JP5842238B2 - Pulley type continuously variable transmission mechanism - Google Patents

Description

  The present invention comprises a driving pulley supported by a driving shaft, a driven pulley supported by a driven shaft, and an endless body wound around the pulleys, and the endless with respect to the driving pulley and the driven pulley. The present invention relates to a pulley type continuously variable transmission mechanism that continuously changes speed by changing a winding radius of a body.

  A drive-side pulley supported by the drive shaft, a driven-side pulley supported by the driven shaft, and an endless body wound around the both pulleys, the endless body being wound around the drive-side pulley and the driven-side pulley Various pulley-type continuously variable transmission mechanisms that continuously change the speed of rotational power transmitted from the drive shaft to the driven shaft by changing the radius have been proposed (see, for example, Patent Document 1 below).

  More specifically, the drive pulley is supported by a drive-side fixed pulley half that is relatively non-rotatable and axially movable on the drive shaft, and is non-rotatably supported by the drive shaft and axially movable by a predetermined amount. The drive-side movable pulley half is included, and the winding radius of the endless body with respect to the drive-side pulley changes according to the axial movement of the drive-side movable pulley half.

Similarly, the driven pulley is supported by a driven fixed pulley half that is supported relative to the driven shaft so as not to rotate relative to the axial direction, and is not supported relative to the driven shaft so as to be movable relative to the driven shaft in the axial direction. The driven-side movable pulley half is included, and the winding radius of the endless body with respect to the drive driven-side pulley changes according to the axial movement of the driven-side movable pulley half.

  However, in the pulley-type continuously variable transmission mechanism described in Patent Document 1, the fixed pulley half and the movable pulley half are completely different from each other in components, so that the cost can be sufficiently reduced. There was a problem that could not be planned.

More specifically, each pulley half has a cylinder part and a main body part extending radially outward from the cylinder part.
The cylindrical part of the fixed pulley half is extrapolated to the corresponding shaft, while the cylindrical part of the movable pulley half is extrapolated to the cylindrical part of the fixed pulley half. That is, in the conventional configuration, the cylindrical portion of the fixed pulley half and the cylindrical portion of the movable pulley half have different dimensions with respect to the inner diameter and the outer diameter.
Further, by the outer diameter of the tubular portion are different, the main body portion which is fixed to the cylindrical portion of the fixed pulley half body and said body portion which is fixed to the cylindrical portion of the movable pulley half body different dimensions relates inner diameter Yes.

Japanese Patent Laid-Open No. 01-283454

  The present invention has been made in view of the prior art, and includes a driving side pulley including a driving side fixed pulley half and a driving side movable pulley half, a driven side fixed pulley half, and a driven side including a driven side movable pulley half. It is an object of the present invention to provide a pulley-type continuously variable transmission mechanism including a side pulley, which can reduce the cost by using as many common parts as possible for each pulley half.

In order to achieve the above object, the present invention is a pulley type continuously variable transmission mechanism that continuously changes the rotational speed of power transmitted from a drive shaft to a driven shaft, and is not relatively rotatable with respect to the drive shaft and moves in the axial direction. A drive-side fixed pulley half supported in an impossible manner, and a drive-side movable pulley half supported by the drive shaft so as to be relatively unrotatable and movable in the axial direction by a predetermined amount while facing the drive-side fixed pulley half. A drive-side biasing member that biases the drive-side movable pulley half toward the drive-side fixed pulley half, and a driven-side fixed pulley half that is supported by the driven shaft so as not to be relatively rotatable and axially movable. A driven-side movable pulley half that is supported by the driven shaft so as not to rotate relative to the driven shaft and to be movable in the axial direction by a predetermined amount in a state of being opposed to the driven-side fixed pulley half, and the driven-side movable pulley half Obedience A driven urging member for urging the side fixed pulley half body, and a driven biasing member biasing force than the driving-side biasing member is large, the drive in response to an external operation force A speed change operation mechanism for increasing the urging force of the moving-side urging member, and the pressure on the driving-side fixed pulley half and the movable pulley half, and the pressure on the driven-side fixed pulley half and the movable pulley half Each of the pulley halves is a cylindrical portion that is extrapolated to the corresponding shaft so as to be movable in the axial direction, and a main body portion that extends radially outward from one axial end side of the cylindrical portion, A pulley forming body including a main body portion having a conical surface inclined so as to be positioned on the other end side of the cylindrical portion with respect to the axial direction of the cylindrical portion as going from the radially inner side to the outer side. In common, the driving pulley and the driven pulley half The cylindrical portion of the pulley forming body formed by pins provided on the corresponding axis is engaged, fixing hole for axially immovably fixing is provided for the corresponding axis said cylindrical portion A pin provided on a corresponding shaft is engaged with a cylindrical portion of the pulley forming body that forms the movable pulley halves on the driving side and the driven side, and the cylindrical portion is predetermined with respect to the corresponding shaft. Provided is a pulley type continuously variable transmission mechanism provided with a sliding groove that allows movement along an axial direction by a distance.

