JPH0650425A - Continuously variable transmission - Google Patents

Abstract

PURPOSE:To maintain the neutral conditions of a continuously variable transmission stably which is composed of the combination of a transmission pulley mechanism and a differential gear mechanism. CONSTITUTION:On the back of a mavable sieve for each transmission pulley 16, 31 in a transmission pulley means 15 a pair of cam means changing the winding dia. of belt while contacting/separating between both pulleys 16, 31 to/from each other are disposed, and an interlocking means 44 varying the shift ratio while interlocking both cam means so as to change the belt winding dia. of each pulley to the different direction is arranged. In the control force tranmission path from a control lever 46 to the interlocking means 44 a non- sensitive part 50 is installed to enable no tranmission from the control force of the lever 46 to the interlocking means under the neutral conditions of a continously variable transmission.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a continuously variable transmission,
In particular, it relates to a combination of a speed change pulley mechanism and a differential gear mechanism.

[0002]

2. Description of the Related Art As an example of a belt type continuously variable transmission,
A fixed sheave fixed to each of the pair of rotating shafts arranged in parallel to each other so as to rotate integrally and non-slidably with respect to each rotating shaft, and a V-shaped member between the fixed sheave and the fixed sheave to the rotating shaft. In addition to having a speed change pulley formed of a movable sheave that is arranged to face each other so as to form a belt groove and is rotatably integrated and slidably supported, a V belt wound between the belt grooves of both speed change pulleys is provided. It is known to include a speed change pulley mechanism that has a variable speed ratio between the rotary shafts by changing the effective radius with respect to the V belt by moving the movable sheave in the axial direction.

By the way, heretofore, in Japanese Patent Laid-Open No. 62-11815.
As disclosed in Japanese Patent Publication No. 9, a continuously variable transmission including the above-described speed change pulley mechanism and a planetary gear mechanism (differential gear mechanism) as a speed change gear mechanism has been proposed.

[0004]

In the continuously variable transmission equipped with the speed change pulley mechanism and the differential gear mechanism, when the output shaft is rotated from the stopped state using the differential gear mechanism, the power transmission path is changed. Is divided into two parts, the driving power and the circulation power. That is, in the closed circuit type differential gear device, one of the three gear elements of the differential gear mechanism is connected to the output shaft, and the rotational speed of the remaining one gear element of the differential gear mechanism is adjusted by adjusting the gear ratio of the pulley mechanism. By changing the rotation direction and the rotation speed between the gear element and the remaining other gear elements, the rotation direction and the rotation speed of the output side gear element, that is, the output shaft are determined. However,
At that time, drive power and circulation power are generated as power,
The output power is the driving power minus the circulating power.
Which of the two power transmission paths from the input shaft to the output shaft is the drive power path or the circulation power path is determined by the angular velocity of the gear element in the differential gear mechanism,
The driving power path has a larger angular velocity.

In the continuously variable transmission including the combination of the speed change pulley mechanism and the differential gear mechanism, the rotation speed of the output shaft can be switched in the forward and reverse directions with respect to the input shaft to perform the speed change. There is an advantage that a separate switching mechanism is unnecessary.

However, on the other hand, there is a problem that it is difficult to stably maintain the neutral state in which the rotation speed of the output shaft is zero. That is, in order to stop the rotation of the output shaft by using the differential gear mechanism, two gear elements other than the gear element connected to the output shaft, for example, a planetary gear mechanism (differential gear mechanism) having a pinion carrier as an output portion. In the case of), it is necessary to match the angular velocities of the ring gear and the sun gear with each other, but the matching is done only at points, and it is extremely difficult to achieve this by friction transmission of a belt such as a speed change pulley mechanism. It was

The present invention has been made in view of the above circumstances, and an object thereof is to provide a speed change pulley by providing a predetermined means for a continuously variable transmission including a combination of a speed change pulley mechanism and a differential gear mechanism. It is to be able to maintain a stable neutral state while having a mechanism.

[0008]

In order to achieve the above object, according to the invention of claim 1, the fixed and movable sheaves of each speed change pulley are arranged so as to be located on opposite sides with respect to the axial direction, An interlocking mechanism that moves the movable sheaves so that they contact and separate from the opposing fixed sheaves is opposite to each other, and in the neutral state, the interlocking mechanism is prevented from being restrained from the outside.

Specifically, the continuously variable transmission of the present invention is
It is provided with first and second rotating shafts arranged in parallel with each other, a speed change pulley mechanism and a differential gear mechanism. The speed change pulley mechanism rotatably drives both rotary shafts in a variable speed manner, and includes a pair of speed change pulleys in which fixed sheaves and movable sheaves are respectively arranged and supported on the respective rotary shafts in opposite directions, The belt wound between both speed change pulleys and the rear side of the movable sheave of each speed change pulley are arranged on the back side of the movable sheave. A pair of drive mechanisms, an interlocking mechanism that interlocks the two drive mechanisms such that the belt winding diameters of the two speed change pulleys change in mutually opposite directions, and changes the gear ratio between the two pulleys; and the interlocking mechanism. The belt thrust is pushed by pressing the switching operation section to be operated and the slack side span of the belt between the both transmission pulleys so that the tension on the slack side span is greater than the tension generated corresponding to the gear ratio between the pulleys. To And a tension mechanism to produce.

Further, the differential gear mechanism has first to third gear elements connected to each other, and the first gear element is connected to the first rotating shaft, while the second gear element is connected to the first rotating shaft. It is connected to the shaft.

One of the first rotary shaft and the third gear element serves as an input portion and the other serves as an output portion, and the output portion is normally rotated with respect to the input portion by the switching operation of the switching operation portion. , And is switched to a neutral state or a reverse rotation state to shift gears.

Further, a dead band portion is provided in the operation force transmission path from the switching operation portion to the interlocking mechanism so that the operating force of the switching operation portion cannot be transmitted to the interlocking mechanism in the neutral state.

According to a second aspect of the present invention, the dead zone portion is provided on one of the switching operation portion and the interlocking mechanism, the engaging portion including a long groove or a long hole, and on the other of the switching operation portion and the interlocking mechanism. A locking member that movably engages with the engaging portion by a predetermined amount.

