JPH0248779B2 - HENSOKUSOCHI - Google Patents

Description

Detailed Description of the Invention (Field of Industrial Application) The present invention relates to a transmission used in tillers, agricultural machinery, etc. This invention relates to an improvement in a device that changes the gear ratio between a pair of rotating shafts by sliding on the rotating shafts.

(Prior Art) Conventionally, as a belt-type transmission using belt transmission, a pair of rotating shafts arranged in parallel to each other has been provided with a transmission that rotates integrally with and cannot slide relative to each of the rotating shafts. A variable pulley consisting of a fixed sheave and a movable sheave that is disposed facing each other so as to form a V-shaped belt groove between the movable sheaves and rotatably and slidably supported on each rotating shaft. At the same time, a belt member is wound between the belt grooves of both variable pulleys, and the movable sheave of each variable pulley is moved in the axial direction to approach and separate from the fixed sheave, and the belt is wound around the belt groove between both the sheaves. It is well known that the transmission ratio between both rotating shafts is changed by making the effective radius of the member variable. Usually, drive control of the movable sheave in the variable pulley is performed using hydraulic pressure. However, when using this hydraulic pressure, hydraulic piping and the like are required, and furthermore, the drive control of the movable shake becomes complicated, and the device configuration becomes large-scale.

On the other hand, conventional methods for mechanically driving the movable shaft of such a variable pulley have been proposed, for example, as shown in Japanese Patent Application Laid-Open No. 59-62760, in which a male threaded tube is attached to the rotary shaft so that it cannot slide but can rotate freely. At the same time, a female threaded tube that is externally fitted and screwed onto this male threaded tube is attached to a movable shaft of a variable pulley on a rotating shaft so that it can move integrally and rotatably in the axial direction. The effective radius of the variable pulley is variably adjusted by loosely fitting into the guide groove and rotating the male threaded tube with a servo motor to screw feed the female threaded tube, thereby changing the distance between the fixed sheave and the movable sheave on the variable pulley. Something like this has been proposed.

(Problem to be Solved by the Invention) However, in this proposal, the output of the servo motor as an actuator is used to screw feed the female thread cylinder and drive the movable sheave of the pulley. There is a problem that the structure becomes complicated and the cost increases because an expensive servo motor is used.

Therefore, the present applicant previously proposed a method that is supported on the rotating shaft and integrally connected to a movable shaft in the variable pulley so as to be able to move in the axial direction by being threaded by relative rotation with the rotating shaft. A screw member and a speed change mechanism that rotates the screw member relative to a rotating shaft are provided, and the movable shaft is driven by the rotational force of the rotating shaft, thereby simplifying and simplifying drive control for the movable shaft. We are proposing a method that can be used even with an inexpensive structure.

By the way, in a transmission device using such a variable pulley mechanism, during a speed change in which the gear ratio between the two rotating shafts is variably adjusted, for example, to ensure safety, the transmission of rotation between the two rotating shafts is quickly transmitted. It is desirable to be able to shut it off quickly and reliably. Therefore,
Utilizing the structure of the variable pulley mechanism, at least one of the fixed sheave or the movable sheave in one of the variable pulleys is moved back in a direction away from the opposing sheave, thereby reducing the tension of the belt member and slowing the rotation between the two rotation axes. By providing an emergency clutch mechanism that cuts off the transmission, it is possible to easily and inexpensively cut off the transmission of rotation between the two rotating shafts without requiring a separate dedicated clutch mechanism at the time of an emergency stop during gear shifting. Conceivable.

However, if the fixed sheave on the variable pulley is moved back and the emergency clutch mechanism is activated while both rotating shafts are rotating at high speed, the belt member, which had been rotating under high tension, will As the tension decreases, it swells in a circular shape due to centrifugal force and hits the belt cover member and other peripheral equipment placed close to the belt member, resulting in the outer peripheral surface (back surface) of the belt member being rubbed. This may cause problems such as abnormal wear and damage to peripheral equipment.

The present invention has been made to solve such problems, and its purpose is to prevent the belt from bulging into a circular shape due to a decrease in the tension of the belt member due to the operation of the emergency clasp mechanism as described above. The purpose is to prevent the member from directly hitting the peripheral equipment, thereby reliably avoiding abnormal wear on the outer circumferential surface of the belt member and damage to the peripheral equipment.