  Preferably, the cylindrical portion of the pulley forming body forming the driving-side and driven-side stationary pulley halves is positioned on one end side in the axial direction, and has a large-diameter portion having a large outer diameter, and the large-diameter portion And a small-diameter portion that extends toward the other end in the axial direction with a step and has a small outer diameter.

  In one form, the said sliding groove provided in the cylinder part of the said pulley formation body which forms the said driven side movable pulley half body moves to the other side from the one axial direction of the said driven shaft to which the said cylinder part respond | corresponds Accordingly, a cam region may be included for moving the cylindrical portion from one side to the other side around the axis of the driven shaft.

For example, the main body portion is formed by a main body portion forming member, and the cylindrical portion is formed by a cylindrical portion forming member that is separated from the main body portion forming member.
The main body forming member includes a radially inner portion provided with a central hole having a predetermined inner diameter, and a radially outer portion extending radially outward from the radially inner portion and provided with the conical surface. The cylindrical portion forming member includes an insertion portion that is inserted in contact with the central hole, and a flange portion that extends radially outward at one axial end side of the insertion portion. It is supposed to have.
The radially inner portion has an outer surface and an inner surface facing in the same direction as the conical surface and in the opposite direction with respect to the axial direction.
In this case, the tubular portion forming member is fixed to the main body portion forming member in a state where the collar portion is in contact with the outer surface and the insertion portion is inserted into the through hole, The inner surface of the side portion acts as a stopper for directly or indirectly locking one end portion of the corresponding urging member.

  Preferably, the radially inner portion is recessed from a radially inner end of the radially outer portion, and the flange portion of the tubular portion forming member is in a recess defined by the radially inner portion. Be positioned.

  According to the pulley type continuously variable transmission mechanism according to the present invention, the driving-side fixed pulley half, the driving-side movable pulley half, the driven-side fixed pulley half, and the driven-side movable pulley half move in the axial direction on the corresponding axes. A cylindrical portion that can be extrapolated, and a main body portion extending radially outward from one axial end side of the cylindrical portion, the cylindrical portion being directed in the axial direction of the cylindrical portion from the radially inner side to the outer side. And a pulley forming body including a main body portion having a conical surface inclined so as to be positioned on the other end side, and forming the driving-side and driven-side stationary pulley halves. A fixed hole is provided in the cylindrical portion of the pulley forming body, and the cylindrical portion of the pulley forming body forming the movable pulley halves on the driving side and the driven side is a predetermined distance from the axis corresponding to the cylindrical portion. Move along the axial direction The sliding groove tolerated is provided, it is possible to inexpensively costs by as much as possible components common.

FIG. 1 is a side view of a working vehicle to which a pulley type continuously variable transmission mechanism according to an embodiment of the present invention is applied. FIG. 2 is a longitudinal side view of the pulley type continuously variable transmission mechanism. FIG. 3 is a cross-sectional view taken along line III-III in FIG. FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. FIG. 5 is a longitudinal rear view of a first modified example of the forward / reverse switching mechanism in the working vehicle. FIG. 6 is a longitudinal rear view of a second modification of the forward / reverse switching mechanism. 7 (a) and 7 (b) are longitudinal sectional views of a fixed pulley half and a movable pulley half in the pulley type continuously variable transmission mechanism. FIG. 8 is a longitudinal sectional view of the pulley forming body. FIG. 9 is a longitudinal sectional view of a modification of the movable pulley half.

  Hereinafter, an embodiment of a pulley type continuously variable transmission mechanism according to the present invention will be described with reference to the accompanying drawings.

The pulley type continuously variable transmission mechanism 100 according to the present embodiment is inserted in a traveling system transmission path in the work vehicle 1.
First, the overall configuration of the working vehicle 1 to which the pulley type continuously variable transmission mechanism 100 according to the present embodiment is applied will be described.

FIG. 1 shows a side view of the working vehicle 1.
As shown in FIG. 1, the working vehicle 1 is in the form of a riding lawn mower.
Specifically, the working vehicle 1 is supported by a vehicle frame 10, front wheels 15 F and rear wheels 15 R supported by the vehicle frame 10, a driver seat 20 supported by the vehicle frame 10, and the vehicle frame 10. The pulley-type continuously variable drive source 25 having a vertical output shaft, and the pulley-type steplessly inserted in the traveling system transmission path from the drive source 25 to the wheels acting as drive wheels among the front wheels 15F and the rear wheels 15R. A speed change mechanism 100, a mower device 30 supported by the vehicle frame 10 in a state of being operatively driven by rotational power from the drive source 25, and a speed change operating member 35 disposed in the vicinity of the driver seat 20. And a steering member 40 disposed in the vicinity of the driver's seat 20.