[0014]

With the above construction, the first aspect of the invention is the first aspect.
Since the speed change pulley mechanism and the differential gear mechanism are arranged in parallel between the second rotary shaft and the second rotary shaft, the power input using one of the first rotary shaft or the third gear element of the differential gear mechanism as an input unit is , One of the speed change pulley mechanism or the differential gear mechanism is used as a drive power path and the other is transmitted as a circulating power path,
The other of the first rotating shaft or the third gear element is output as an output unit. Then, by operating the switching operation section to change the speed ratio of the speed change pulley mechanism, the output section is switched to the forward rotation state, the neutral state or the reverse rotation state with respect to the input section.

In the above-mentioned speed change pulley mechanism, when one of the drive mechanisms is operated by the operation of the switching operation portion to move the movable sheave of one speed change pulley in the axial direction, the other drive mechanism also operates accordingly. The movable sheave of the other speed change pulley moves by the operation opposite to the contacting / separating operation of the movable sheave with respect to the fixed sheave in the above one speed change pulley. Be changed.

At this time, the drive mechanisms are arranged such that the fixed and movable sheaves of the speed change pulleys are located on the opposite sides with respect to the axial direction, and the movable sheaves are opposed to each other from the rear side. Since both drive mechanisms are linked by the interlocking mechanism, when the continuously variable transmission is in the neutral state,
Both of the speed change pulleys in the speed change pulley mechanism are drive side pulleys (or driven side pulleys), the belt tension distribution between the two pulleys is balanced, and the belt thrust forces are the same.

However, when the continuously variable transmission changes from the neutral state to the forward rotation side or the reverse rotation side, and the belt winding diameter of one pulley becomes larger than the other, the belt tension distribution in both pulleys becomes unbalanced. Then, the belt thrust of the pulley on the side where the belt winding diameter is increased becomes larger than that on the side where the belt winding diameter is decreased, and the difference in the belt thrust increases as the load increases. That is, when the continuously variable transmission changes from the neutral state even a little, due to the difference in the belt thrust, the winding diameter of the pulley on the side where the belt winding diameter increases increases so as to decrease, and The restoring force that returns to the neutral state acts on. And
In the operation force transmission path from the switching operation unit to the interlocking mechanism,
Since the dead zone that makes it impossible to transmit the operating force of the switching operation unit to the interlocking mechanism in the neutral state is positively provided, the restoration to the neutral state is not restricted, and this stabilizes the neutral state. Can be maintained.

According to a second aspect of the invention, the dead zone portion is provided on one of the switching operation portion and the interlocking mechanism, the engaging portion being a long groove or a long hole, and on the other of the switching operation portion and the interlocking mechanism. Since it is configured with a locking member that movably engages with the engaging portion by a predetermined amount, the operation force of the switching operation portion cannot be transmitted to the interlocking mechanism by the movement of the locking member at the engaging portion. The dead zone is easily obtained with a simple structure.

[0019]

Embodiments of the present invention will be described below with reference to the drawings.

(Embodiment 1) FIGS. 2 and 3 show the overall structure of a continuously variable transmission according to Embodiment 1 of the present invention. In these drawings, reference numeral 1 denotes a casing divided into a plurality of parts, and inside thereof, first and second rotating shafts 2, 2 arranged in parallel to each other.
3 is rotatably supported. The first rotary shaft 2 constitutes an input shaft as an input section, and the second rotary shaft 3 constitutes an intermediate shaft.

In the casing 1, the second rotating shaft 3
A planetary gear mechanism 4 as a differential gear mechanism arranged on the right end portion of the above is accommodated, and a speed change pulley mechanism 15 for drivingly connecting the rotating shafts 2 and 3 by a V belt B so that the speed can be changed.

The planetary gear mechanism 4 has a sun gear 5 as a second gear element fixed to the second rotating shaft 3 so as to rotate integrally therewith.
And a plurality of pinions 6, 6, ... Which mesh with the sun gear 5.
And a pinion carrier 7 as a third gear element that is rotatably supported by the second rotating shaft 3 and carries the pinions 6, 6, ...
.. and a ring gear 9 as a first gear element that meshes with the inner circumference. The ring gear 9 is meshed on the outer periphery with a gear 10 axially supported by the casing 1.
Reference numeral 0 is meshed with a gear 12 which is rotatably attached to the front end of the first rotary shaft 2 through a similar gear 11. The pinion carrier 7 constitutes an output portion, and an output gear 8 is integrally fixed to the right end of the pinion carrier 7, and the output gear 8 is drivingly connected to an output shaft (not shown).

On the other hand, the speed change pulley mechanism 15 has a first speed change pulley 16 arranged on the left end of the first rotating shaft 2. The first speed change pulley 16 includes a flange-shaped fixed sheave 17 fixed to the first rotating shaft 2 integrally and non-slidably by a boss portion 17a, and a boss portion 17a of the fixed sheave 17 (first rotation shaft). The shaft 2) comprises a flange-shaped movable sheave 18 slidably and relatively rotatably supported by a boss portion 18a so as to face the fixed sheave 17, and a belt is provided between these sheaves 17, 18. The groove 19 is formed.

On the other hand, a second speed change pulley 31 having the same diameter as the first speed change pulley 16 is provided on the left end of the second rotary shaft 3. The second speed change pulley 31 has the same structure as the first speed change pulley 16, and has a boss portion 32a on the second rotary shaft 3.
A flange-shaped fixed sheave 32 which is fixed integrally with and fixed in a non-sliding manner, and a boss portion 32a of the fixed sheave 32.
The (second rotary shaft 3) is slidable by the boss portion 33a so as to face the fixed sheave 32 in a direction opposite to the direction in which the movable sheave 18 faces the fixed sheave 17 in the first speed change pulley 16. It is composed of a flange-shaped movable sheave 33 which is coupled so as to be rotatable relative to each other, and a belt groove 34 is formed between these sheaves 32, 33.