(Means for Solving the Problem) In order to achieve this object, the solution of the present invention is to provide a regulating member at a position related to the rotation range of the belt member to reduce the tension during rotation. The belt member, which tends to swell in a circular shape as a result of the movement, is brought into contact with the regulating member to avoid the belt member from bulging out in a circular shape.

Specifically, the configuration of the present invention is such that the movable sheave is brought into contact with the fixed sheave and is wound between the two shafts, which are mounted on two rotating shafts on the input side and the output side that are arranged parallel to each other. A variable pulley mechanism having a pair of variable pulleys that can adjust the effective radius with respect to the belt member to be hung, and a relative rotation difference between the above-mentioned input-side rotation shaft and rotating a movable sheave in the variable pulley on the input-side rotation shaft. The present invention assumes a transmission device equipped with a transmission mechanism that changes the transmission ratio between both rotating shafts by sliding on the shaft.

With respect to this premise, at least one of the fixed sheave and the movable sheave in at least one of the variable pulleys on the input side or the output side is expanded so that the tension of the belt member becomes incapable of transmitting rotation. An emergency clutch mechanism is provided that slides into sliding contact with the opposing sheave on the opposite side so as to lower the clutch.

Furthermore, the emergency clutch mechanism is located outside a portion of the belt member that is not wrapped around the pulley in a plane passing through the belt member and outside the movement range of the belt member that moves during the speed change of the gear ratio between the rotating shafts. The present invention is characterized in that a regulating member is provided that contacts the outer circumferential surface of the belt member, which expands into a circular shape as the tension decreases during operation.

(Function) With this configuration, in the present invention, when the two rotating shafts are rotating, by operating the transmission mechanism using the relative rotational difference with the input side rotating shaft,
The movable sheave in the variable pulley on the input rotating shaft is slid on the rotary shaft and moved toward and away from the fixed sheave, changing the effective radius with respect to the belt member and adjusting the gear ratio between both rotating shafts. .

When the transmission of rotation between the two rotary shafts is interrupted during such a speed change, the operation of the emergency clutch mechanism causes at least one of the fixed or movable sheave of at least one variable pulley to slide away from the opposing sheave. The movement of the sheaves widens the distance between the two sheaves, lowers the tension in the belt member, and thereby interrupts the transmission of rotation between the two rotating shafts. Therefore, since at least one of the fixed and movable shafts is moved backward to interrupt the transmission of rotation between the two rotating shafts, a dedicated clutch mechanism is not required, and costs can be reduced accordingly. It turns out.

In that case, as the sheave moves backward, the belt member whose tension has decreased tries to swell into a circular shape due to centrifugal force, but the belt member is not wrapped around the pulley of the belt member in the plane passing through the belt member. Since the regulating member is provided outside the area where the belt member moves during the gear ratio change between the rotating shafts, the belt member does not swell into a circular shape due to the regulation by the regulating member. As a result, abnormal wear on the outer circumferential surface of the belt member and damage to peripheral equipment of the belt member can be reliably avoided.

Furthermore, since the regulating member is disposed outside the movement range of the belt member that moves during the speed change of the gear ratio between the rotating shafts, it does not come into contact with the belt member during normal speed changes.

(Example) Hereinafter, an example of the present invention will be described based on the drawings.

FIG. 1 shows the overall configuration of an embodiment in which the present invention is applied to a transmission device in a tiller, etc., and 1 is an input shaft as one rotating shaft in the present invention. (2) is drivingly connected to the Further, reference numeral 2 denotes an output shaft as the other rotating shaft disposed parallel to the input shaft 1, and this output shaft 2 is connected to a drive wheel (not shown) of a tiller or the like. A drive pulley 3 as a variable pulley is provided on the input shaft 1, and the drive pulley 3 includes a flange-shaped fixed sheave 4 which is rotationally integrally keyed to the input shaft 1 at a boss portion 4a. A flange-shaped movable sheave 5 is spline-coupled to the input shaft 1 at a boss portion 5a so as to be slidably and rotatably integral with the input shaft 1 so as to face the fixed sheave 4.
A belt groove 6 having a substantially V-shaped cross section is formed between the two sleeves 4 and 5.