FIG. 2 shows a longitudinal side view of the pulley type continuously variable transmission mechanism 100.
3 and 4 are cross-sectional views taken along lines III-III and IV-IV in FIG. 1, respectively.

As shown in FIGS. 2 and 4, the work vehicle 1 further includes a forward / reverse switching mechanism 300 and a differential gear mechanism 400 inserted in the traveling system transmission path.
In the present embodiment, the rear wheel 15R is a drive wheel.
Accordingly, the pulley type continuously variable transmission mechanism 100, the forward / reverse switching mechanism 300, and the differential gear mechanism 400 are inserted in a transmission path from the drive source 25 to the rear wheel 15R.
Further, in the present embodiment, the front wheel 15F is a steering wheel, and the front wheel 15F is steered in response to an artificial operation on the steering member 40.

  The pulley-type continuously variable transmission mechanism 100 continuously transmits the power from the vertical drive shaft 50 to the vertical driven shaft 55 in the traveling system transmission path, and continuously speeds the rotational power transmitted to the driven shaft 55. It is configured to be able to.

Specifically, as shown in FIGS. 2 and 3, the pulley-type continuously variable transmission mechanism 100 includes a driving-side fixed pulley half 110 supported on the driving shaft 50 so as not to be relatively rotatable and axially movable, A driving-side movable pulley half 120 supported by the driving shaft 50 so as not to rotate relative to the driving-side fixed pulley half 110 and to be movable in the axial direction by a predetermined amount. A drive-side biasing member 130 that biases the drive-side fixed pulley half 110 toward the drive-side fixed pulley half 110; a driven-side fixed pulley half 140 supported by the driven shaft 55 so as not to be relatively rotatable and axially movable; and the driven side a fixed pulley half body 140 and the relative rotation and a predetermined amount of the driven shaft 55 in the opposite state for axially movably supported driven-side movable pulley half body 150, the driven-friendly A driven-side urging member 160 that urges the pulley half 150 toward the driven-side fixed pulley half 140, wherein the urging force is larger than that of the driving-side urging member 130. 160, a speed change operation mechanism 170 that increases the biasing force of the driven-side biasing member 130 in response to an external operating force, a driving-side pulley including the driving-side fixed pulley half 110 and the movable pulley half 130, and the driven And an endless body 180 wound around a driven pulley including a side fixed pulley half 140 and a movable pulley half 150.

A bearing 90 a that supports the upper end side of the drive shaft 50 and a bearing 90 b that supports the lower end side are held by cross members 101 and 102 fixed to the vehicle frame 10. The bearing 90 b that supports the upper end side of the driven shaft 55 is also held by the cross member 103 that is fixed to the vehicle frame 10.
The speed change operation mechanism 170 includes an operation arm portion 170a, a support shaft portion 170b, and a fork portion 170c, and the support shaft portion 170b is supported by the cross member 102 so as to be substantially horizontal.

The pulley type continuously variable transmission mechanism 100 operates as follows.
That is, since the urging force of the driven urging member 160 is greater than the urging force of the driving urging member 130, in the initial state where no external operating force is applied to the speed change operation mechanism 170, The separation distance between the driving side movable pulley half 120 and the driving side fixed pulley half 110 is maximized, and the separation force between the driven side movable pulley half 150 and the driven side fixed pulley half 140 is minimized. Become.

In this state, the winding radius of the endless body 180 with respect to the driving pulley formed by the driving-side fixed pulley half 110 and the driving-side movable pulley half 120 is minimum, and the driven-side fixed pulley half 140 is driven. In addition, the winding radius of the endless body 180 with respect to the driven pulley formed by the driven movable pulley half 150 is in the minimum speed state (see FIG. 2).

When an external operation force is applied to the shift operation mechanism 170 from the lowest speed state, the shift operation mechanism 170 increases the urging force of the drive-side urging member 130 in accordance with the increase in the external operation force. As a result, the drive-side movable pulley half 120 moves along the axial direction of the drive shaft 50 in the direction approaching the drive-side fixed pulley half 110, and at the same time, the driven-side movable pulley half 150 It moves along the axial direction of the driven shaft 55 in a direction away from the driven-side fixed pulley half 140.
Accordingly, the winding radius of the endless body 180 with respect to the driving pulley increases, and accordingly, the winding radius of the endless body 180 with respect to the driven pulley decreases, and the rotational speed of the driven shaft 55 increases. .
Preferably, a low-friction coating can be applied to a region of the drive shaft 50 where the driving-side movable pulley half 120 moves and a region of the driven shaft 55 where the driven-side movable pulley half 150 moves. .

  In the present embodiment, as shown in FIG. 2, the drive shaft 50 has a drive side end cap on the back side of the drive side movable pulley half 120 (the side opposite to the drive side fixed pulley half 110). 135 is supported, one end of the coil spring forming the drive side biasing member 130 is engaged with the back side of the drive side movable pulley half 120 and the other end is engaged with the drive side end cap 135. Are combined.