The V-belt B is wound between the belt groove 19 of the first speed change pulley 16 and the belt groove 34 of the second speed change pulley 31.
Each of the movable sheaves 18 and 33 of 31 is a fixed sheave 1
The belt winding diameters of the pulleys 16 and 31 are changed by bringing them into contact with and separating from the pulleys 7 and 32. For example, when the movable sheave 18 of the first speed change pulley 16 is brought closer to the fixed sheave 17 and the movable sheave 33 of the second speed change pulley 31 is separated from the fixed sheave 32, the belt winding diameter of the first speed change pulley 16 becomes By making it larger than the two-speed pulley 31,
The rotation of the first rotary shaft 2 is accelerated and transmitted to the second rotary shaft 3. On the other hand, conversely, the movable sheave 18 of the first transmission pulley 16
Is separated from the fixed sheave 17, and the second transmission pulley 3
When the first movable sheave 33 is brought close to the fixed sheave 32, the belt winding diameter of the first speed change pulley 16 is reduced,
By increasing the belt winding diameter of the second speed change pulley 31, the rotation of the first rotary shaft 2 is decelerated and transmitted to the second rotary shaft 3.

The movable sheave 18 of the first transmission pulley 16
A torque cam mechanism 20 is arranged between the boss portion 18 a and the first rotating shaft 2. This torque cam mechanism 20
For example, a pair of torque pins 21 and 21 formed of bolts projecting from the outer peripheral surface of the first rotating shaft 2 at diametrically opposite positions.
And cam grooves 22 and 22 formed on the boss portion 18a of the movable sheave 18 and engaged with the pins 21 and 21, respectively. The respective cam grooves 22 are predetermined in a direction parallel to the rotation axis. The lead cam is inclined by the lead angle, and the torque sheave mechanism 20 is actuated to move the movable sheave 18 to the fixed sheave 1 when transmitting power in a forward state where the continuously variable transmission is frequently used.
It is designed to be separated from 7.

A first speed change pulley 1 is mounted on the first rotary shaft 2.
The movable sheave 18 on the back side of the movable sheave 18 in FIG.
A first cam mechanism 23 is provided as a drive mechanism for bringing the stationary sheave 17 into and out of contact with the stationary sheave 17. The cam mechanism 23 has a cylindrical cam 25 on the boss portion 18a of the movable sheave 18 which is externally fitted and supported by a bearing 24 so as to be relatively rotatable and axially movable integrally. This cam 25
A pair of inclined cam surfaces 25a, 25a (only one is shown) are formed on the end surface opposite to the first speed change pulley 16 at equal angular intervals (180 ° intervals) in the circumferential direction, and on the outer circumference. As shown in FIG. 3, a turning lever 26 is provided so as to turn integrally.

Further, on the back side of the cylindrical cam 25, there are arranged rollers 27, 27 as cam followers that roll by contacting the respective cam surfaces 25a, and each roller 27 is a shaft fixed to the casing 1. It is rotatably supported by 28.

On the other hand, on the second rotary shaft 3, on the rear side of the movable sheave 33 in the second speed change pulley 31, there is provided a second drive mechanism for bringing the movable sheave 33 into and out of contact with the fixed sheave 32. A cam mechanism 35 is provided. The second cam mechanism 35 has the same structure as the first cam mechanism 23, and has the bearing 3 on the boss portion 33 a of the movable sheave 33.
6 has a cylindrical cam 37 that is externally fitted and supported so as to be capable of relative rotation and move integrally in the axial direction. A pair of inclined cam surfaces 3 is provided on the end surface of the cam 37 opposite to the second speed change pulley 31.
7a and 37a (only one is shown) are formed at equal angular intervals in the circumferential direction, and a rotating lever 38 (see FIG.
(See) is provided so as to integrally rotate. Also, the cylindrical cam 3
Rollers 39, 39 are provided on the rear surface side of the roller 7 so as to come into contact with the respective cam surfaces 37a and roll. The rollers 39 are rotatably supported by the casing 1 via a shaft 40.

As shown in FIG. 3, one end of a link 42 is connected to the tip of the rotary lever 26 of the first cam mechanism 23 via a pin 41, and the other end of the link 42 is the second cam mechanism. The rotary lever 38 is connected to the tip of the rotary lever 38 via a pin 43, and the rotary levers 26, 38, the link 42, and the pins 41, 43 form an interlocking mechanism 44. By this interlocking mechanism 44, each cam mechanism 23,
The cams 25 and 37 in 35 are linked to each other and rotated around the boss portions 18a and 33a of the movable sheaves 18 and 33,
By rolling the rollers 27 and 39 on the respective cam surfaces 25a and 37a, the movable sheaves 18 and 33 are moved in the axial direction to be brought into contact with and separated from the fixed sheaves 17 and 32, and the belt groove The effective radii of 19, 34, that is, the belt winding diameters of the pulleys 16, 31 are made variable to change the gear ratio between the first and second rotating shafts 2, 3.

Further, as shown in FIG. 1, in the interlocking mechanism 44 of the speed change pulley mechanism 15, an operation lever 46 as a switching operation portion is connected to the tip of the rotating lever 38 of the second cam mechanism 35 via a rod 45. Has been done. The operation lever 46 swings back and forth around the shaft 47 between the forward position, the neutral position and the reverse position, and its shift pattern is as shown in FIG. 4 when moving from the reverse position to the forward position via the neutral position. At the neutral position, it is once moved to the left as shown in. The rod 45 is connected to the lower end of the operation lever 46, and the switching mechanism of the operation lever 46 actuates the interlocking mechanism 44 to change the speed ratio of the speed change pulley mechanism 15 to change the speed ratio of the planetary gear mechanism 4. Pinion Carrier 7
(Output part) is in a normal rotation state with respect to the first rotary shaft 2 (input part),
The speed is changed by switching to the neutral state or the reverse rotation state, and in the neutral state, the belt winding diameter of the first speed change pulley 16 is 108 mm, and the belt winding diameter of the second speed change pulley 31 is 72 mm, for example. It is configured.