On the other hand, a driven pulley 7 as a variable pulley having the same configuration as the drive pulley 3 is provided on the output shaft 2 . That is, this driven pulley 7 includes a flange-shaped fixed sheave 8 that is rotatably and non-slidably fixed to the output shaft 2, and a fixed sheave 8 that is connected to the fixed sheave 4 of the drive pulley 3 on the input shaft 1. It consists of a flange-shaped movable sheave 9 that is slidably and rotatably spline-coupled to the output shaft 2 so as to face the movable sheave 5 in a direction opposite to that of the movable sheave 5. A belt groove 10 having a substantially V-shaped cross section is formed. In addition, the driven pulley 7
A spring seat 11 is integrally fixed to the output shaft 2 on the rear side of the movable shaft 9, and the movable shaft 9 is attached in the direction toward the fixed shaft 8 between the spring seat 11 and the rear surface of the movable shaft 9. Two types of springs 12a and 12b, large and small, are packed together. A V-belt 13 as a belt member is wound between the belt groove 6 of the drive pulley 3 and the belt groove 10 of the driven pulley 7, and the movable sheave 5 of the drive pulley 3 is connected to the fixed sheave 4. When the movable sheave 5 of the drive pulley 3 approaches the fixed sheave 4, the effective radius of the drive pulley 3 and the driven pulley 7 with respect to the V-belt 13 is variably adjusted.
By increasing the effective radius of the V-belt 13, the movable sheave 9 of the driven pulley 7 is moved by the spring 12.
By making the effective radius of the driven pulley 7 smaller than that of the driving pulley 3 by separating it from the fixed sheave 8 against the urging force of When the movable sheave 5 is separated from the fixed sheave 4, the effective radius of the driving pulley 3 is made small, and the movable sheave 9 of the driven pulley 7 is moved by the tension of the V-belt 13 to the fixed sheave 8 by the biasing force of the spring 12. By making the effective radius of the driven pulley 7 larger than that of the driving pulley 3, the input/output shafts 1, 2
A variable pulley mechanism 14 is configured to reduce the gear ratio between the two.

An auxiliary screw member 15 having a male threaded portion 15a on the outer circumference of the input shaft 1 on the side opposite to the fixed sheave 4 with respect to the movable sheave 5 in the driving pulley 3
are fixed as a pair, and a cylindrical screw member 16 is externally fitted onto the outer peripheral male threaded portion 15a of the auxiliary screw member 15, and this screw member 16 is connected to the drive pulley 3.
The screw member 16 is connected to the boss portion 5a of the movable shaft 5 via a bearing 17 so as to be relatively rotatable and movable in the axial direction, and by rotating the screw member 16 relative to the auxiliary screw member 15, that is, the input shaft 1, The screw member 16 is threaded together with the movable shaft 5 so as to be movable in the axial direction of the input shaft 1. For example, when the screw member 16 is rotated relative to the input shaft 1 in the deceleration direction, the screw member 16
is moved in the direction in which the movable sheave 5 approaches the fixed sheave 4 (leftward in the figure), and conversely, the screw member 16
When the input shaft 1 is rotated relative to the input shaft 1 in the speed increasing direction, the screw member 16 is moved in the direction in which the movable sheave 5 moves away from the fixed sheave 4 (to the right in the figure).

Further, on the input shaft 1, a first V-belt pulley 18 is rotatably fixed on an auxiliary screw member 15 located on the opposite side of the drive pulley 3 with respect to the screw member 16. On the other hand, on the output shaft 2, on the side opposite to the spring seat 11 with respect to the driven pulley 7, there is a substantially cylindrical sleeve 19 with a bearing 20,
The sleeve 19 has a second V-belt pulley 22 having a smaller diameter than the first V-belt pulley 18 at the end opposite to the spring seat 11. The V belt pulleys 18 and 22 are fixed to rotate together, and there is a V belt between the two V belt pulleys 18 and 22.
A belt 23 is wrapped around it. Further, a first toothed pulley 24 having a larger effective radius than the second V-belt pulley 22 is rotatably fixed to the end of the sleeve 19 on the spring seat 11 side. Further, a cylindrical member 25 having a flange-like operating portion 25a is disposed around the screw member 16 on the input shaft 1 so as to be movable in the axial direction concentrically with the input shaft 1. Cylindrical member 2
A second toothed pulley 26 having a smaller diameter than the first toothed pulley 24 is supported on the outer peripheral surface of the toothed pulley 5 so as to be non-slidable and relatively rotatable via a bearing 27.
A timing belt 28 is wound between the second toothed pulley 26 and the first toothed pulley 24, and the above-mentioned belt transmission structure causes the second toothed pulley 26 on the threaded member 16 to Pulley 26 is connected to input shaft 1
It is designed to be rotated in the same direction as that and at a faster rotational speed. Note that the first toothed pulley 24 has an outer periphery so that the timing belt 28 does not come off even if the second toothed pulley 26 moves in the axial direction as the cylindrical member 25 moves in the axial direction. The belt wrapping surface is set to a wide width.