  In the present embodiment, one end of the drive side biasing member 130 is connected to the drive side movable pulley via a contact plate 136 (see FIG. 2) that is externally attached to the drive shaft 50 so as to be movable in the axial direction. The half body 120 is engaged with the back surface.

Similarly, a driven side end cap 165 is supported by the driven shaft 55 on the back side of the driven side movable pulley half 150 (the side opposite to the driven side fixed pulley half 140). One end of the coil spring forming the biasing member 160 is engaged with the back side of the driven movable pulley half 150 and the other end is engaged with the driven end cap 165.
The driven side end cap 165 receives a biasing force from the driven side biasing member 160 via an adjustment screw mechanism 167 (see FIG. 2).

  In the present embodiment, one end of the driven-side urging member 160 is connected to the driven-side movable pulley via a contact plate 166 (see FIG. 2) that is externally attached to the driven shaft 55 so as to be movable in the axial direction. The half body 150 is engaged with the back surface.

  The drive-side end cap 135 is positioned at an initial position in the axial direction in a state where the drive force from the speed change operation mechanism 170 is not received, and the drive side fixed pulley as the force from the speed change operation mechanism 170 increases. It is supported by the drive shaft 50 while being operatively connected to the speed change operation mechanism 170 so as to move to one side in the axial direction close to the half body 110.

As shown in FIG. 2, the initial position is determined by an adjusting screw mechanism 138 that abuts the driving side end cap 135 via a pressure plate 137.
Further, the free end portion of the fork portion of the speed change operation mechanism 170 is engaged with the back surface of the pressure plate 137, and when the external operation force is transmitted from the speed change operation mechanism 170, the drive side end cap 135 is It is moved to the one axial side (upward in FIG. 2) against the urging force via the pressure plate 137.

The driven-side end cap 165 is supported by the driven shaft 55 so as not to move from a predetermined position in the axial direction to the opposite side to the one axial side adjacent to the driven-side fixed pulley half 140.
The predetermined position is determined by the adjustment screw mechanism 167 that contacts the driven end cap 165. The illustrated maximum deceleration position of the pulley type continuously variable transmission mechanism 100 is set by the both adjusting screw mechanisms 138 and 167.

The speed change operation mechanism 170 can have various configurations as long as the urging force of the driven side urging member 130 can be increased in response to an artificial operation on the speed change operation member 35.
In the present embodiment, as shown in FIG. 1, the speed change operation mechanism 170 is operatively connected to the speed change operation member 35 via a mechanical link 175.

  Instead, the working vehicle 1 includes a sensor (not shown) that detects the operation amount of the speed change operation member 35, an actuator (not shown) that operates the speed change operation mechanism 170, and a control device ( (Not shown), and the control device can be configured to operate the actuator based on a signal from the sensor.

  The forward / reverse switching mechanism 300 is configured to change the drive direction of the drive wheel in accordance with an external operation.

  In the present embodiment, as shown in FIG. 2, the forward / reverse switching mechanism 300 is disposed between the pulley-type continuously variable transmission mechanism 100 and the differential gear mechanism 400 in the transmission direction, and can be used for external operation. Accordingly, a forward state in which forward rotational power is transmitted from the driven shaft 55 to the differential gear mechanism 400, a reverse state in which rotational power in the reverse direction is transmitted from the driven shaft 55 to the differential gear mechanism 400, or The neutral state in which the power transmission from the driven shaft 55 to the differential gear mechanism 400 is interrupted can be selectively exhibited.

  Specifically, as shown in FIG. 2, the forward / reverse switching mechanism 300 includes a forward / reverse input shaft 310 operatively connected to the driven shaft 55, and a forward / reverse output shaft 350 operatively connected to the differential gear mechanism 400. A forward-side bevel gear 320 and a backward-side bevel gear 325 supported on the forward / reverse input shaft 310 so as to be relatively rotatable about the axis in a state of being spaced apart from each other; The forward / backward advancement in a state of being engaged with the switching slider 330 supported so as to be movable in the axial direction between the forward bevel gear 320 and the backward bevel gear 325 according to an external operation, and the forward side bevel gear 320 and the backward side bevel gear 325. And a driven bevel gear 340 supported on the force shaft 350 so as not to rotate relative to the force shaft 350.

As shown in FIG. 2, in the present embodiment, the forward / reverse input shaft 310 is integrally formed with the driven shaft 55.
In other words, a single shaft acts as the driven shaft 55 and the forward / reverse input shaft 310.

  The forward bevel gear 320 and the backward bevel gear 325 have engagement protrusions 321 and 326 on the end surfaces facing the switching slider 330.

  The switching slider 330 includes a forward-side engagement protrusion 331 that can be engaged with the engagement protrusion 321 of the forward-bevel gear 320, and a reverse-side engagement protrusion 332 that can be engaged with the engagement protrusion 326 of the backward-bevel gear 325. Have.