Specifically, a pin 48 as a locking member is provided at the tip of the rotary lever 38 of the second cam mechanism 35.
On the other hand, an engaging portion 49 that engages with the pin 48 is formed at the end of the rod 45.
Is a long groove (or long hole) elongated in the length direction of the rod 45 by a predetermined dimension, and when the operating lever 46 is in the neutral position by the engaging portion 49 and the pin 48,
A dead zone portion 50 is configured to make it impossible to transmit the operating force of the operating lever 46 to the interlocking mechanism 44.

The first and second speed change pulleys 16,
Of the pair of spans of the belt B stretched between the belts 31, the span on the loose side is pressed outward from the inner surface of the belt B.
A tension mechanism 51 is provided that generates a belt thrust by applying a tension to the belt. This tension mechanism 51
As shown in an enlarged view in FIGS. 5 and 6, the cylindrical guide 53 integrally attached to the casing 1 around the second rotary shaft 3 by the bolts 52 and 52, and the guide 5
3 is attached to the tip of the arm 54b of the arm 54, and an arm 54 including a boss 54a that is swingably fitted to and supported by the outer periphery of the boss 54 and an arm 54b that is provided on the outer peripheral surface of the boss 54a. A shaft 55 extending parallel to the second rotating shafts 2 and 3 and a tension roller 56 rotatably supported by the shaft 55 and having a length in the axial direction smaller than the belt width are provided. Further, a lever portion 54c (see FIGS. 5 and 6) is provided on the outer periphery of the boss portion 54a of the arm 54 on the opposite side of the arm 54 portion. As shown in FIG. 4, one end of a spring 57 is connected to the tip of the lever portion 54c, and the other end of the spring 57 is connected via a push-pull wire 58 to, for example, an intermediate portion of the operating lever 46. The left and right movement of the operating lever 46 in the neutral position causes the arm 54 to swing around the second rotating shaft 3 via the spring 57, so that the outer peripheral surface of the tension roller 56 causes the loose side span of the belt B to change from the inner surface side. When the span of the belt B on the upper side of FIG. 3 is on the loose side in the forward movement state of the continuously variable transmission, the arm 54 is rotated clockwise in FIG. 3 by the extension force of the contracted spring 57. While pressing the inner surface of the loose side of the belt B, when the lower span of the belt B in FIG.
The springs 5 that have been extended by rotating them counterclockwise with
The inner surface of the slack side of the belt B is pressed by the contracting force of 7, and the shaft of the tension roller 56 is placed on the plane connecting the axial centers of the first and second rotating shafts 2 and 3 during the switching between the forward and reverse states. It is positioned so that its outer peripheral surface is separated from the inner surface of the belt B. Then, the rotational biasing force of the spring 57 with respect to the arm 54 is set so that the tension roller 56 presses the loose side span of the belt B with a tension larger than the maximum tension generated in the loose side span, The belt thrust is generated by this tension.

Further, as shown in FIGS. 5 and 6, a pair of pins 59, is formed on the inner peripheral surface of the boss portion 54a of the arm 54.
59 are provided so as to be opposed to each other in the diametrical direction, while guide grooves 60, 60 that engage with the pins 59, 59 are formed on the outer periphery of the guide 53. As shown in FIG. 7, each of the guide grooves 60 basically extends in the circumferential direction, but one half of the guide groove 60 is bent from the central position so as to extend in the axial direction toward the end. The tension roller 56 is moved in the axial direction in response to the swing of the arm 54. For example, in the reverse drive state of the continuously variable transmission, the tension roller 56 is moved to the neutral position shown in FIG. 8B as shown in FIG. 8C. Although it is rotated at the same position as the state, in the forward state, as shown in FIG. 8A, the tension roller 56 is rotated while being moved axially rightward from the neutral position.

Next, the operation of the above embodiment will be described. Since the speed change pulley mechanism 15 and the planetary gear mechanism 4 are arranged in parallel in the power transmission path between the input / output portions of the continuously variable transmission, the power input from the first rotary shaft 2 during the operation of the speed change apparatus. Is transmitted to the speed change pulley mechanism 15, the gears 12 to 10 on the first rotating shaft 2 and the planetary gear mechanism 4, and then is output as output power from the output gear 8 of the pinion carrier 7 in the planetary gear mechanism 4. .

Specifically, when the operating lever 46 is positioned at the neutral position, the pinion carrier 7 of the planetary gear mechanism 4 is stopped rotating and the continuously variable transmission is in the neutral state. In this neutral state,
The belt winding diameter of the first transmission pulley 16 of the transmission pulley mechanism 15 is 108 mm, the belt winding diameter of the second transmission pulley 31 is 72 mm, and the gear ratio is 0.66.
6 and a predetermined value, the first and second speed change pulleys 16, 3
Both 1 are the driving side (or the driven side). Also,
4, assuming that the operating lever 46 is on the right side in the neutral position, the arm 54 of the tension mechanism 51 is at the counterclockwise turning end position in FIG. 3, and the tension roller 56 causes the belt to move due to the contracting force of the spring 57. The lower span in FIG. 3 of B is pressed from the inner surface side.

At this time, the fixed sheaves 17, 32 and the movable sheaves 18, 33 of the speed change pulleys 16, 31 are arranged so as to be located on the opposite sides with respect to the axial direction, and the movable sheaves 18, 33 are respectively arranged. A cam mechanism 23 for bringing the fixed sheaves 17 and 32 into and out of contact with each other from the back side,
Since the gear 35 is linked by the interlocking mechanism 44, in the neutral state, as shown in FIG. 11A, both the transmission pulleys 16 and 31 are on the drive side (or the driven side). , 31, the tension distribution of the belt B is balanced, and the belt thrusts are equal to each other. And
Change from this neutral state to the forward rotation side or the reverse rotation side,
As shown in FIG. 11B or FIG. 11C, when the belt winding diameter of one of the first and second speed change pulleys 16 and 31 is larger than the other, the tension of the belt B on both pulleys 16 and 31. The distribution is unbalanced, and the belt thrust force of the pulley 16 (or 31) on the side where the belt winding diameter is increased becomes larger than that of the pulley 31 (or 16) on the side where the belt winding diameter is decreased. It increases as the load increases. This means that when the continuously variable transmission changes from the true neutral state even a little, the pulley 16 on the side where the belt winding diameter is increased due to the difference in the belt thrust.
(Or 31) changes so as to reduce the winding diameter,
A restoring force that automatically returns to the neutral state acts. Further, in this embodiment, the dead band portion 50 that prevents the operation force of the operation lever 46 from being transmitted to the interlocking mechanism 44 in the neutral state is provided in the operation force transmitting path from the operation lever 46 to the interlocking mechanism 44. Therefore, when trying to return to the neutral state, the pin 48 in the dead zone portion 50 is freely moved by the engaging portion 49, and the restoration to the neutral state is not restrained, thus stabilizing the neutral state. Can be maintained.