A disc-shaped friction ring 29 is integrally fixed to the side surface of the second toothed pulley 26 opposite to the drive pulley 3. Further, a flange-shaped friction part 16a that can come into contact with the friction ring 29 on one side is integrally formed on the outer periphery of the screw member 16, and on the other side of the friction part 16a, the other side of the friction part 16a is formed. A contactable brake plate 30 is arranged, and the screw member 16 can be moved by an external operation.
By bringing one of the friction ring 29 of the second toothed pulley 26 or the control plate 30 into contact with the friction portion 16a of the screw member 16, the screw member 16 is rotated relative to the input shaft 1 in the speed increasing direction or the decelerating direction. When the control plate 30 is brought into contact with the friction portion 16a of the screw member 16 to brake its rotation, the screw member 16 is rotated relative to the input shaft 1 in the deceleration direction, thereby causing the screw member 16 to rotate against the input shaft 1. The movable sheave 5 is threaded in the direction toward the fixed sheave 4 by screwing with the male threaded portion 15a of the integrated auxiliary screw member 15, increasing the effective radius of the drive pulley 3, while the friction portion 16a of the screw member 16 Input shaft 1
When the friction ring 29 that is rotating at a faster speed is brought into contact and its rotation is increased, the screw member 16 is moved by rotating the screw member 16 relative to the input shaft 1 in the speed increasing direction. A transmission mechanism 31 is configured in which the sheave 5 is threaded in a direction away from the fixed sheave 4 to reduce the effective radius of the drive pulley 3.

Furthermore, the fixed sheave 4 in the drive pulley 3 is fixed with respect to the input shaft 1 in order to adjust the gear ratio between the input and output shafts 1 and 2. It is supported so as to be slidable a predetermined distance in the direction away from the movable shield 5 (to the left in the figure).

Also, a boss portion 4a located on the opposite side of the movable sheave 5 in the fixed sheave 4 of the driving pulley 3
A cylindrical passive cam member 32 having a cylindrical cam surface 32a is supported in a relatively rotatable and slidable manner via a bearing 33, and this passive cam member 3
2 is held in a non-rotatable state by a support lever mechanism 34. Further, on the input shaft 1 on the side opposite to the drive pulley 3 of the passive cam member 32, there is a cylindrical cam surface 3 that contacts the cam surface 32a of the passive cam member 32.
A cylindrical drive cam member 35 having a diameter 5a is relatively rotatable via a bearing 46, that is, the input shaft 1
An operating lever 36 is provided on the outer circumferential surface of the driving cam member 35, and by operating the operating lever 36, the driving cam member 35 is moved to the input shaft. By rotating the driven cam member 32 once and reducing the pressing force against the passive cam member 32, the fixed sheave 4 of the drive pulley 3 is slid from the reference position to the side opposite to the movable sheave 5 by the tension of the V-belt 13. the V-belt 13 by increasing the distance between it and the movable shaft 5.
An emergency clutch mechanism 37 is configured to reduce the tension of the clutch to the point where rotation cannot be transmitted.

Further, as a feature of the present invention, as shown in FIG. 2, between the pulleys 3 and 7, there is a V-belt 13 which tends to swell into a circular shape due to the decrease in tension accompanying the operation of the emergency clutch mechanism 37. A regulating member 38 made of a cylindrical pin that contacts the outer circumferential surface of the V-belt 13 to regulate the movement range of the V-belt 13 is disposed. Parallel to the input/output shafts 1, 2 outside the part of the V-belt 13 that is not wrapped around the pulleys 3, 7 and outside the movement range of the V-belt 13 that moves during the gear ratio change between the input/output shafts 1, 2 is fixedly supported.