  In the switching slider 330, the forward-side engaging protrusion 331 does not engage with the engaging protrusion 321 of the forward-bevel gear 320 and the backward-side engaging protrusion 332 engages with the backward-bevel gear 325 according to an external operation. A neutral position (see FIG. 2) that does not engage with 326, and a forward position that is located on one side in the axial direction from the neutral position and in which the forward-side engagement protrusion 331 engages with the engagement protrusion 321 of the forward-bevel gear 320. Further, it is configured to be able to selectively take a reverse position that is located on the other side in the axial direction from the neutral position and in which the reverse side engagement protrusion 332 engages with the engagement protrusion 326 of the reverse direction bevel gear 325.

  In the present embodiment, the switching slider 330 inputs an external operating force via the operating arm 335 (see FIG. 1).

  Preferably, as shown in FIG. 2, the forward / reverse switching mechanism 300 has an axis line between the forward position, the neutral position and the reverse position when an operating force exceeding a predetermined magnitude is applied. A detent mechanism 360 is provided that prevents unintentional axial movement while allowing movement in the direction.

Of course, instead of the forward / reverse switching mechanism 300, a forward / reverse switching mechanism having another configuration may be employed.
FIG. 5 shows a longitudinal rear view of the forward / reverse switching mechanism 300B according to the first modification.
In the drawing, the same members as those in the forward / reverse switching mechanism 300 are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 5, the forward / reverse switching mechanism 300B according to the first modification includes the forward / reverse input shaft 310, the forward / reverse output shaft 350, and the forward / reverse input shaft that are separated from each other. 310, a forward-side bevel gear 320B and a backward-side bevel gear 325B that are rotatably supported around the axis line 310, and a forward-bevel gear 320B and a backward-bevel gear gear 325B that cannot rotate relative to the forward / backward input shaft 310 and that can be rotated according to external operations. A switching slider 330B supported so as to be movable in the axial direction in between, and the driven bevel gear 340.

  In the forward / reverse switching mechanism 300, the forward engagement protrusion 331 or the reverse engagement protrusion 332 of the switching slider 330 is engaged with the corresponding engagement protrusions 321 and 326 of the bevel gears 320 and 325. Rotational power is transmitted from the forward / reverse input shaft 310 to the corresponding bevel gears 320 and 325 via the switching slider 330.

  Instead, in the forward / reverse switching mechanism 300B according to the first modification, the switching slider 330B is configured to transmit rotational power to the forward bevel gear 320B or the backward bevel gear 325B by friction engagement. Yes.

  Specifically, the forward bevel gear 320B and the reverse bevel gear 325B have concave friction engagement surfaces 321B and 326B on the end surfaces facing the switching slider 330B.

  On the other hand, the switching slider 330B has a convex forward frictional engagement surface 331B on an end surface facing the forward bevel gear 320B, and a convex reverse frictional engagement on an end surface facing the reverse bevel gear 325B. It has a surface 332B.

  In the switching slider 330B, the forward friction engagement surface 331B does not engage with the friction engagement surface 321B of the forward bevel gear 320B and the reverse friction engagement surface 332B of the reverse bevel gear 325B in accordance with an external operation. A neutral position that does not engage with the friction engagement surface 326B (see FIG. 5), an axial direction one side from the neutral position, and the forward friction engagement surface 331B is a friction engagement surface 321B of the forward bevel gear 320B. A forward position to be engaged and a reverse position that is located on the other side in the axial direction from the neutral position and in which the reverse friction engagement surface 332B engages with the friction engagement surface 326B of the reverse bevel gear 325B can be taken selectively. It is configured as follows.

FIG. 6 shows a longitudinal rear view of the forward / reverse switching mechanism 300C according to the second modification.
In the figure, the same members as those in the forward / reverse switching mechanism 300 or the first modification 300B are denoted by the same reference numerals, and detailed description thereof is omitted.

In the forward / reverse switching mechanism 300 and the first modification 300C, the switching sliders 330 and 330B are supported by the forward / reverse input shaft 310.
On the other hand, in the forward / reverse switching mechanism 300C according to the second modification, the switching slider 330C is supported by the forward / reverse output shaft 350.

  Specifically, as shown in FIG. 6, the forward / reverse switching mechanism 300 </ b> C according to the second modification is relative to the forward / reverse input shaft 310, the forward / reverse output shaft 350, and the forward / reverse input shaft 310. A drive-side bevel gear 315 that is non-rotatably supported; a forward-side bevel gear 320C that is meshed with the drive-side bevel gear 315 and spaced apart from each other; A reverse-side bevel gear 325C, and the switching slider 330C supported by the forward / reverse output shaft 350 so as not to rotate relative to the axis and axially movable between the forward-bevel gear 320C and the reverse-bevel gear 325C in response to an external operation. It has.

  The forward bevel gear 320C and the reverse bevel gear 325C have concave frictional engagement surfaces 321C and 326C on the end surfaces facing the switching slider 330C.