Specifically, according to the present inventor, as an example in which the speed change ratio i of the speed change pulley mechanism 15 is i = 0.666,
As described above, in addition to the case where the belt winding diameters of the first and second speed change pulleys 16 and 31 are 108 mm and 72 mm, respectively, the belt winding diameters are 78 mm, 52 mm and 13 respectively.
Assuming three cases of 8 mm, 92 mm, 183 mm, and 122 mm, the gear ratio when the movable sheaves 18 and 33 of both speed change pulleys 16 and 31 are axially moved by ± 1 mm in the neutral state. Was considered. The result is shown in FIG. From FIG. 9, even with the same gear ratio,
It can be seen that the change amount of the gear ratio decreases as the belt winding diameter increases.

The shaded portion in FIG. 9 illustrates the range of the gear ratio corresponding to the dead zone in the neutral state set by the dead zone section 50, and the gear ratio i changes depending on the neutral position of the operating lever 46. However, if i = 0.
As long as it is within the range of 62 to 0.712, a stable neutral state can be maintained.

Further, FIG. 10 shows that the range of the gear ratio (i =
Movable sheave 1 for setting 0.62-0.712)
The necessary movement amounts of the movable sheaves 18 and 33 are shown to increase as the belt winding diameter increases.

Cam mechanism 2 of each of the above-mentioned speed change pulleys 16 and 31
The rotation levers 26 and 38 of the links 3 and 35 are linked to each other.
Since it is linked by two, the output ratio of the pinion carrier 7 of the planetary gear mechanism 4, that is, the output of the continuously variable transmission is changed to the forward or reverse state by changing the speed ratio of the speed change pulley mechanism 15 by switching the operation lever 46. And the rotation speed can be increased and changed.

That is, when the operation lever 46 is positioned at the forward position from the neutral state, the operation lever 46 is connected to the rotary lever 38 on the outer periphery of the cam 37 of the second cam mechanism 35, and thus the forward position is reached. In the switching state of, the cam 37 has its cam surfaces 37a, 37a.
While rolling the cam rollers 39, 39 respectively, the boss portion 3 of the movable sheave 33 in the second speed change pulley 31 is rotated.
Rotate around 3a in one direction. As a result, the cam surface 37a is pushed by the roller 39, and the cam 37 moves the second rotary shaft 3
The movable sheave 33 that moves upward and moves integrally with the cam 37 via the bearing 36 moves in the same direction to move the stationary sheave 3
Approach 2 As a result, the second speed change pulley 31 is closed and the belt winding diameter is 72 in the neutral state.
The maximum belt diameter is 120 mm and the maximum belt diameter is 120 mm. Due to the increase in the belt winding diameter, the V belt B is pulled toward the second speed change pulley 31 side.

At the same time, the operating lever 46 is
Of the second speed change pulley 31
In synchronization with the movement of the movable sheave 33 of the first cam mechanism 23.
The cam 25 rotates on the first rotary shaft 2 in the same one direction as the cam 37 of the second cam mechanism 35. The rotation of the cam 25 eliminates the pressing force on the cam roller 27. Therefore, due to the tension of the belt B moving to the side of the second speed change pulley 31, the movable sheave 18 connected to the cam 25 and the bearing 24 via the bearing moves along the first rotary shaft 2 in the direction away from the fixed sheave 17. Move and both sheaves 1
Due to the separation of 7 and 18, the first transmission pulley 16 is opened and the belt winding diameter is reduced from 108 mm in the neutral state to a minimum of 60 mm. As a result, the belt winding diameter of the second speed change pulley 31 becomes larger than that of the first speed change pulley 16, the rotation of the first rotary shaft 2 is accelerated, and the second rotary shaft 3 is rotated.
Be transmitted to. With this gear ratio, the pinion carrier 7
The rotation direction of the pinion carrier 7 becomes a normal rotation state with respect to the first rotation shaft 2, and the gear ratio is further changed, so that
It is possible to increase the rotational speed in the forward rotation direction of the vehicle, that is, the forward speed.

At this time, the input power is set as a drive power path through the gears 12 to 10 and the ring gear 9 of the planetary gear mechanism 4 to the pinion carrier 7, and the sun gear 5 of the planetary gear mechanism 4 makes a second rotation. The path extending from the shaft 3 to the speed change pulley mechanism 15 is transmitted as a circulating power path, and the second speed change pulley 31 becomes a drive side pulley, while the first speed change pulley 16 becomes a driven side pulley. The span is on the loose side. Since the speed change pulley mechanism 15 serves as a circulating power path in this way, it is possible to transmit a circulating power that is smaller than the driving power to the belt B, and the belt B can be used even at the time of high output in a forward state where it is frequently used. B
The transmission load of can be reduced.

Further, since the shift pattern of the operating lever 46 is set so as to move in the left-right direction at the neutral position, the operating lever 46 operated to the forward position once moves to the left side at the neutral position and then moves forward. Move in the direction. Since the lever portion 54c of the arm 54 of the tension mechanism 51 is connected to the operating lever 46 via the wire 58 and the spring 57, the wire 58 is moved to the lever portion 54 as the operating lever 46 moves to the left.
3, the arm 54 is rotated in the clockwise direction in FIG. 3, whereby the tension roller 56 moves upward away from the lower belt span in FIG. 3, and the tension roller 56 moves in the clockwise direction in the arm 54. At the rotation end position, the contracting force of the spring 57 presses the loose side span on the upper side of the belt B in FIG. 3 from the inner surface side.