Note that 39 is a bearing provided on the boss portion 4a of the fixed sheave 4 corresponding to the bottom of the belt groove 6 of the drive pulley 3, and moves to the bottom of the belt groove 6 when the effective radius of the drive pulley 3 becomes the minimum. It supports the V-belt 13 and blocks transmission of rotation between the input and output shafts 1 and 2.

Next, the operation of the above embodiment will be explained.

First, to explain the movement of changing the gear ratio between the input and output shafts 1 and 2, under normal conditions, the input shaft 1
The screw member 16 of the transmission mechanism 31 screwed into the
Neither the brake plate 30 nor the friction ring 29 comes into contact with the friction portion 16a, and the screw member 16 rotates integrally with the input shaft 1 without a speed difference. Further, the rotation of the input shaft 1 is applied to the second toothed pulley 26 on the cylindrical member 25, and the belt transmission between the first and second V-belt pulleys 18, 22 and the first
The speed is increased and transmitted by the belt transmission between the second toothed pulleys 24 and 26, and therefore,
The second toothed pulley 26 and a friction ring 29 fixed to its side surface are rotating in the same direction as the input shaft 1 at a faster rotational speed.

From this state, for example, when increasing the gear ratio between input and output shafts 1 and 2 to enter high-speed mode,
The above-mentioned brake plate 30 is attached to the friction portion 1 on the outer periphery of the screw member 16.
6a to control the rotation of the screw member 16. Due to this braking action, the screw member 16 is decelerated relative to the input shaft 1, and due to this relative rotation in the deceleration direction, the screw member 16 is threaded on the input shaft 1 in the direction toward the drive pulley 3,
The movable sheave 5 of the drive pulley 3, which is movably connected to the threaded member 16 via a bearing 17, approaches the fixed sheave 4, and the effective radius of the drive pulley 3 increases. In addition, with the increase in the effective radius of the drive pulley 3, the V-belt 13
is drawn toward the driving pulley 3 as a whole, and the movable sheave 9 of the driven pulley 7 moves in a direction away from the fixed sheave 8 against the biasing force of the spring 12 due to the movement of the V-belt 13. The effective radius of is reduced.
As a result, the effective radius of the driving pulley 3 becomes larger than that of the driven pulley 7, and the rotation of the input shaft 1 is accelerated and transmitted to the output shaft 2.

On the other hand, when lowering the gear ratio between the input and output shafts 1 and 2 to set the low speed mode, the second toothed pulley 26 is moved by the cylindrical member 25, and the friction ring 29 is moved to the friction portion 16a. By bringing them into contact, the screw member 16 is driven in the speed increasing direction. This driving action increases the speed of the screw member 16 relative to the input shaft 1, and this relative rotation in the speed increasing direction causes the screw member 16 to move toward the input shaft 1.
The movable sheave 5 of the drive pulley 3 moves in the direction away from the fixed sheave 4, and the drive pulley 3
The effective radius of is reduced. As the effective radius of the drive pulley 3 decreases, the V-belt 13 is entirely moved around the driven pulley 7 by the biasing force of the spring 12.
This V-belt 1
3 moves the movable sheave 9 of the driven pulley 7.
approaches the fixed sheave 8, and the effective radius of the driven pulley 7 increases. As a result, the effective radius of the drive pulley 3 becomes smaller than that of the driven pulley 7, and the rotation of the input shaft 1 is decelerated and transmitted to the output shaft 2.

Further, when the movable sheave 5 of the drive pulley 3 is located at the farthest position from the fixed sheave 4, the V-belt 13 is separated from both the sheaves 4 and 5 of the drive pulley 3 and is placed on the bearing 39 at the bottom of the belt groove 6. In this state, transmission of rotation is cut off between the input and output shafts 1 and 2, and this structure ensures the clutch function.

In this case, by bringing the friction ring 29 or the brake plate 30 into contact with the friction portion 16a on the outer periphery of the screw member 16 screwed and supported by the input shaft 1 to decelerate or increase the speed of the screw member 16, the input shaft 1 and the screw member Since the movable sheave 5 of the drive pulley 3 is moved in the axial direction by the relative rotation between the movable sheave 5 and the movable sheave 5, the drive structure for the movable sheave 5 is extremely simple, and its control is also facilitated.