  On the other hand, the switching slider 330C has a convex forward friction engagement surface 331C on the end surface facing the forward bevel gear 320C, and has a convex reverse friction engagement surface on the end surface facing the reverse bevel gear 325C. It has a surface 332C.

  In the switching slider 330C, the forward friction engagement surface 331C does not engage with the friction engagement surface 321C of the forward bevel gear 320C and the reverse friction engagement surface 332C of the reverse bevel gear 325C according to an external operation. A neutral position (see FIG. 6) that is not engaged with the friction engagement surface 326C, an axial direction one side from the neutral position, and the forward friction engagement surface 331C is a friction engagement surface 321C of the forward bevel gear 320C. A forward position to be engaged and a reverse position that is located on the other side in the axial direction from the neutral position and in which the reverse friction engagement surface 332C engages with the friction engagement surface 326C of the reverse bevel gear 325C can be taken selectively. It is configured as follows.

  In the second modification 300C, the switching slider 330C is configured to input rotational power from the forward bevel gear 320C or the reverse bevel gear 325C by engagement via an engagement protrusion instead of friction engagement. It is also possible to do.

  Here, detailed configurations of the driving-side fixed pulley half 110, the driving-side movable pulley half 120, the driven-side fixed pulley half 140, and the driven-side movable pulley half 150 will be described.

7A and 7B are longitudinal sectional views of the fixed pulley halves 110 and 140 and the movable pulley halves 150 and 150, respectively.
As shown in FIG. 7 (a), each of the pulley halves 110, 120, 140, 150 includes a cylindrical portion 210 that is externally attached to a corresponding shaft so as to be movable in the axial direction, and one axial end side of the cylindrical portion 210. A conical surface 231 that is inclined so as to be positioned on the other end side of the tubular portion 210 with respect to the axial direction of the tubular portion as it goes from the radially inward to the outward. This is common in that it includes a pulley forming body 200 including a main body portion 230 having.
FIG. 8 is a longitudinal sectional view of the pulley forming body.

  As shown in FIG. 7A and FIG. 8, a fixing hole 211 is provided in the cylindrical portion 210 of the pulley forming body 200 that forms the driving-side and driven-side fixing pulley halves 110 and 140. .

  As shown in FIGS. 2 and 3, a pin 58 provided on the corresponding shaft 50 (55) is engaged with the fixed hole 211, whereby the driving-side and driven-side fixed pulley halves 110 and 140 are engaged. Is not rotatable relative to the corresponding shaft 50 (55) and cannot move in the axial direction.

  As shown in FIGS. 7B and 8, the cylinder portion 210 of the pulley forming body 200 that forms the movable pulley halves 120 and 150 on the driving side and the driven side corresponds to the axis corresponding to the cylinder portion 210. 50 (55) is provided with a sliding groove 212 that allows movement along the axial direction by a predetermined distance.

  As shown in FIGS. 2 and 3, a pin 59 provided on the corresponding shaft 50 (55) is engaged with the sliding groove, so that the movable pulley halves 120, 150 on the driving side and the driven side are engaged. Is not rotatable relative to the corresponding shaft 50 (55) and is movable in the axial direction by a distance corresponding to the length of the sliding groove 212 in the axial direction.

  Thus, by forming the fixing hole 211 in the pulley forming body 200, the driving-side and driven-side fixed pulley halves 110 and 140 are obtained, and the pulley-forming body 200 is in the state described above. By forming the sliding groove 212, the movable pulley halves 120 and 150 on the driving side and the driven side are obtained.

  That is, in the pulley type continuously variable transmission mechanism 100 according to the present embodiment, the two pulley halves 110 and 120 forming the driving pulley and the two pulley halves 140 forming the driven pulley. In all 150, the pulley forming body 200 is used as a common material, so that the cost can be reduced as much as possible by sharing parts.

  More specifically, even in the conventional pulley-type continuously variable transmission mechanism, the driving-side fixed pulley half, the driving-side movable pulley half, the driven-side fixed pulley half, and the driven-side movable pulley half include the cylindrical portion and the cylindrical portion. And a main body portion extending radially outward.

  Here, the cylindrical portion of the driving-side fixed pulley half is extrapolated to a corresponding driving shaft, and the cylindrical portion of the driving-side movable pulley half is extrapolated to the cylindrical portion of the driving-side fixed pulley half. Has been. Similarly, the cylindrical portion of the driven-side fixed pulley half is extrapolated to the corresponding driven shaft, and the cylindrical portion of the driven-side movable pulley half is extrapolated to the cylindrical portion of the driven-side fixed pulley half. Has been.

In such a conventional configuration, the cylindrical portion of the stationary pulley half and the cylindrical portion of the movable pulley half have different dimensions with respect to the inner diameter and the outer diameter.
And since the outer diameter of the cylinder part of the fixed pulley half and the outer diameter of the cylinder part of the movable pulley half are different, the main body part fixed to the cylinder part of the fixed pulley half and the movable pulley half The main body portion fixed to the cylindrical portion has a different size with respect to the inner diameter.

  Accordingly, in the conventional configuration, a dedicated cylinder part and a main body part for forming the fixed pulley half and a dedicated cylinder part and a main body part for forming the movable pulley half are required, and the manufacturing cost increases.

  On the other hand, in the present embodiment, the driving-side fixed pulley half 110, the driving-side movable pulley half 120, the driven-side fixed pulley half 140, and the driven-side movable pulley half 150 are connected to the cylinder. The pulley forming body 200 including the portion 210 and the main body portion 230 is used as a common material. Therefore, cost reduction by sharing parts as much as possible can be effectively achieved.

  In the present embodiment, as shown in FIGS. 2, 3 and 7A, the cylindrical portion 210 of the pulley forming body 200 forming the fixed pulley halves 110 and 140 on the driving side and the driven side is A large-diameter portion 220 that is positioned on one end side in the axial direction and has a large outer diameter, and a small-diameter portion that extends from the large-diameter portion 220 to the other end side in the axial direction with a step 226 and has a small outer diameter. 225.

  According to such a configuration, the stepped portion 226 can be used as an engagement portion with which the inner ring member of the bearing member 90 (see FIG. 1) engages, and the fixed pulley halves 110 and 140 are connected to the corresponding shaft 50. It is possible to effectively prevent the stationary pulley halves 110, 140 from moving to the other side in the axial direction while being relatively rotatable around the axis with respect to (55).

  In addition, the said small diameter part 225 can be easily formed by cutting the outer peripheral surface of the axial direction predetermined area | region of the said cylinder part 210 of the said pulley formation body 200, for example.

  Preferably, as shown in FIG. 9, the cylindrical portion 210 of the pulley forming body 200 that forms the driven-side movable pulley halves 120 and 150 corresponds to the cylindrical portion 210 instead of the sliding groove 212. The driven shaft 55 is allowed to move from one side in the axial direction to the other side, and the cylindrical portion 210 is moved around the axial line of the driven shaft 55 in accordance with the movement of the cylindrical portion 210 from one side in the axial direction to the other side. A sliding groove 213 including a cam region 214 that moves from one side to the other can be formed.

  According to such a configuration, in addition to the shift based on the manual operation by the shift operation mechanism 170, the travel load of the drive wheel (the rear wheel 15R in the present embodiment) operatively connected to the driven shaft 55 is added. Automatic shifting can be realized.

  Further, in the present embodiment, the main body portion 230 and the cylindrical portion 210 of the pulley forming body 200 are formed by separate members and are fixed to each other by welding or the like.

  Specifically, as shown in FIGS. 7A and 7B, FIG. 8, and FIG. 9, the main body portion 230 is formed by a main body portion forming member 235, and the cylindrical portion 210 is different from the main body portion forming member 235. It is formed by a cylindrical part forming member 215 which is a separate body.

  The main body forming member 235 includes a radially inner portion 236 provided with a central hole having a predetermined inner diameter, and a radially extending portion extending radially outward from the radially inner portion 236 and provided with the conical surface 231. And an outer portion 237.

The tubular portion forming member 215 includes an insertion portion 216 that is inserted in contact with the central hole, and a flange portion 217 that extends radially outward at one axial end side of the insertion portion 216. Have.
In the configuration in which the cylindrical portion 210 includes the large diameter portion 220 and the small diameter portion 225, the large diameter portion 220 functions as the insertion portion 216 (see FIG. 7A).

  The radially inner portion 235 has an outer surface 236a and an inner surface 236b that face the same direction as the conical surface 231 and the opposite direction with respect to the axial direction.

The outer surface 236a acts as a hook engaging surface that engages with the hook 217.
That is, the cylindrical part forming member 215 is welded to the main body forming member 235 by welding or the like in a state where the flange part 217 is in contact with the outer surface 236a and the insertion part 216 is inserted into the through hole. It is fixed.

On the other hand, the inner surface 236b acts as a stopper for directly or indirectly locking one end of the corresponding biasing member 130, 160.
In the present embodiment, the inner surface 236b locks one end portion of the corresponding biasing member 130, 160 via the contact plate 136, 166.

Preferably, the outer surface 236a and the inner surface 236b are substantially orthogonal to the axial direction of the cylindrical portion 210.
According to such a configuration, the engagement of the flange portion 217 and the outer surface 236a and the engagement of the urging members 130 and 160 and the inner surface 236b can be stably performed.

Preferably, as shown in FIGS. 7A and 7B, the radially inner portion 236 is recessed from the radially inner end of the radially outer portion 237, and the flange portion 217 is It is configured to be located in a recess defined by the radially inner portion 236.
According to such a configuration, it is possible to stably fix the cylindrical portion 210 and the main body portion 230 while preventing the cylindrical portion 210 from protruding outward from the conical surface 231.

50 driving shaft 55 driven shaft 100 pulley type continuously variable transmission mechanism 110 driving side fixed pulley half body 120 driving side movable pulley half body 130 driving side biasing member 140 driven side fixed pulley half body 150 driven side movable pulley half body 160 driven side Biasing member 170 Speed change operation mechanism 180 Endless body 200 Pulley forming body 210 Cylinder part 211 Fixing hole 212 Sliding groove 213 Sliding groove 214 Cam region 215 Cylindrical part forming member 216 Insertion part 217 Groove part 220 Large diameter part 225 Small diameter part 226 Step 230 Body portion 231 Conical surface 235 Body portion forming member 236 Radial inner portion 236a Outer surface 236b Inner surface 237 Radial outer portion

Claims (5)

A pulley type continuously variable transmission mechanism that continuously changes the rotational speed of power transmitted from the drive shaft to the driven shaft,
A drive-side fixed pulley half supported by the drive shaft so as not to be rotatable relative to the drive shaft and not movable in the axial direction, and in a state of being opposed to the drive-side fixed pulley half cannot be rotated relative to the drive shaft and can move in the axial direction by a predetermined amount. A drive-side movable pulley half supported by the drive-side movable pulley half, a drive-side biasing member that biases the drive-side movable pulley half toward the drive-side fixed pulley half, and an axial direction that is relatively unrotatable to the driven shaft A driven-side fixed pulley half that is immovably supported, and a driven-side movable pulley half that is supported by the driven shaft so as not to rotate relative to the driven shaft and to move in the axial direction by a predetermined amount. A driven-side biasing member that biases the driven-side movable pulley half toward the driven-side fixed pulley half, wherein the biasing force is greater than that of the driving-side biasing member. A force member; A shift operating mechanism to increase the biasing force of the drive moving with the side biasing member in accordance with section operating force, narrow pressurized and the driven-side fixed pulley half body and movable on the drive side fixed pulley half body and the movable pulley half With an endless body that is confined to the pulley half,
Each of the pulley halves includes a cylindrical portion that is externally attached to a corresponding shaft so as to be movable in the axial direction, and a main body portion that extends radially outward from one axial end side of the cylindrical portion, and that is outward from the radially inner side. Common in that it includes a pulley forming body including a main body portion having a conical surface inclined so as to be located on the other end side of the cylindrical portion with respect to the axial direction of the cylindrical portion as going toward
Pins provided on corresponding shafts are engaged with the cylindrical portions of the pulley forming bodies forming the fixed pulley halves on the driving side and the driven side, and the cylindrical portions are axially oriented with respect to the corresponding shafts. A fixing hole is provided to fix it immovably .
A pin provided on a corresponding shaft is engaged with a cylindrical portion of the pulley forming body that forms the movable pulley halves on the driving side and the driven side, and the cylindrical portion has a predetermined distance from the corresponding shaft. A pulley-type continuously variable transmission mechanism characterized in that a sliding groove is provided that allows movement only along the axial direction.   The cylinder part of the pulley forming body forming the driving and driven fixed pulley halves is located on one end side in the axial direction, and has a large diameter part with a large outer diameter, and a step from the large diameter part. The pulley-type continuously variable transmission mechanism according to claim 1, further comprising a small-diameter portion that extends toward the other end in the axial direction and has a small outer diameter.   The sliding groove provided in the cylindrical portion of the pulley forming body forming the driven-side movable pulley half is adapted to move as the cylindrical portion moves from one side to the other side in the axial direction of the corresponding driven shaft. The pulley-type continuously variable transmission mechanism according to claim 1 or 2, further comprising a cam region that moves the shaft from one side to the other side around the axis of the driven shaft. The main body part is formed by a main body part forming member, and the cylindrical part is formed by a cylindrical part forming member that is separate from the main body part forming member,
The main body forming member includes a radially inner portion provided with a central hole having a predetermined inner diameter, and a radially outer portion extending radially outward from the radially inner portion and provided with the conical surface. Have
The cylindrical portion forming member has an insertion portion that is inserted in contact with the central hole, and a flange portion that extends radially outward at one end side in the axial direction of the insertion portion,
The radially inner portion has an outer surface and an inner surface facing in the same direction as the conical surface and in the opposite direction with respect to the axial direction,
The cylindrical part forming member is fixed to the main body part forming member in a state where the collar part is in contact with the outer surface and the insertion part is inserted into the through hole,
The pulley according to any one of claims 1 to 3, wherein an inner surface of the radially inner portion acts as a stopper for directly or indirectly locking one end portion of the corresponding biasing member. Type continuously variable transmission mechanism.   The radially inner portion is recessed from a radially inner end of the radially outer portion, and the flange portion of the tubular portion forming member is positioned in a recess defined by the radially inner portion. The pulley type continuously variable transmission mechanism according to claim 4, wherein the pulley type continuously variable transmission mechanism is provided.

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