A pair of pins 59 and 59 are provided on the inner periphery of the boss portion 54a of the arm 54 so as to project therefrom.
Is engaged with the guide groove 60 of the guide 53, the guide groove 60 guides the pin 59 to move the arm 54 in the axial direction as it rotates clockwise in FIG. Along with this, the position of the tension roller 56 also moves in the axial direction from the state of FIG. 8B to the state of FIG. 8A.

The arm 54 is rotationally biased by the biasing force of the spring 57 of the tension mechanism 51, and the tension roller 56 at the tip of the arm 54 pushes the inner surface of the slack side span of the belt B. Is given,
Since this tension is larger than the maximum tension generated in the slack side span, this belt tension causes the pulley 16 of the belt B,
A wedge effect is generated on 31 to generate thrust, and this thrust transmits power between the pulleys 16 and 31 via the belt B.

On the other hand, when the operation lever 46 is positioned at the reverse position, the first lever is in the switching state to the reverse position.
The cam 25 of the cam mechanism 23 rotates in the other direction around the boss portion 18a of the movable sheave 18 of the first transmission pulley 16 while rolling the cam roller 27 on each cam surface 25a. As a result, the cam surface 25a is pushed by the roller 27, and the cam 25 moves on the first rotary shaft 2.
The movable sheave 18, which is integrally movable, moves in the same direction to approach the fixed sheave 17. As a result, the first speed change pulley 1
6 is closed and the belt winding diameter is increased from 108 mm in the neutral state to a maximum of 120 mm. Due to the increase in the belt winding diameter, the V-belt B causes the first speed change pulley 16 to move.
Attracted to the side.

Further, the cam 37 of the second cam mechanism 35 moves to the second position as the operation lever 46 is switched to the reverse position.
The rotary shaft 3 is rotated in the same other direction as the cam 25 of the first cam mechanism 23. The rotation of the cam 37 eliminates the pressing force on the cam roller 39. Therefore, due to the tension of the belt B moving to the side of the first speed change pulley 16, the movable sheave 33 connected through the cam 37 and the bearing 36 to the second sheave 32 is separated from the fixed sheave 32.
As the sheaves 32, 33 are moved on the rotary shaft 3, the second transmission pulley 31 is opened by the separation of the sheaves 32, 33, and the belt winding diameter is reduced from 72 mm in the neutral state to a minimum of 60 mm. As a result, the belt winding diameter of the first speed change pulley 16 becomes larger than that of the second speed change pulley 31, and the rotation of the first rotary shaft 2 is accelerated and transmitted to the second rotary shaft 3. With this gear ratio, the rotation direction of the pinion carrier 7 becomes, for example, a reverse rotation state with respect to the first rotation shaft 2, and the rotation speed of the pinion carrier 7 in the reverse rotation direction, that is, the reverse speed is increased by further changing the gear ratio. You can

At this time, contrary to the above-mentioned forward movement, the input power is set as a drive power path from the speed change pulley mechanism 15 or the second rotary shaft 3 to the sun gear 5 of the planetary gear mechanism 4.
From the pinion carrier 7 of the planetary gear mechanism 4 to the pinion 6,
6, through ring gear 9 and gears 10 to 12
The first transmission pulley 16 serves as a drive pulley, the second transmission pulley 31 serves as a driven pulley, and the lower span of the belt B in FIG. Be on the side.

Further, the operation lever 46 operated to the reverse position once moves rightward at the neutral position and then moves in the reverse direction. As the operating lever 46 moves to the right, the wire 58 pulls the lever portion 54c to rotate the arm 54 counterclockwise in FIG. 3, which causes the tension roller 56 to move from the upper belt span in FIG. The tension roller 56 separates and moves downward, and presses the slack side span of the belt B on the lower side in FIG. 3 from the inner surface side by the extension force of the spring 57 at the counterclockwise rotating end position of the arm 54.

Further, due to the guiding action of the guide groove 60 with respect to the pin 59 on the inner circumference of the boss portion 54a of the arm 54, the arm 54 rotates counterclockwise in FIG. 3 but does not move in the axial direction, and tension is applied. The position of the roller 56 changes from the state shown in FIG. 8B to the state shown in FIG. 8C.

Therefore, in this embodiment, the axial length of the tension roller 56 in the tension mechanism 51 is smaller than the belt width, and the tension roller 56 presses the inner surface of the belt span to apply the belt thrust. Therefore, the tension roller 5 with a large outer diameter
While using 6 to reduce the bending ratio of the belt span,
The outer periphery of the tension roller 56 is attached to each of the speed change pulleys 16, 31.
Since the axial distance between the first and second rotary shafts 2 and 3 can be shortened by arranging them in the belt grooves 19 and 34, the continuously variable transmission can be made compact.

Further, as described above, the lateral movement of the operation lever 46 at the neutral position causes the arm 54 of the tension mechanism 51 to rotate and press the inner surface of the span on the loose side of the belt B. Even if the slack side span of the belt B changes due to the reverse relationship between the drive pulley and the driven side between the speed change pulleys 16 and 31 due to the switching of the reverse drive, the span on the slack side can always be pressed. Moreover, since these switching operations are performed by operating the operation lever 46 for switching between forward and backward movements, it is possible to switch between forward and backward movements and press the slack side span of the belt B with one operating lever 46.

Furthermore, as the arm 54 of the tension mechanism 51 rotates in response to the change in the loosening side span of the belt B, the pins 59, 59 on the inner circumference of the boss portion 54a of the arm 54 are rotated.
Is guided by the guide grooves 60, 60 on the outer periphery of the guide 53,
Since the arm 54 moves in the axial direction, the width of the tension roller 56 is smaller than the belt width as described above, and the belt B has its winding groove changed while the winding diameter is changed by opening and closing the speed change pulleys 16 and 31. Even if the tension rollers 56 are axially moved along the side surfaces of the fixed sheaves 17, 34 on the side of the fixed sheaves 17, 32, the tension roller 56 does not deviate from the position of the belt B in the axial direction and cannot press the loose side span. It can be pressed stably.

Further, as described above, when the continuously variable transmission shifts from the neutral state to the forward state, the belt winding diameter of the first transmission pulley 16 in the transmission pulley mechanism 15 is, for example, 108 mm to a minimum of 60 mm, and the second transmission pulley 16 has a second winding diameter. The belt winding diameter of the speed change pulley 31 is 72 mm to a maximum of 120 mm
The belt winding diameter of the first transmission pulley 16 changes from 108 mm to a maximum of 120 mm, and the belt winding diameter of the second transmission pulley 31 changes from 72 mm to a minimum of 60 mm. The amount of change in the belt winding diameter from the neutral state to the forward state is larger than that in the reverse state. As described above, the gear ratio of the speed change pulley mechanism 15 in the neutral state (the belt winding around the speed change pulley is wound so that the circulating power smaller than the driving power is transmitted to the belt B of the speed change pulley mechanism 15 in the frequently used forward state. Since the diameter is set, only by providing the torque cam mechanism 20 only on the first speed change pulley 16 side, a low operating force by the torque cam mechanism 20 can be reliably obtained.

Moreover, the torque cam mechanism 20 is the first side which is driven by the circulating power when the continuously variable transmission is in the forward drive state.
Since it is provided on the speed change pulley 16 side, even if the lead angle of the torque cam groove 22 is constant, the required belt thrust force according to the speed change ratio can be easily taken out.

For example, when the amount of change in the gear ratio of the transmission pulley mechanism 15 from the neutral state to the forward state is equal to the amount of change in the reverse state, as shown in FIG. It is necessary to provide the torque cam mechanisms 20 and 29. At that time, each torque cam groove 22
Is bent at the neutral line LN corresponding to the neutral line of the continuously variable transmission, the lead angle is set to a predetermined angle on one side of the neutral line LN, and the lead angle is set to 0 on the other side. The sides where the lead angle is 0 are made opposite by the torque cam mechanisms 20 and 29.

Thus, as shown in FIG. 13, when one of the torque cam mechanisms 20 (or 29) is in the operating state, the other torque cam mechanism 29 (or 20) has a lead angle of the torque cam groove 22 of 0. Then, only the function of key combination is lost. Therefore, the torque cam mechanism 2
It is possible to cope with the reverse rotation of the drive side and the driven side of the speed change pulley mechanism 15 while reducing the speed change operation force by increasing the belt thrust force by 0, 29.

(Embodiment 2) In the above embodiment, the arm 54 of the tension mechanism 51 is rotated by the lateral movement of the operation lever 46 at the neutral position to press the inner surface of the span on the loose side of the belt B. However, the tension mechanism 51 may be modified as shown in FIG.

That is, FIG. 14 shows a second embodiment of the present invention, in which the tensioning mechanism 51 has a second
The casing 1 around the rotary shaft 3 has two arms 54, 54 that are swingably supported by a boss portion 54a. Each of the arms 54 is different from the first embodiment and the operating lever 46 is provided.
Is not connected to. Arm portion 54b of each arm 54
A tension roller 56 capable of pressing the inner surface of each span of the belt B is rotatably supported at the tip end thereof via a shaft 55 parallel to the first and second rotation shafts 2 and 3. Also,
Spring supports 65, 65 that are swingable around the shaft 55 are attached to the tip of each arm 54b. One end of a spring 66 is integrally connected to the one spring receiver 65, and the other end of the spring 66 is integrally connected to the other spring receiver 65. Both arms are extended by the extension biasing force of the spring 66. The tension rollers 56 are respectively urged to rotate the belts 54, 54 in a direction in which the angular interval between them becomes large (the upper arm 54 in the clockwise direction and the lower arm 54 in the counterclockwise direction in FIG. 14). The inner surface of each span of B is constantly pressed.

Therefore, in this embodiment, the tension roller 5 at the tip of each arm 54 is in the neutral state.
6 presses the inner surface of each span of the belt B with the same pressing force. The neutral state is switched to the forward state, the second rotary shaft 3 becomes the drive side, and the first rotary shaft 2
14 becomes the driven side, the lower span of the belt B in FIG. 14 becomes the tension side span, and the upper span becomes the slack side span, as shown by the solid line in FIG. The pressing lower tension roller 56 is pushed back to the upper side in the figure, which compresses the spring 66, and the upper tension roller 56 causes the inner surface of the slack side of the belt B by a predetermined pressing force. Press.

On the other hand, when the first rotary shaft 2 is on the drive side and the second rotary shaft 3 is on the driven side, the upper span is the tension side span and the lower span is the loose side span in the figure. Then, as shown by the phantom line in the figure, the upper tension roller 56 pressing the inner surface of the tension side span is pushed back to the lower side, whereby the spring 66 is compressed and the lower tension roller 56 is compressed. Presses the inner surface of the slack side span of the belt B with a predetermined pressing force.

In this way, the tension roller 56 at the tip of each arm 54 constantly presses the inner surface of each span of the belt B, and the return of the tension side span provides a pressing force for the slack side span. As described above, the slack side span can be automatically pressed in response to switching between forward and reverse without connecting the arm 54 to the operation lever 46.

In each of the above embodiments, the first and second
If there is a margin in the distance between the rotating shafts 2 and 3, it is sufficient to increase the axial length of the roller 56 of the tension mechanism 51, thereby moving the roller 56 in the axial direction of the rotating shafts 2 and 3. There is no need to do this.

In each of the above embodiments, the planetary gear mechanism 4 is used.
Although the ring gear 9 is connected to the first rotation shaft 2, the pinion carrier 7 may be connected to the first rotation shaft 2 and the ring gear 9 may be used as the output unit. Further, the sun gear 5 may be used as an output part, in short, one of the sun gear 5, the pinion carrier 7 and the ring gear 9 of the planetary gear mechanism 4 is the first rotating shaft 2 and the other is the second rotating shaft 3. Each connected,
The rest may be used as the output unit.

Further, it is possible to use the pinion carrier 7 of the planetary gear mechanism 4 as the power input section and the first rotary shaft 2 as the output section.

[0068]

As described above, according to the invention of claim 1, a continuously variable transmission having a combination of a speed change pulley mechanism and a differential gear mechanism between a pair of rotary shafts is provided.
On the rear side of the movable sheaves of the speed change pulleys in the speed change pulley mechanism, a pair of movable sheaves are moved toward and away from opposite fixed sheaves in opposite directions to change the belt winding diameter of the speed change pulleys. A drive mechanism is provided, and an interlocking mechanism that changes the gear ratio between both pulleys by interlocking both drive mechanisms so that the belt winding diameters of the two speed change pulleys change in opposite directions is provided. In the operation force transmission path from the switching operation unit of, the stepless transmission is positively provided with a dead zone portion that makes it impossible to transmit the operation force of the switching operation unit to the interlocking mechanism in the neutral state of the continuously variable transmission. Uses the characteristic of automatically returning to the neutral state due to the difference in belt thrust due to the imbalance of belt tension distribution between both pulleys when changing from the neutral state to the forward rotation side or the reverse rotation side , That the restoration to its neutral state is bound it can be prevented by the dead band section, thus the neutral state of the continuously variable transmission apparatus comprising a combination of variable speed pulley mechanism and the differential gear mechanism can be maintained stably.

According to the second aspect of the present invention, the dead zone portion is provided on one of the switching operation portion and the interlocking mechanism, the engaging portion being a long groove or a long hole, and on the other of the switching operation portion and the interlocking mechanism. The dead band portion can be easily obtained with a simple structure because it is configured with the locking member that movably engages with the engaging portion by a predetermined amount.

[Brief description of drawings]

FIG. 1 is a front view showing a dead zone portion of a continuously variable transmission according to a first embodiment of the present invention.

FIG. 2 is a cross-sectional view showing an overall configuration of a continuously variable transmission.

FIG. 3 is a front view schematically showing an overall configuration of a continuously variable transmission.

FIG. 4 is a diagram schematically showing a mechanism for switching a belt span pressing position of a tension roller in a tension mechanism.

FIG. 5 is a front view of an arm and a guide of the tension mechanism.

FIG. 6 is a sectional view of an arm and a guide of the tension mechanism.

FIG. 7 is a development view showing a guide groove on the outer circumference of the guide in the tension mechanism.

FIG. 8 is an explanatory diagram showing a movement state of a tension roller in the tension mechanism in the axial direction.

FIG. 9 is a characteristic diagram illustrating a setting range of an appropriate neutral width with respect to a belt winding diameter.

FIG. 10 is a characteristic diagram illustrating a movable sheave movement amount corresponding to an appropriate neutral width.

FIG. 11 is a schematic front view showing a change in belt winding diameter with respect to a pulley when the belt is stabilized in a neutral state.

FIG. 12 is a diagram schematically showing a modified example of a continuously variable transmission equipped with a torque cam mechanism on both transmission pulley sides.

FIG. 13 is a characteristic diagram showing a change in belt gear ratio with respect to a rotation direction in a modified example of the continuously variable transmission.

FIG. 14 is a front view showing a speed change pulley mechanism according to a second embodiment of the present invention.

[Explanation of symbols]

 2 1st rotating shaft 3 2nd rotating shaft 4 Planetary gear mechanism (differential gear mechanism) 5 Sun gear (2nd gear element) 7 Pinion carrier (3rd gear element) 9 Ring gear (1st gear element) 15 Speed change pulley mechanism 16 , 31 Speed change pulley 17, 32 Fixed sheave 18, 33 Movable sheave 19, 34 Belt groove 20, 29 Torque cam mechanism 23, 35 Cam mechanism (drive mechanism) 25, 37 Cylindrical cam 25a, 37a Cam surface 27, 39 Roller 42 Link 44 Interlocking mechanism 46 Operating lever (switching operation part) 48 Pin 49 Engaging part 50 Dead zone part 51 Tension mechanism 53 Guide 54 Arm 56 Tension roller 58 Wire 59 Pin 60 Guide groove B Transmission belt

Claims (2)

[Claims] 1. A first and a second rotating shafts arranged in parallel with each other, and a pair of speed change pulleys, wherein a fixed sheave and a movable sheave are arranged and supported on the respective rotating shafts so as to be opposite to each other. A belt wound between the speed change pulleys and a rear side of the movable sheave of each speed change pulley, and the movable sheave is brought into contact with and separated from a fixed sheave facing each other, and a belt winding diameter of the speed change pulley. A pair of drive mechanisms for changing the gear ratio, a link mechanism for linking the drive mechanisms so that the belt winding diameters of the shift pulleys change in opposite directions, and a gear ratio between the pulleys, and the link mechanism. Press the switching operation part that operates the mechanism and the loose side span of the belt between the two speed change pulleys so that the tension becomes greater than the tension generated on the loose side span corresponding to the speed change ratio between the pulleys. Emit belt thrust And a speed change pulley mechanism for drivingly connecting both rotary shafts in a variable speed manner, and first to third gear elements connected to each other, the first gear element being connected to the first rotary shaft. On the other hand, the second gear element includes a differential gear mechanism connected to the first rotation shaft, and one of the first rotation shaft and the third gear element serves as an input portion and the other serves as an output portion. The switching operation section is configured to switch the output section to the forward rotation state, the neutral state, or the reverse rotation state with respect to the input section to shift gears, and the operation from the switching operation section to the interlocking mechanism is performed. In the force transmission path,
A continuously variable transmission, comprising: a dead zone portion that disables transmission of the operating force of the switching operation portion to the interlocking mechanism in the neutral state. 2. The continuously variable transmission according to claim 1, wherein the dead zone portion is an engaging portion formed of a long groove or a long hole provided in one of the switching operation portion and the interlocking mechanism, and the other of the switching operation portion and the interlocking mechanism. And a locking member that is movably engaged with the engaging portion by a predetermined amount, and a continuously variable transmission.