Furthermore, the movable shaft 5 is
Since the movable sieve 5 is moved, a conventional expensive servo motor or the like is not required as a drive source for the movable sieve 5, and therefore it can be manufactured at low cost.

During the above-mentioned speed change, when the rotation of the input/output shafts 1 and 2 suddenly stops due to stopping of the engine, etc., the rotation of the second toothed pulley 26 and the screw member 16 in the speed change mechanism 31 also stops accordingly. Therefore, it becomes impossible to change the gear ratio between the input and output shafts 1 and 2, and the gear ratio is maintained at the gear ratio immediately before stopping, that is, the increased gear ratio. At the same time as the engine is stopped, the emergency clutch mechanism 37 is activated, and the drive cam member 35 is rotated around the input shaft 1, and the cylindrical cam surface 35a is pushed back by the cam surface 35a. The pressing force on the driven cam member 32 decreases, and this decrease in pressing force causes the driven cam member 3 to
2, and a drive pulley 3 movably connected to the driven cam member 32 via a bearing 33.
The fixed sheave 4 moves backward under the tension of the V-belt 13, and the interval between the belt grooves 6 of the drive pulley 3 becomes wider. As a result, the V-belt 1
3 decreases to approximately zero, and transmission of rotation between the input and output shafts 1 and 2 is interrupted.

Thereafter, when the engine is restarted, the transmission mechanism 31 becomes operable by the rotation of the screw member 16, the second toothed pulley 26, etc.
As a result, the movable sheave 5 of the drive pulley 3 is positioned at the farthest position from the fixed sheave 4,
Bearing 3 at the bottom of belt groove 6 of drive pulley 3
V-belt 13 is placed on top of 9. Next, the effective radius of the drive pulley 3 gradually increases, transmission of rotation starts again between the input and output shafts 1 and 2, and the gear ratio between the input and output shafts 1 and 2 increases from the minimum gear ratio. , the power tiller etc. shifts to the driving state again.

In that case, there is a regulating member 3 between both pulleys 3 and 7.
8 is arranged, the above fixed sieve 4
When the input shaft 1 starts to rotate when the engine is restarted, the V-belt 13, which has become loose as shown by the solid line in FIG. The belt groove 6 is pushed toward the bottom of the belt groove 6, so that transmission of rotation between the input and output shafts 1 and 2 can be reliably interrupted when the engine is restarted.

In this way, when the engine is restarted after being stopped and the input shaft 1 rotates, the rotation of the input shaft 1 will not be transmitted to the output shaft 4 at an increased gear ratio as in the case where the fixed shift is immovable. As a result, it is possible to reliably avoid the tiller from flying out.

In addition, when the engine is running and the gear ratio between the input and output shafts 1 and 2 can be changed by operating the transmission mechanism 31, the output shaft 2 may be changed for some reason such as ensuring safety. When it becomes necessary to stop the rotation, the transmission mechanism 3
1, the movable sheave 5 of the drive pulley 3 is separated from the fixed sheave 4, and at the same time, the emergency clutch mechanism 37 can be actuated to retract the fixed sheave 4. In that case, both the shafts 4 and 5 move back at the same time and the belt groove 6 opens, so that the transmission of rotation between the input and output shafts 1 and 2 can be instantaneously interrupted, further improving safety, etc. .

Also, at that time, as both the sheaves 4 and 5 in the drive pulley 3 move backward, the input and output shafts 1 and 2
When the transmission of rotation between the pulleys 3 and 7 is cut off, the V-belt 13, which had been rotating at high speed until then, attempts to swell into a circular shape due to centrifugal force. Since the V-belt 13 that is about to inflate is provided with the regulating member 38
The V-belt 13 is regulated and pushed back, and does not swell into a circular shape, thereby reliably preventing damage to peripheral equipment and abnormal wear of the outer circumferential surface of the V-belt 13.

Therefore, by moving the fixed sheave 4 of the drive pulley 3 in this way, the input/output shaft 1,
Since the rotation between the two is reliably and immediately interrupted, there is no need for a special clutch mechanism for emergencies.
Accordingly, the structure can be simplified and costs can be reduced.

