is transmitted to the first cone holder 31, the guide member 43 is biased by the springs 44, 44 at a position in FIG. 6 parallel to the transmission main shaft 21.

Therefore, when the first cone holder 31 attempts to rotate around the transmission spindle 21 by the transmission torque reaction of the drive face 29 when the CVT is shifted, the guide member 43 is transmitted by the transmission torque reaction force. ) Swings around the pin 42 and stops at the position in FIG. 7A suitable for the spring force of the springs 44 and 44. Forming inclination angle with respect to the axis (L) of the groove wherein rollers (43 ₁₎ the transmission main shaft 21 in Fig α is not constant and varies depending on the transmitted torque. Specifically, when the transmission torque increases, the inclination angle α also increases, making it difficult to shift to the TOP side, which increases the speed of rotation.

Figure 8 (A) is a roller groove ₍₄₁₎ angle of inclination written by showing the transmission characteristics of the first embodiment of the continuously variable transmission (T) of α is fixed, 8 (B) also in the roller groove (43 ₁₎ The inclination angle α shows the speed change characteristic of the continuously variable transmission T of the second embodiment. As is apparent from the figure, according to the continuously variable transmission T of the second embodiment in which the inclination angle α is variable, since the inclination angle α becomes small when the transmission torque is small, the shift to the TOP side is performed at a low engine speed. In addition, it can provide quieter driving and reduce fuel consumption. On the other hand, when the transmission torque is large, since the inclination angle α becomes large, shifting to the TOP side is performed at a high engine speed, and more powerful running is possible.

Conversely, when torque is transmitted from the output shaft 22 side to the input shaft 23 side, i.e., during engine brake, the guide member 43 swings in the reverse direction around the pin 42, and the springs 44, 44 It stops at the position of FIG. 7 (B) suitable for the elasticity of Also in this case, the angle of inclination forms with respect to the axis (L) of the roller groove (43 ₁₎ the transmission main shaft (21) (α) is not constant, which increases with an increase in the transmission torque. Therefore, since the inclination angle α increases when the engine brake is suddenly lowered, the shift to TOP becomes difficult, so that the engine brake performance is improved, and when the engine brake is flat, the inclination angle α decreases. Shifting to TOP tends to be performed, and excessive engine brake is suppressed.

As mentioned above, although the Example of this invention was described above, various design modifications can be made in this invention in the range which does not deviate from the summary.

For example, in the torque cam mechanism 33 of the first and second embodiments, the roller 36 is provided on the first cone holder 31 side, and the roller grooves 4 ₁ and 43 are provided on the casing 1 side. ₁ ), but the positional relationship may be reversed. In addition, in the second embodiment, the guide member 43 is automatically rocked in accordance with the transmission torque, which can be rocked by a hydraulic actuator or an electronic actuator or by the driver's manual operation based on the driver's switch operation. In this way, the shift characteristic can be arbitrarily set according to the driver's preference.

As described above, according to the invention described in claim 1, the guide cam provided so that the torque cam mechanism is inclined with respect to one axis of the casing and the cone holder, and the other side of the casing and the cone holder, which is engaged with the guide groove, Since it has a guide member, it is possible to automatically control the speed ratio of the continuously variable transmission in accordance with the torque transmitted to the cone holder without performing manual shift operation and providing a complicated electrical control device of the structure. In addition, by appropriately setting the shape of the guide groove, the shift characteristic can be easily adjusted.

In addition, according to the invention of claim 2, the centrifugal mechanism is provided on the back side of the drive face, and is not movable in the axial direction, and the movable cam surface is provided so as to face the fixed cam surface and is movable in the axial direction together with the cone holder. Since there is a centrifugal weight disposed between the two cam surfaces, the transmission ratio of the continuously variable transmission is automatically controlled according to the input rotational speed of the transmission main shaft without performing a manual shift operation and without installing a complicated electrical control device. It becomes possible. In addition, the rational layout of the centrifugal mechanism can reduce the axial dimension of the continuously variable transmission.

Further, according to the invention of claim 3, the transmission ratio of the continuously variable transmission can be automatically controlled according to the torque transmitted to the cone holder and the input rotation speed of the transmission main shaft, so that the continuously variable transmission suitable for a vehicle can be provided at a low price. .

According to the invention described in claim 4, since the inclination angle of the guide grooves provided on one of the casing and the cone holder is variable with respect to the axis, the shift characteristic of the continuously variable transmission can be arbitrarily adjusted.

Further, according to the invention of claim 5, since the inclination angle changes in accordance with the torque input to the cone holder, the shift characteristic can be automatically adjusted in accordance with the driving state without the driver performing any special operation.

According to the invention described in claim 6, since the inclination angle is changed by the driver's command operation, the shift characteristic according to the driver's preference can be selected.

Claims (6)

A casing 1, a drive face 29 rotatably supported on the transmission spindle 21, a driven face 30 rotatably supported on the transmission spindle 21, and a cone freely movable along the transmission spindle 21. The holders 31 and 56, the double cone support shaft 37 supported by the cone holders 31 and 56 so as to follow the conical bus line centering the transmission main shaft 21, and the first cone 40 sharing the bottom surface. ) And a second cone 41 is rotatably supported by the double cone support shaft 37, and the first cone 40 abuts the drive face 29 and at the same time the second cone 41 driven face. A torque cam for moving the cone holders 31 and 56 in the direction of the axis L of the transmission main shaft 21 in accordance with the input cones of the double cone 39 and the cone holders 31 and 56 in contact with the 30. With a continuously variable transmission having a mechanism 33, the torque cam mechanism 33 is inclined with respect to the axis L on one side of the casing 1 and the cone holders 31, 56. Groping guide groove _(41, 43 ₁₎ and a casing (1) and the cone holder is installed to the other side of the (31, 56) with the guided member 36 to engage with the guide groove _(41, 43 ₁₎ CVT, characterized in that. Drive face 29 rotatably supported on the transmission spindle 21, drive face 30 rotatably supported on the transmission spindle 21, and cone holders 31 and 56 moveable along the transmission spindle 21; And a double cone support shaft 37 supported by the cone holders 31 and 56 so as to follow the conical busbar centering the transmission main shaft 21 as a center line, and the first cone 40 and the second cone sharing the bottom surface. 41 is rotatably supported by the double cone support shaft 37, the first cone 40 abuts the drive face 29, and at the same time the second cone 41 is driven by the driven face 30 Stepless endlessly provided with a double cone 39 in contact and a centrifugal mechanism 51 for moving the cone holders 31 and 56 in the direction of the axis L of the transmission main shaft 21 in accordance with the input rotational speed of the transmission main shaft 21. As a transmission, the centrifugal mechanism 51 is provided on the rear side of the drive face 29 and is fixed to the fixed cam surface (not movable in the direction of the axis L) ( 26 _1), and is installed so as to face the fixed cam surface (26 ₁₎ cone holder (31, 56) and the axis (L) moves in a direction of a movable cam surface (54 _1), the amount the cam surfaces (26 _1, 54 with ₁ ) continuously variable transmission having a centrifugal weight (55) disposed between. 2. A gearing mechanism (51) according to claim 1, characterized in that the cone holder (31) and (56) are moved in the direction of the axis (L) of the transmission main shaft (21) in accordance with the input rotational speed of the transmission main shaft (21), the centrifugal mechanism 51 is installed on the rear side of the drive Face 29 is provided to be opposed to the axis (L) stationary cam surface can not be moved in the direction (26 ₁₎ and a fixed cam surface (26 _1), the axis (L And a centrifugal weight (55) disposed between the movable cam surface (54 ₁ ) movable in the) direction and the cam surfaces (26 ₁ , 54 ₁ ). 2. The continuously variable transmission according to claim 1, wherein the inclination angle [alpha] of the guide groove (43 ₁ ) with respect to the axis (L) is made variable. 5. The continuously variable transmission according to claim 4, wherein said inclination angle (α) changes in accordance with a torque input to the cone holder (31, 56). 5. The continuously variable transmission according to claim 4, wherein the inclination angle is changed by a driver's command operation.