3A to 3D each show modified examples of the regulating member 38, and in the one shown in FIG. It is fixedly supported by a pin 42 via. In addition, in the case of Fig. b, the bearing 43 is supported by the pin 42,
In FIG. C, a coating layer 44 is formed by coating the outer peripheral surface of the pin 42 with a self-lubricating Teflon resin or the like. Furthermore, figure d
In this case, a tube 45 made of self-lubricating polyethylene resin is externally fitted onto the pin 42, and any of these tubes can provide the same effects as the above embodiment.

In the above embodiment, when the screw member 16 is rotated relative to the input shaft 1 in the deceleration direction, the screw member 16 is screw-fed in the direction away from the drive pulley 3. It goes without saying that by reversing the direction, the screw member may be threaded in a direction closer to the drive pulley as the screw member rotates relative to the input shaft in the deceleration direction.

Further, in the above embodiment, the fixed sheave 4 of the drive pulley 3 provided on the input shaft 1 is moved by the emergency clutch mechanism 37, but conversely, the fixed sheave 4 of the driven pulley 7 on the output shaft 2 is moved. 8 may be moved. Furthermore, the driving pulley 3 and the driven pulley 7
At least one of the movable sheaves 5, 9 may be moved in a direction away from the fixed sheaves 4, 8, respectively, and in either case, the same effects as in the above embodiment can be achieved.

Further, as the transmission mechanism 31, in addition to the structure as in the above embodiment, various known transmission means can be employed.

(Effects of the Invention) As explained above, according to the present invention, the movable sheave of the variable pulley is brought into contact with the fixed sheave due to the relative rotational difference with the input side rotating shaft that is drivingly connected to the engine, etc. In a variable pulley type transmission that changes the gear ratio between two rotating shafts, at least one of the fixed sheave or the movable sheave of the variable pulley is slid in a direction away from the opposing sheave, and the An emergency clutch mechanism is provided which reduces the tension of the belt member to the point where rotation cannot be transmitted by increasing the interval, and the belt member is provided with an emergency clutch mechanism that reduces the tension of the belt member to the point where rotation cannot be transmitted. By providing the regulating member in contact with the outer circumferential surface of the belt member, which swells in a circular shape due to the tension being reduced by the operation of the emergency clutch mechanism, outside the movement range of the belt member that moves during the speed change of the gear ratio, both Contact with the regulating member can prevent the belt member, whose tension has decreased, from expanding in a circular shape due to centrifugal force due to the operation of the emergency clutch mechanism during gear shifting between the rotating shafts, thereby preventing abnormal wear of the belt member. It is possible to reliably prevent damage to peripheral equipment and improve the durability of the transmission.

[Brief explanation of drawings]

The drawings show an embodiment of the present invention, and FIG. 1 is a sectional view showing the overall structure of the transmission, and FIG.
It is a sectional view taken along the line - in the figure. FIG. 3 is a front view showing a modification of the regulating member. 1...Input shaft, 2...Output shaft, 3...Drive pulley, 4...Fixed shaft, 5...Movable shaft,
7... Driven pulley, 8... Fixed shaft, 9...
Movable shaft, 13...V belt, 14...Variable pulley mechanism, 16...Screw member, 29...Friction ring, 30...Brake plate, 31...Transmission mechanism, 32
... Passive cam member, 35 ... Drive cam member, 37
...Emergency clutch mechanism, 38...Regulation member.

Claims (1)

[Claims] 1 It is installed on two rotating shafts on the input side and the output side that are arranged parallel to each other, and the effective radius of the belt member wound between the two sheaves is adjusted by moving the movable sheave toward and away from the fixed sheave. A variable pulley mechanism having a pair of variable pulleys and a relative rotational difference between the above-mentioned input-side rotation shaft causes the movable sheave of the variable pulley on the input-side rotation shaft to slide on the rotation shaft, In a transmission equipped with a transmission mechanism that changes a gear ratio between rotary shafts, at least one of a fixed sheave or a movable sheave on a variable pulley on at least one of the rotary shafts is expanded so that the belt an emergency clutch mechanism for sliding the opposite side of the opposing sheave so that the tension in the member is reduced to the point where rotation cannot be transmitted; Further, a regulating member is provided outside the movement range of the belt member that moves during the speed change of the gear ratio between the rotating shafts, and comes into contact with the outer circumferential surface of the belt member that swells into a circular shape when the tension is reduced by the operation of the emergency clutch mechanism. A transmission device characterized by: