JP4873558B2 - Belt-type continuously variable transmission and straddle-type vehicle equipped with the same - Google Patents

Description

  The present invention relates to a belt-type continuously variable transmission, a straddle-type vehicle including the belt-type continuously variable transmission, and a pressing body of the belt-type continuously variable transmission.

  Conventionally, a straddle-type vehicle including a belt type continuously variable transmission is known. The belt-type continuously variable transmission includes a primary sheave to which driving force from an engine is transmitted and a secondary sheave to which driving force is transmitted from the primary sheave via a belt. At least one of the primary sheave and the secondary sheave is configured such that the belt winding diameter is variable, and the speed is changed by changing the ratio of the belt winding diameter of the primary sheave to the same winding diameter of the secondary sheave. The ratio is adjustable.

  In detail, the primary sheave is generally a fixed sheave body (hereinafter referred to as a “primary fixed sheave body”) and a cross section of the primary fixed sheave body facing the primary fixed sheave body and a belt wound around the primary fixed sheave body. A movable sheave body (hereinafter referred to as a “primary movable sheave body”) that forms a V-shaped belt groove. The primary movable sheave body is displaceable in the direction of the rotation axis with respect to the primary fixed sheave body (that is, displaceable in the direction of approaching or leaving).

  In addition, the primary sheave is provided with a cam plate that faces the surface of the primary movable sheave body opposite to the primary fixed sheave body. The cam plate is formed in a tapered shape so as to be closer to the primary movable sheave body toward the radially outer side. A plurality of roller weights are disposed between the primary movable sheave body and the cam plate, which are displaceable in the radial direction of the primary sheave and rotate with the rotation of the primary movable sheave body and the cam plate. On the other hand, the primary movable sheave body is formed with a plurality of stoppers that project toward the outer periphery of the cam plate. This stopper determines the maximum displacement position of the roller weight on the outer side in the radial direction. The roller weight usually includes a cylindrical or columnar metal weight main body and a covering member. The covering member is formed so as to cover the surface (specifically, the outer peripheral surface) of the weight main body that contacts the metal primary movable sheave body and the cam plate.

  Similarly to the primary sheave, the secondary sheave also has a fixed sheave body (hereinafter referred to as a “secondary fixed sheave body”) and a secondary fixed sheave body that is opposed to the secondary sheave body, and has a cross-section approximately V around which the belt is wound together with the secondary fixed sheave body. And a movable sheave body (hereinafter referred to as “secondary movable sheave body”) that forms a letter-shaped belt groove. The secondary movable sheave body is biased by a spring in a direction in which the width of the belt groove is narrowed (that is, a direction in which the distance from the secondary fixed sheave body is narrowed).

  When the rotation speed of the primary sheave is low, the belt groove width of the secondary sheave is kept narrow by the biasing force of the spring. For this reason, the winding diameter of the belt of the secondary sheave is relatively large. As a result, the belt is pulled closer to the secondary sheave, and the roller weight is held closer to the rotating shaft by the force, and the width of the belt groove of the primary sheave is kept relatively wide. As a result, the gear ratio becomes large.

  As the rotational speed of the primary sheave increases, the centrifugal force generated in the roller weight increases with it. Thereby, the roller weight moves toward the radially outer side while pressing the primary movable sheave body toward the primary fixed sheave body. As a result, the belt winding diameter of the primary sheave increases. Along with this, the belt is drawn toward the primary sheave side, and the belt winding diameter of the secondary sheave becomes small. Therefore, the rotational speed of the primary sheave, that is, the rotational speed of the engine increases, and the gear ratio becomes smaller. The speed ratio becomes the minimum when the roller weight reaches the maximum displacement position where it abuts against the stopper and the width of the belt groove of the primary sheave becomes minimum (hereinafter, the speed ratio at this time is referred to as “minimum speed ratio”). .)

  Thus, in the belt-type continuously variable transmission, the roller weight is displaced inward and outward in the radial direction while sliding on the primary movable sheave body and the cam plate as the speed ratio changes. For this reason, with time, the portions of the roller weight that come into contact with the primary movable sheave body and the cam plate are particularly greatly worn and deformed. Therefore, the width of the roller weight in the facing direction between the primary movable sheave body and the cam plate decreases with time. As a result, there is a problem that the width of the belt groove of the primary sheave increases with time. That is, there is a problem that the minimum gear ratio changes with time.

In view of such a problem, for example, Patent Document 1 discloses a technique in which the stopper is shaped to promote wear on a part of the outer surface of the roller weight. According to this technique, when the roller weight receives a centrifugal force and is pressed against the stopper, only a part of the outer surface of the roller weight is actively worn. Due to this wear, the pressing body bites into the stopper and further moves outward in the radial direction. As a result, the speed ratio can be changed in a direction to reduce the speed ratio by narrowing the width of the belt groove of the primary sheave. In other words, it is possible to correct an increase in the gear ratio due to the roller weight coming into contact with the cam plate or the like and being worn. Therefore, the change of the speed ratio at the minimum speed ratio can be suppressed to a small amount by a simple method of simply changing the shape of the stopper.
International Publication WO2005 / 090828 A1 Pamphlet

  However, as a result of intensive studies by the inventors of the present application, in the technique described in Patent Document 1, when the covering member is cracked or the covering member is cracked, the covering member is rapidly damaged, and the life of the roller weight is shortened. It was discovered for the first time. That is, the covering member is normally fixed so as not to be displaceable with respect to the weight main body, but if the covering member is cracked or cracked, the covering member is not firmly fixed to the weight main body. For this reason, the moving operation of the roller weight inward and outward in the radial direction is not smoothly performed, and the covering member is severely damaged by colliding with the weight main body and other members disposed in the vicinity. As a result, the life of the roller weight may be shortened.

  The present invention has been made in view of such a point, and an object of the present invention is to suppress a change in the speed ratio at the minimum speed ratio of the belt-type continuously variable transmission and improve durability. is there.

A first belt-type continuously variable transmission according to the present invention includes a primary sheave that rotates around a rotation shaft, a secondary sheave, and a belt that is wound around the primary sheave and the secondary sheave. It is a step transmission. The primary sheave is opposed to the first sheave body and the first sheave body and is disposed so as to be relatively displaceable in the axial direction of the first sheave body. A second sheave body that forms a belt groove to be wound, a pressing body, and a covering member that covers at least a part of the surface of the pressing body, and with the rotation of the second sheave body The belt rotates around the rotating shaft, and moves to the outside of the second sheave body in the radial direction while pressing the second sheave body toward the first sheave body by the centrifugal force generated during the turning. When the pressing body that narrows the width of the groove and the second sheave body reaches the minimum speed ratio position that narrows the width of the belt groove, the second body of the pressing body comes into contact with the covering member of the pressing body. The displacement of the sheave body in the radial direction And a stopper, the has. The stopper has a shape that promotes wear of part of the covering member. At least part of a portion of the surface of the pressing body that is covered with the covering member is formed with a concavo-convex portion including a convex portion or a concave portion that engages with the covering member. At least two uneven portions are formed, and a portion of the covering member whose wear is promoted by the stopper is located between the at least two uneven portions in the circumferential direction of the primary sheave.

A second belt-type continuously variable transmission according to the present invention includes a primary sheave that rotates about a rotation shaft, a secondary sheave, and a belt that is wound around the primary sheave and the secondary sheave. It is a step transmission. The primary sheave is opposed to the first sheave body and the first sheave body and is disposed so as to be relatively displaceable in the axial direction of the first sheave body. A second sheave body that forms a belt groove to be wound, a pressing body, and a covering member that covers at least a part of the surface of the pressing body, and with the rotation of the second sheave body Swiveling around the rotation axis, and by the centrifugal force generated at the time of swiveling, the second sheave body is pressed toward the first sheave body while moving outward in the radial direction of the second sheave body. And when the second sheave body reaches the minimum gear ratio position where the width of the belt groove is most narrowed, it comes into contact with the covering member of the pressure body and the second body of the pressure body Stroke that regulates the radial displacement of the sheave body It has path and, the. The stopper includes a contact surface that contacts the covering member of the pressing body and a convex portion that is formed on the corresponding contact surface and protrudes toward the pressing body. At least part of a portion of the surface of the pressing body that is covered with the covering member is formed with a concavo-convex portion including a convex portion or a concave portion that engages with the covering member. At least two uneven portions are formed, and a portion of the covering member whose wear is promoted by the stopper is located between the at least two uneven portions in the circumferential direction of the primary sheave.

  The pressing body may be a roller (that is, a member that displaces while rotating) or a slider (a member that slides).

  According to the present invention, it is possible to suppress the change in the speed ratio at the minimum speed ratio and improve the durability.

(Embodiment 1)
The first embodiment effectively suppresses the damage of the covering member by devising the shape of the roller weight, particularly the surface shape of the portion of the roller weight that contacts the covering member of the weight body, together with the shape of the stopper, Therefore, it is possible to effectively suppress the change in the speed ratio at the minimum speed ratio and improve the durability. Hereinafter, the specific configuration of the first embodiment will be described in detail with reference to the drawings. In the first embodiment, an off-road type motorcycle 1 shown in FIG. 1 will be described as an example of a saddle-ride type vehicle implementing the present invention. However, the saddle riding type vehicle according to the present invention is not limited to this, and may be, for example, a motorcycle other than the off-road type (motorcycle type, scooter type, so-called moped type motorcycle, etc.). Good. Further, it may be a straddle-type vehicle other than a motorcycle (for example, ATV: All Terrain Vehicle, snowmobile, etc.).

-Schematic configuration of motorcycle 1-
FIG. 1 is a side view of a motorcycle 1 according to the first embodiment. First, a schematic configuration of the motorcycle 1 will be described with reference to FIG. In the following description, the front, rear, left, and right directions refer to directions viewed from a passenger seated on the seat 11.

  The motorcycle 1 includes a body frame 2. The vehicle body frame 2 includes a head pipe 3, a down tube 4 extending downward from the head pipe 3, and a seat pillar 5 extending rearward from the head pipe 3. The lower end of the head pipe 3 is connected to the front wheel 7 via a front fork 6 or the like. A rear arm 8 extending rearward is supported near the lower end of the seat pillar 5. The rear end of the rear arm 8 is connected to the rear wheel 9. A cover 10 that covers the vehicle body frame 2 is disposed above the vehicle body frame 2. A seat 11 is provided slightly behind the center of the cover 10.

  An engine unit 12 supported by the down tube 4 and the seat pillar 5 is disposed between the down tube 4 and the seat pillar 5. As shown in FIG. 2, the engine unit 12 includes an engine 13, a belt-type continuously variable transmission (hereinafter referred to as “CVT”) 14 (see FIG. 2), a speed reduction mechanism 16, and the like. The driving force generated in the engine unit 12 is transmitted to the rear wheel 9 via power transmission means (not shown) such as a chain belt. Here, the engine 13 is described as a four-cycle single-cylinder engine, but the engine 13 may be a two-cycle engine, for example. A multi-cylinder engine may also be used.

-Configuration of engine unit 12-
Next, the configuration of the engine unit 12 will be described with reference to FIG. The engine unit 12 includes an engine 13, a CVT 14, a centrifugal clutch 15, and a speed reduction mechanism 16. For convenience of explanation, a part of the structure of the speed reduction mechanism 16 is omitted in FIG.

  The engine 13 includes a crankcase 17, a substantially cylindrical cylinder 18, and a cylinder head 19. The crankcase 17 is composed of two case blocks, a first case block 17a located on the left side and a second case block 17b located on the right side. The first case block 17a and the second case block 17b are arranged to face each other in the vehicle width direction. The cylinder 18 is connected obliquely in front of the crankcase 17 (see also FIG. 1). The cylinder head 19 is connected to the tip of the cylinder 18.

  A crankshaft 20 extending horizontally in the vehicle width direction is accommodated in the crankcase 17. The crankshaft 20 is supported by the first case block 17a and the second case block 17b via bearings 21 and 22.

  A piston 23 is slidably inserted into the cylinder 18. One end of a connecting rod 24 is connected to the crankshaft 20 side of the piston 23. The other end of the connecting rod 24 is connected to a crank pin 59 disposed between the left crank arm 20a and the right crank arm 20b of the crankshaft 20. As a result, the piston 23 reciprocates in the cylinder 18 as the crankshaft 20 rotates.

  The cylinder head 19 is formed with a recess 19a connected to the internal space of the cylinder 18, and an intake port and an exhaust port (not shown) communicating with the recess 19a. A spark plug 25 is inserted into and fixed to the cylinder head 19 so that the ignition portion at the tip is exposed in the recess 19a.

  A cam chain chamber 26 that connects the inside of the crankcase 17 and the inside of the cylinder head 19 is formed on the left side in the cylinder 18. A timing chain 27 is disposed inside the cam chain chamber 26. The timing chain 27 is wound around the crankshaft 20 and the camshaft 28. As a result, the camshaft 28 is rotated with the rotation of the crankshaft 20, and an intake valve and an exhaust valve (not shown) are opened and closed.

  A generator case 30 that houses the generator 29 is detachably attached to the left side of the front half of the first case block 17a. On the other hand, a transmission case 31 that houses the CVT 14 is attached to the right side of the second case block 17b.

  An opening is formed on the right side of the second half of the second case block 17b. This opening is closed by the clutch cover 32. The clutch cover 32 is detachably fixed to the second case block 17b by bolts 33.

  The transmission case 31 is formed independently of the crankcase 17. The transmission case 31 includes an inner case 31a that covers the inner side (left side) of the CVT 14 in the vehicle width direction and an outer case 31b that covers the outer side (right side) of the CVT 14 in the vehicle width direction. The inner case 31 a is attached to the right side of the crankcase 17. On the other hand, the outer case 31b is attached to the right side of the inner case 31a, and a belt chamber 34 is defined by the outer case 31b and the inner case 31a.

  The left end portion of the crankshaft 20 passes through the first case block 17 a and reaches the generator case 30. A generator 29 is attached to the left end of the crankshaft 20. Specifically, the generator 29 includes a stator 29a and a rotor 29b disposed to face the stator 29a. The stator 29a is fixed to the generator case 30 so that it cannot be rotated or displaced. On the other hand, the rotor 29b is fixed to a sleeve 35 that rotates together with the crankshaft 20 so as not to rotate. Thereby, with rotation of the crankshaft 20, the rotor 29b rotates with respect to the stator 29a, and electric power generation is performed.

  The belt chamber 34 accommodates the CVT 14. The CVT 14 includes a primary sheave 36 and a secondary sheave 37 disposed behind the primary sheave 36. The crankshaft 20 passes through the second case block 17b and the inner case 31a and extends to the belt chamber 34, and its right side portion (strictly, the right side portion from the bearing 22) constitutes the primary sheave shaft 20c. is doing. The primary sheave 36 is pivotally supported by the primary sheave shaft 20c. Thereby, the primary sheave 36 rotates with the rotation of the crankshaft 20.

  On the other hand, a secondary sheave shaft 38 that extends through the inner case 31 a and the clutch cover 32 and extends into the crankcase 17 is disposed in the rear half of the transmission case 31. The secondary sheave shaft 38 is attached to the clutch cover 32 via a bearing 39. The secondary sheave 37 is pivotally supported by the secondary sheave shaft 38 in the belt chamber 34.

  A belt (for example, a (resin block) V belt) 41 is wound around the secondary sheave 37 and the primary sheave 36. Therefore, when the primary sheave 36 rotates together with the crankshaft 20, the torque is transmitted to the secondary sheave 37 via the belt 41, and the secondary sheave shaft 38 rotates together with the secondary sheave 37. The rotation of the secondary sheave shaft 38 is transmitted to the rear wheel 9 through the centrifugal clutch 15, the speed reduction mechanism 16, and power transmission means (not shown) such as a belt or a chain.

-Specific configuration of CVT14-
Hereinafter, the configuration of the CVT 14 will be described in more detail with reference to FIG. As described above, the CVT 14 includes the primary sheave 36, the secondary sheave 37, and the belt 41, and is accommodated in the belt chamber 34. The primary sheave 36 includes a tapered fixed sheave body 36a and a movable sheave body 36b. The fixed sheave body 36a is fixed to the right end portion of the primary sheave shaft 20c so as to approach the outer side (right side) in the vehicle width direction toward the outer side in the radial direction, and rotates together with the primary sheave shaft 20c. On the other hand, the movable sheave body 36b is opposed to the fixed sheave body 36a from the center (left side) of the fixed sheave body 36a, and is arranged so as to approach the inner side (left side) in the vehicle width direction radially outward. . The movable sheave body 36b is non-rotatable to the primary sheave shaft 20c, and is attached to be slidable in the axial direction. That is, the fixed sheave body 36a and the movable sheave body 36b form a substantially V-shaped belt groove 36c around which the belt 41 is wound, and the width of the belt groove 36c is such that the movable sheave body 36b is fixed to the fixed sheave body. It is variable by being displaced relative to 36a.

  A cooling fan 46 is provided on the outer side surface (the right side surface in FIG. 2) of the fixed sheave body 36a. A plurality of cam surfaces 42 extending in the radial direction are formed on the left side surface of the movable sheave body 36b. A cam plate 43 is disposed on the left side of the movable sheave body 36b so as to face the cam surface 42 thereof. Between the cam plate 43 and the cam surface 42, a plurality of substantially cylindrical (or substantially columnar) roller weights (pressing bodies) 44 that are not displaceable in the circumferential direction but are displaceable in the radial direction are arranged. ing. The cam surface 42 is formed in a tapered shape so as to approach the cam plate 43 radially outward from the center. On the other hand, the cam plate 43 is also tapered so as to approach the cam surface 42 radially outward from the center. That is, the width between the cam plate 43 and the cam surface 42 becomes narrower radially outward.

  The secondary sheave 37 includes a fixed sheave body 37a positioned on the inner side in the vehicle width direction, and a movable sheave body 37b positioned on the outer side in the vehicle width direction and disposed opposite to the fixed sheave body 37a. The fixed sheave body 37a is fixed to the secondary sheave shaft 38 so as to approach the inner side (left side) in the vehicle width direction toward the radially outer side, and rotates together with the secondary sheave shaft 38. On the other hand, the movable sheave body 37b is fixed to the secondary sheave shaft 38 so as to approach the outer side (right side) in the vehicle width direction toward the outer side in the radial direction. The movable sheave body 37b is non-rotatable to the secondary sheave shaft 38, and is attached to be slidable in the axial direction. That is, the fixed sheave body 37a and the movable sheave body 37b form a belt groove 37c having a substantially V-shaped cross section around which the belt 41 is wound. The width of the belt groove 37c is such that the movable sheave body 37b is fixed to the fixed sheave body. It is variable by being displaced relative to 37a. The shaft portion of the fixed sheave body 37a has a cylindrical slide collar and is spline-fitted to the secondary sheave shaft 38.

  A compression coil spring 45 is disposed on the outer side (right side) of the movable sheave body 37b in the vehicle width direction. The movable sheave body 37b is urged by the compression coil spring 45 against the fixed sheave body 37a. As a result, the width of the belt groove 37c is minimized when the engine speed is low, for example, in an idling state.

  In the CVT 14, the roller weight 44 presses the primary movable sheave body 36b toward the primary fixed sheave body 36a (rightward), and the compression coil spring 45 biases the secondary movable sheave body 37b toward the secondary fixed sheave body 37a (leftward). The transmission ratio is determined by the ratio with the force to be applied.

  More specifically, when the rotational speed of the primary sheave shaft 20c is low, the width of the belt groove 37c of the secondary sheave 37 is narrowed by the urging force of the compression coil spring 45 (from the secondary sheave shaft 38 of FIG. 2). (See also the state of the secondary sheave 37 drawn on the upper side (maximum speed ratio position)). For this reason, the belt winding diameter of the secondary sheave 37 is increased, and the belt 41 is drawn toward the secondary sheave 37 side. As a result, the primary movable sheave body 36b is pressed toward the cam plate 43 by the belt 41, and the width of the belt groove 36c of the primary sheave 36 is widened (the primary sheave 36 drawn below the primary sheave shaft 20c in FIG. 2). (See the maximum gear ratio position). As a result, the gear ratio increases.

  On the other hand, when the rotational speed of the primary sheave shaft 20c increases, the roller weight 44 receives the centrifugal force and moves outward in the radial direction. Here, since the distance between the primary movable sheave body 36b and the cam plate 43 becomes narrower toward the outer side in the radial direction, the primary movable sheave body 36b moves as the roller weight 44 moves outward in the radial direction. It is pressed toward the primary fixed sheave body 36a (toward the right). Then, the primary movable sheave body 36b slides toward the primary fixed sheave body 36a, and the belt groove 36c is narrowed (see the state of the primary sheave 36 (minimum speed ratio position) drawn above the primary sheave shaft 20c in FIG. 2). ). As a result, the belt winding diameter of the primary sheave 36 is increased. Along with this, the belt 41 is drawn toward the primary sheave 36, and the belt 41 opposes the urging force of the compression coil spring 45 and presses the secondary movable sheave body 37b away from the secondary fixed sheave body 37a (rightward). As a result, the secondary movable sheave body 37b slides away from the secondary fixed sheave body 37a, and the belt winding diameter of the secondary sheave 37 decreases (the secondary sheave 37 drawn below the secondary sheave shaft 38 in FIG. 2). (Refer to the minimum gear ratio position). As a result, the gear ratio becomes small.

  The materials of the primary fixed sheave body 36a, the primary movable sheave body 36b, the secondary fixed sheave body 37a, the secondary movable sheave body 37b, and the cam plate 43 are not particularly limited, and examples thereof include iron, aluminum, and stainless steel materials. The metal represented may be sufficient. Further, the surface may be subjected to surface treatment such as chrome plating.

  Further, since the roller weight 44 changes the distance between the cam surface 42 and the cam plate 43 by moving inward and outward in the radial direction, any roller weight can be used as long as it can move inward and outward in the radial direction. Something like that. For example, it may be spherical or bowl-shaped. Moreover, it may move while rotating, or it may slide.

-Configuration of primary sheave 36 and roller weight 44-
Hereinafter, the configuration of the primary sheave 36 and the roller weight 44 according to the first embodiment will be described in more detail with reference to FIGS. First, the configuration of the primary movable sheave body 36b will be described in detail with reference to FIGS.

<Configuration of primary movable sheave body 36b>
FIG. 3 is a rear view of the primary movable sheave body 36b as viewed from the center side in the vehicle width direction. A plurality of guide portions 51 in which the roller weights 44 are disposed are formed on the back surface of the primary movable sheave body 36b. Specifically, the six guide parts 51 are radially formed so as to extend radially outward from the boss part 50, respectively. The six guide portions 51 constitute three guide portion pairs including two guide portions 51 arranged adjacently in a V shape, and these three guide portion pairs are substantially equal around the boss portion 50. Arranged at intervals. Each guide portion 51 includes a cam surface 42 and a pair of guide walls 52a and 52b. As shown in FIG. 2, the cam surface 42 extends obliquely toward the cam plate 43 toward the radially outer side. As shown in FIG. 5, each of the guide walls 52 a and 52 b rises from the end side of the cam surface 42 so as to face each other in parallel and extends in the radial direction along the end side of the cam surface 42. The distance between the guide wall 52a and the guide wall 52b is set substantially equal to the height of the roller weight 44, and the roller weight 44 can displace the guide portion 51 in the radial direction along the guide walls 52a and 52b. It has become.

  A stopper 53 erected from the cam surface 42 toward the cam plate 43 is provided at the radially outer end of each guide portion 51 (see also FIG. 2). The stopper 53 determines the radially outer end of the movable range of the roller weight 44. Specifically, when the primary movable sheave body 36b is positioned at the minimum speed ratio position where the width of the belt groove 36c is the narrowest, the roller weight 44 contacts the roller weight 44 (specifically, the covering member 44a of the roller weight 44). The further displacement to the radial direction outer side of is controlled.

  As shown in FIG. 3, the stopper surface 54 that contacts the roller weight 44 of the stopper 53 is formed in a shape that actively wears a part of the outer surface of the roller weight 44 (specifically, the covering member 44a). Yes. Specifically, as shown in FIGS. 5 and 6, a linear protrusion 55 having a rectangular cross section that protrudes toward the roller weight 44 is formed at substantially the center in the circumferential direction of the primary sheave 36. ing. As shown in FIG. 7, the convex portion 55 comes into contact with the outer surface of the roller weight 44, and wear of the contact portion is promoted as compared with other portions.

  In the present specification, “the portion where wear is promoted by the stopper of the covering member” means the other portion of the portion that contacts the stopper when the pressing body (roller weight or the like) is in a new state. The part where the surface pressure is higher. Specifically, in the first embodiment, a portion of the covering member 44a that contacts the convex portion 55 corresponds to “a portion where wear is promoted by the stopper of the covering member”.

<Configuration of roller weight 44>
FIG. 8A is a perspective view of the roller weight 44. FIG. 8B is a view taken in the direction of arrows VIII (b) -VIII (b) in FIG. The roller weight 44 includes a cylindrical weight metal main body 44b (for example, iron, aluminum, stainless steel, etc.) and a covering member 44a that covers the outer peripheral surface of the weight main body 44b. The weight main body 44b may not be made of metal, but preferably has a specific gravity of a certain level or more from the viewpoint of generating a certain level of centrifugal force. On the other hand, it is preferable that the covering member 44a has a lower hardness than the weight main body 44b. Specifically, the covering member 44a is preferably made of resin.

  In the first embodiment, at least a part (or the whole) of the outer peripheral surface 44c covered with the covering member 44a is formed with a concavo-convex portion including a convex portion or a concave portion that engages with the covering member 44a. In other words, the outer peripheral surface 44c covered with the covering member 44a is a so-called rough surface in which fine irregularities are formed, a smooth surface or a surface in which a concave portion or a convex portion is formed on a part of the rough surface, a concave surface or a convex surface ( The surface shape may be a rough surface or a smooth surface), or a concave surface or a convex surface (the surface shape may be a rough surface or a smooth surface). It is formed in the surface in which the recessed part or the convex part was formed.

  Specifically, in the first embodiment, the entire outer peripheral surface 44c is formed into a rough surface. In addition, the method of forming the outer peripheral surface 44c into a rough surface is not particularly limited, and examples thereof include a mechanical processing method using blast and knurling, and a chemical processing method typified by etching. .

  The thickness t of the covering member 44a (see FIG. 8B, specifically, the thickness of the portion in contact with the convex portion 55) t is the height H of the convex portion 55 in the radial direction of the primary sheave 36 (see FIG. 5). ) Is set larger than. More specifically, the thickness t of the covering member 44 a is set to be 1 mm or more larger than the height H of the convex portion 55. Further, it is preferably set to 0.01 times or more of the outer peripheral radius of the roller weight 44.

-Action and effect-
Next, operations and effects of the first embodiment will be described with reference to FIGS. 9 and 10 disclose a state in which the movable sheave body 36b of the primary sheave 36 is moved to the position of the minimum gear ratio through the new roller weight 44. FIG. In this state, the covering member 44 a of the roller weight 44 is in contact with the cam plate 43, the convex portion 55, and the cam surface 42. When the portion of the covering member 44a that comes into contact with the cam plate 43 and the cam surface 42 begins to wear, the distance between the cam plate 43 and the cam surface 42 becomes shorter. Accordingly, the width of the belt groove 36c of the primary sheave 36 is widened, and the belt winding diameter is reduced. As a result, the minimum gear ratio becomes smaller than when not in use. That is, the minimum gear ratio changes with time due to wear of portions of the covering member 44a that are in contact with the cam plate 43 and the cam surface 42.

  However, according to the first embodiment, when the movable sheave body 36b slides to the position of the minimum speed ratio, the convex portion 55 formed on the stopper surface 54 contacts the covering member 44a of the roller weight 44. For this reason, the surface pressure of the contact portion 36d that contacts the convex portion 55 of the covering member 44a becomes higher than the surface pressure of other portions. In addition, the covering member 44a is formed of a material having a relatively low hardness, specifically, a resin. For this reason, the contact part 36d is actively worn compared to the other parts.

  11 and 12 disclose a state in which the contact portion 36d of the covering member 44a is locally worn. As shown in FIGS. 11 and 12, due to local wear of the abutting portion 36d, a concave portion 36e having a shape corresponding to the shape of the convex portion 55 is formed, and the convex portion 55 bites into the covering member 44a. . As a result, the roller weight 44 moves toward the radially outer side of the movable sheave body 36b by an amount corresponding to the height H of the convex portion 55. As a result, the width of the belt groove 36c is reduced, and the belt winding diameter of the primary sheave 36 is increased. That is, the decrease in the belt winding diameter caused by wear of the portion of the covering member 44a that contacts the cam plate 43 and the cam surface 42 is corrected by the increase in belt winding diameter caused by the wear of the contact portion 36d. As a result, the relationship of the speed ratio to the rotational speed of the primary sheave shaft 20c and the change with time of the minimum speed ratio are effectively suppressed.

  However, as the wear of the contact portion 36d progresses, the depth of the recess 36e becomes deeper, and there is a possibility that the covering member 44a is cracked by the recess 36e. Further, when the wear further progresses, the recess 36e may reach the weight main body 44b. Then, the movement operation of the roller weight 44 inward and outward in the radial direction is not smoothly performed (rattle), and the covering member 44a collides with the weight main body 44b and the cam plate 43 disposed in the vicinity, or slides strongly. It will move and be severely damaged. As a result, the life of the roller weight 44 is shortened.

  However, in the first embodiment, a portion of the outer peripheral surface 44c of the weight main body 44b that is covered with the covering member 44a is formed on a surface that is engaged with the covering member 44a, specifically, a rough surface. For this reason, even if the covering member 44a is cracked or the recess 36e reaches the weight main body 44b, the frictional force between the outer peripheral surface 44c of the weight main body 44b and the inner peripheral surface of the covering member 44a. The covering member 44a is still fixed to the weight body 44b. For this reason, the smoothness of the movement operation of the roller weights 44 in the radial direction is not impaired, and damage to the covering member 44a is suppressed. Therefore, the durability of the belt type continuously variable transmission 14 is improved.

  Further, in the first embodiment, the thickness t (see FIG. 8B) of the covering member 44a is set larger than the height H (see FIG. 5) of the convex portion 55 in the radial direction of the primary sheave 36. Yes. For this reason, even when the convex portion 55 is completely recessed into the covering member 44a, the concave portion 36e still does not reach the weight main body 44b. Accordingly, the covering member 44a is less likely to be broken or divided. Furthermore, it is particularly preferable that the thickness (t) of the covering member 44a is set to be 1 mm or more larger than the height (H) of the convex portion 55 from the viewpoint of effectively suppressing cracking / splitting of the covering member 44a. Further, it is particularly preferable to set the outer peripheral radius of the roller weight 44 to 0.01 times or more.

  As mentioned above, although the example of the 1st preferable form which implemented this invention has been demonstrated, the part (namely, outer peripheral surface 44c) coat | covered with the coating | coated member 44a of the surface of the weight main body 44b does not necessarily need to be a rough surface. Good. That is, an uneven part including a convex part or a concave part engaging with the covering member 44a is formed on at least a part of the portion (outer peripheral surface 44c) covered with the covering member 44a on the surface of the weight main body 44b. The covering member 44a only needs to be fixed to the weight main body 44b even when a crack or the like occurs in 44a. Specifically, one or a plurality of concave portions or convex portions may be formed on the outer peripheral surface 44c. In addition, the outer peripheral surface 44c is concave in the cross section orthogonal to the primary sheave shaft 20c (in the cross section orthogonal to the primary sheave shaft 20c, the lowest point thereof faces the portion that contacts the convex portion 55 of the covering member 44a. Preferably). In the following Embodiments 2 and 3, an example in which a concave portion is formed on the outer peripheral surface 44c will be described. In the following description of Embodiments 2 and 3, FIGS. 1 to 7, FIG. 8A, and FIGS. 9 and 11 are referred to in common. In addition, components having substantially the same function are described with reference numerals common to the first embodiment, and description thereof is omitted.

(Embodiment 2)
FIG. 13 is a cross-sectional view of the roller weight 144 according to the second embodiment. FIG. 14 is a schematic plan view showing the positional relationship between the roller weight 144 and the convex portion 55 of the stopper 53 in the second embodiment.

  The roller weight 144 according to the second embodiment includes a metal weight main body 144b formed in a columnar shape and a covering member 144a. On the outer peripheral surface 144c of the weight main body 144b, a plurality of (specifically, two) annular grooves 144d having a rectangular cross section extending in the circumferential direction are formed. Specifically, as shown in FIG. 14, a portion that contacts the convex portion 55 of the covering member 44 a (a portion whose wear is promoted by the stopper 53) is positioned between the two annular grooves 144 d. The covering member 144a covers the outer peripheral surface 144c of the weight main body 144b and is formed so as to bite into the two annular grooves 144d formed on the outer peripheral surface 144c.

  As described above, since the covering member 144a is engaged with the annular groove 144d and the portion of the covering member 44a that contacts the convex portion 55 is located between the two annular grooves 144d, Even when the covering member 144a is cracked by the friction or the protrusion 55 reaches the weight main body 144b, the covering member 144a is still fixed to the weight main body 144b. For this reason, the smoothness of the movement operation of the roller weight 144 in the radial direction is not impaired, and damage to the covering member 144a is suppressed.

  From the viewpoint of more effectively suppressing the cracking / splitting of the covering member 144a, the thickness of the portion of the covering member 144a with which the convex portion 55 abuts is set to be larger than the height of the convex portion 55. It is preferable that the height of the portion 55 is set to be 1 mm or more. Further, it is preferable that the thickness of the portion of the covering member 144a with which the convex portion 55 abuts is set to 0.01 times or more the outer peripheral radius of the roller weight 144. As in the first embodiment, the outer peripheral surface 144c of the weight main body 144b may be a rough surface.

  As described above, in the second embodiment, the example in which the two annular grooves 144d are formed on the outer peripheral surface 144c of the weight main body 144b has been described. However, the present invention is not limited to this configuration. It suffices if the covering member 144a is formed in such a manner that it engages with the outer peripheral surface 144c. For example, three or more annular grooves 144d may be formed. Moreover, the recessed part formed in the outer peripheral surface 144c of the weight main body 144b does not need to be annular. Furthermore, instead of the annular groove 144d, one or a plurality of convex portions (for example, an annular convex portion) may be formed.

(Embodiment 3)
FIG. 15 is a cross-sectional view of the roller weight 244 in the third embodiment. FIG. 16 is a schematic plan view showing the positional relationship between the roller weight 244 and the convex portion 55 of the stopper 53 in the third embodiment. FIG. 17 is a cross-sectional view showing a state in which the roller weight 244 bites into the convex portion 55 of the stopper 53.

  As shown in FIG. 15, the roller weight 244 includes a cylindrical metal weight main body 244b and a covering member 244a. An annular groove 244d having a rectangular cross section extending in the circumferential direction is formed on the outer peripheral surface 244c of the weight body 244b. The annular groove 244d is located at a position (hereinafter, referred to as a portion where the wear is promoted by the stopper 53 of the covering member 244a (a portion that comes into contact with the convex portion 55 of the covering member 244a) substantially at the center in the axial direction of the weight main body 244b. (It may be a “position corresponding to the convex portion 55”). The annular groove 244d is set so that its depth (d2) is larger than the height (H) of the convex portion 55 (preferably 1 mm or more). Further, the annular groove 244d has a width (W2) so as to include a portion in contact with the convex portion 55 of the covering member 244a when viewed from the radial direction of the primary sheave 36 in a cross section orthogonal to the primary sheave shaft 20c. Is set to be wider than the width (W1) of the convex portion 55. That is, the annular groove 244 d is formed wider than the convex portion 55.

  The covering member 244a covers the outer peripheral surface 244c of the weight main body 244b and is formed so as to bite into the annular groove 244d formed in the outer peripheral surface 244c. In other words, the covering member 244a is formed with an annular convex portion 255 that protrudes toward the weight main body 244b and bites into the annular groove 244d.

  For this reason, as shown in FIG. 17, even when the covering member 244a rubs against the convex portion 55 and the convex portion 55 bites into the covering member 244a, the tip of the convex portion 55 contacts the outer peripheral surface 244c of the weight main body 244b. It is not reached. For this reason, it is hard to produce a crack and a crack in the covering member 244a.

  Further, even when the convex portion 55 bites into the covering member 244a and a crack or crack occurs in the covering member 244a, the first convex portion 255a and the first convex portion 255a separated from the convex portion 255 of the covering member 244a as shown in FIG. 2 convex portions 255b are respectively engaged with the annular grooves 244d of the weight main body 244b. Therefore, the covering member 244a is still fixed to the weight main body 244b. Therefore, the smoothness of the movement operation of the roller weight 244 in the radial direction is not impaired, and damage to the covering member 244a is suppressed.

  In the present embodiment, the width (W2) of the annular groove 244d is set to be wider than the width (W1) of the convex portion 55. For this reason, when the covering member 244a is further worn and the convex portion 55 reaches the weight main body 244b, the first convex portion 255a and the second convex portion 255b still remain. Therefore, even when the convex portion 55 reaches the weight main body 244b, the covering member 244a is still fixed to the weight main body 244b. Accordingly, the smoothness of the movement operation of the roller weight 244 in the radial direction is not impaired, and damage to the covering member 244a is suppressed.

  As described above, by forming the annular groove 244d at a position corresponding to the convex portion 55 on the surface of the weight main body 244b and increasing the thickness of the covering member 244a in that portion, the covering member 244a is cracked or cracked. It becomes difficult to occur, and it becomes difficult for the convex portion 55 to reach the weight main body 244b. By the way, for example, as a method of increasing the thickness of the covering member 244a at a position corresponding to the convex portion 55 of the weight main body 244b, it is conceivable to increase the thickness of the covering member 244a as a whole in addition to forming the annular groove 244d. . However, in this case, the volume of the weight main body 244b is reduced as compared with the case of the third embodiment, and the weight of the roller weight 244 is reduced. On the other hand, according to the method of forming the annular groove 244d as in this embodiment, the volume of the weight main body 244b is minimized and the covering member 244a at the position corresponding to the convex portion 55 of the weight main body 244b is used. The thickness can be increased.

  In the third embodiment, as in the first embodiment, the outer peripheral surface 244c of the weight main body 244b may be formed in a rough surface. Further, as in the second embodiment, one or a plurality of annular grooves (or annular convex portions) may be further formed on both sides of the roller weight 244 in the axial direction.

  As mentioned above, although Embodiment 1-3 which implemented this invention has been demonstrated, the stopper 53 is not limited to the thing of the aspect by which the one convex part 55 was formed in the said stopper surface 54. FIG. For example, as shown in FIG. 18, the stopper 53 may be formed with one protrusion 55 a at each end of the stopper surface 54 a of the stopper 53 a in the axial direction of the roller weight 44. Moreover, you may form a stopper surface in the convex surface which protrudes toward roller weight. In the following modification, an example in which the stopper surface is formed as a convex surface will be described. In the following description of the modified examples, components having substantially the same functions are described with reference numerals common to the first to third embodiments, and description thereof is omitted. 1 and 2 are referred to in common with the first embodiment.

(Modification)
FIG. 19 is a schematic view showing the shape of the stopper 53b in this modification. In this modification, the stopper surface 54 b of the stopper 53 is formed as a convex surface that protrudes toward the roller weight 344. Even in this configuration, as in the case of the first embodiment, the wear of the portion of the roller weight 344 that contacts the top of the stopper surface 54b of the covering member 344a is promoted. As a result, the belt winding diameter of the primary sheave 36 is increased, and the decrease in the belt winding diameter due to wear of the portion of the covering member 344a that contacts the cam plate 43 and the cam surface 42 is corrected. As a result, the relationship of the speed ratio to the rotational speed of the primary sheave shaft 20c and the change with time of the minimum speed ratio are effectively suppressed.

  In this modification, the roller weight 344 includes a weight main body 344b and a covering member 344a. The outer peripheral surface 344c of the weight main body 344b is formed in a concave shape in the axial cross section of the weight main body 344b. On the other hand, the inner peripheral surface of the covering member 344a is formed as a convex surface, and is fitted to the outer peripheral portion of the weight main body 344b. The lowest point of the outer peripheral surface 344c of the weight main body 344b in the cross section orthogonal to the primary sheave shaft 20c faces the apex of the stopper surface 54b in the radial direction of the primary sheave 36.

  Therefore, as in the case of the third embodiment, the thickness of the portion of the covering member 344a that contacts the vertex of the stopper surface 54b is relatively thick, and the vertex of the stopper surface 54b reaches the outer peripheral surface of the weight body 344b. It has a difficult structure. Therefore, the occurrence of cracks and cracks in the covering member 344a is effectively suppressed. From the viewpoint of increasing the thickness of the portion of the covering member 344a that contacts the apex of the stopper surface 54b, it is preferable that the radius of curvature of the outer peripheral surface of the weight body 344b is larger than the radius of curvature of the stopper surface 54b.

  Even when the covering member 344a is divided into two, each of the two divided covering members 344a is engaged with the weight main body 344b, so that the covering member 344a is still fixed to the weight main body 344b. It is in the state. For this reason, the smoothness of the movement operation of the roller weight 344 in the radial direction is not impaired, and damage to the covering member 344a is suppressed.

  The present invention is useful for a straddle-type vehicle including a belt-type continuously variable transmission. In particular, the present invention is useful for a straddle-type vehicle including a belt type continuously variable transmission having a relatively large displacement.

1 is a side view of a motorcycle according to a first embodiment. It is sectional drawing showing the structure of an engine unit. It is the top view seen from the vehicle width direction center side of the primary movable sheave body. It is the IV-IV arrow line view in FIG. It is an expanded sectional view of the stopper in Embodiment 1. It is a VI-VI arrow line view in FIG. FIG. 3 is a schematic plan view showing a positional relationship between a roller weight and a convex portion of a stopper in the first embodiment. (A) is a perspective view of a roller weight. (B) is a VIII (b) -VIII (b) arrow view in (a). In Embodiment 1, it is sectional drawing of the primary sheave which shows the state in which the new roller weight contact | connected the convex part of the stopper. FIG. 10 is an XX arrow view in FIG. 9. In Embodiment 1, it is sectional drawing of the primary sheave which shows the state which the roller weight digged into the convex part of the stopper. It is a XII-XII arrow line view in FIG. 6 is a cross-sectional view of a roller weight in Embodiment 2. FIG. It is a schematic plan view which shows the positional relationship of the roller weight in Embodiment 2, and the convex part of a stopper. 6 is a cross-sectional view of a roller weight in Embodiment 3. FIG. It is a schematic plan view which shows the positional relationship of the roller weight in Embodiment 3, and the convex part of a stopper. In Embodiment 3, it is sectional drawing of the primary sheave which shows the state which the roller weight digged into the convex part of the stopper. It is the schematic showing the variation of the shape of a stopper. It is the schematic showing the shape of the stopper in a modification.

Explanation of symbols

1 Motorcycle
12 Engine unit
13 engine
14 CVT
20 Crankshaft
20c Primary sheave shaft
36 Primary sheave
36a Primary fixed sheave body
36b Primary movable sheave body
36c Belt groove
37 Secondary sheave
37a Secondary fixed sheave body
37b Secondary movable sheave body
37c Belt groove
38 Secondary sheave shaft
41 belt
42 Cam surface
43 Cam plate
44 Rollerweight
44a Cover member
44b Weight body
51 Guide section
53 Stopper
54 Stopper surface
55 Convex

Claims (16)

A belt-type continuously variable transmission comprising a primary sheave rotating around a rotation shaft, a secondary sheave, and a belt wound around the primary sheave and the secondary sheave,
The primary sheave is
A first sheave body;
A second sheave that is opposed to the first sheave body and is disposed so as to be relatively displaceable in the axial direction of the first sheave body, and forms a belt groove around which the belt is wound together with the first sheave body. Body,
Centrifugal force generated at the time of turning, having a pressing body main body and a covering member that covers at least a part of the surface of the pressing body main body, swirling around the rotation axis with the rotation of the second sheave body By pressing the second sheave body toward the first sheave body, the pressing body moves outward in the radial direction of the second sheave body and narrows the width of the belt groove;
When the second sheave body reaches the minimum speed ratio position at which the width of the belt groove is most narrowed, the second sheave body comes into contact with the covering member of the pressing body so that the pressing body moves outward in the radial direction of the second sheave body. A stopper for regulating displacement,
The stopper has a shape that promotes wear of a part of the covering member,
A concavo-convex portion including a convex portion or a concave portion that engages with the covering member is formed on at least a part of a portion of the surface of the pressing body that is covered with the covering member,
A belt type in which at least two uneven portions are formed, and the portion of the covering member whose wear is promoted by the stopper is located between the at least two uneven portions in the circumferential direction of the primary sheave. Continuously variable transmission. A belt-type continuously variable transmission comprising a primary sheave rotating around a rotation shaft, a secondary sheave, and a belt wound around the primary sheave and the secondary sheave,
The primary sheave is
A first sheave body;
A second sheave that is opposed to the first sheave body and is disposed so as to be relatively displaceable in the axial direction of the first sheave body, and forms a belt groove around which the belt is wound together with the first sheave body. Body,
A pressing member main body and a covering member that covers at least a part of the surface of the pressing body main body, swirling around the rotation axis as the second sheave body rotates, and by centrifugal force generated during the swiveling A pressing body that moves outward in the radial direction of the second sheave body while narrowing the width of the belt groove while pressing the second sheave body toward the first sheave body;
When the second sheave body reaches the minimum speed ratio position at which the width of the belt groove is most narrowed, the second sheave body comes into contact with the covering member of the pressing body so that the pressing body moves outward in the radial direction of the second sheave body. A stopper for regulating displacement,
The stopper has a contact surface that contacts the covering member of the pressing body, and a convex portion that is formed on the corresponding contact surface and protrudes toward the pressing body,
A concavo-convex portion including a convex portion or a concave portion that engages with the covering member is formed on at least a part of a portion of the surface of the pressing body that is covered with the covering member,
A belt type in which at least two concavo-convex portions are formed, and a portion of the covering member that contacts the convex portion of the stopper is located between the at least two concavo-convex portions in the circumferential direction of the primary sheave. Continuously variable transmission. A belt-type continuously variable transmission comprising a primary sheave rotating around a rotation shaft, a secondary sheave, and a belt wound around the primary sheave and the secondary sheave,
The primary sheave is
A first sheave body;
A second sheave that is opposed to the first sheave body and is disposed so as to be relatively displaceable in the axial direction of the first sheave body, and forms a belt groove around which the belt is wound together with the first sheave body. Body,
Centrifugal force generated at the time of turning, having a pressing body main body and a covering member that covers at least a part of the surface of the pressing body main body, swirling around the rotation axis with the rotation of the second sheave body By pressing the second sheave body toward the first sheave body, the pressing body moves outward in the radial direction of the second sheave body and narrows the width of the belt groove;
When the second sheave body reaches the minimum speed ratio position at which the width of the belt groove is most narrowed, the second sheave body comes into contact with the covering member of the pressing body so that the pressing body moves outward in the radial direction of the second sheave body. A stopper for regulating displacement,
The stopper has a shape that promotes wear of a part of the covering member,
A concavo-convex portion including a convex portion or a concave portion that engages with the covering member is formed on at least a part of a portion of the surface of the pressing body that is covered with the covering member,
In the radial direction of the primary sheave, a belt in which a concave portion that engages with the covering member is formed on the surface of the pressing body main body at a position facing a wear portion where wear is promoted by the stopper of the covering member. Type continuously variable transmission. A belt-type continuously variable transmission comprising a primary sheave rotating around a rotation shaft, a secondary sheave, and a belt wound around the primary sheave and the secondary sheave,
The primary sheave is
A first sheave body;
A second sheave that is opposed to the first sheave body and is disposed so as to be relatively displaceable in the axial direction of the first sheave body, and forms a belt groove around which the belt is wound together with the first sheave body. Body,
A pressing member main body and a covering member that covers at least a part of the surface of the pressing body main body, swirling around the rotation axis as the second sheave body rotates, and by centrifugal force generated during the swiveling A pressing body that moves outward in the radial direction of the second sheave body while narrowing the width of the belt groove while pressing the second sheave body toward the first sheave body;
When the second sheave body reaches the minimum speed ratio position at which the width of the belt groove is most narrowed, the second sheave body comes into contact with the covering member of the pressing body so that the pressing body moves outward in the radial direction of the second sheave body. A stopper for regulating displacement,
The stopper has a contact surface that contacts the covering member of the pressing body, and a convex portion that is formed on the corresponding contact surface and protrudes toward the pressing body,
A concavo-convex portion including a convex portion or a concave portion that engages with the covering member is formed on at least a part of a portion of the surface of the pressing body that is covered with the covering member,
In the radial direction of the primary sheave, a belt type in which a concave portion that engages with the covering member is formed at a position of the surface of the pressing body facing the portion of the covering member that contacts the convex portion of the stopper. Continuously variable transmission. In the belt type continuously variable transmission according to claim 3 ,
The belt-type continuously variable transmission, wherein the recess includes the wear portion and is wider than the wear portion when viewed from the radial direction of the primary sheave. In the belt type continuously variable transmission according to claim 4 ,
It said recess, when viewed from a radial direction of the primary sheave comprises a protrusion abutting portion of the stopper, a belt type continuously variable transmission that is wider than the partial. A belt-type continuously variable transmission comprising a primary sheave rotating around a rotation shaft, a secondary sheave, and a belt wound around the primary sheave and the secondary sheave,
The primary sheave is
A first sheave body;
A second sheave that is opposed to the first sheave body and is disposed so as to be relatively displaceable in the axial direction of the first sheave body, and forms a belt groove around which the belt is wound together with the first sheave body. Body,
Centrifugal force generated at the time of turning, having a pressing body main body and a covering member that covers at least a part of the surface of the pressing body main body, swirling around the rotation axis with the rotation of the second sheave body By pressing the second sheave body toward the first sheave body, the pressing body moves outward in the radial direction of the second sheave body and narrows the width of the belt groove;
When the second sheave body reaches the minimum speed ratio position at which the width of the belt groove is most narrowed, the second sheave body comes into contact with the covering member of the pressing body so that the pressing body moves outward in the radial direction of the second sheave body. A stopper for regulating displacement,
The stopper has a shape that promotes wear of a part of the covering member,
A concavo-convex portion including a convex portion or a concave portion that engages with the covering member is formed on at least a part of a portion of the surface of the pressing body that is covered with the covering member,
The covering portion of the surface of the pressing body, which is covered with the covering member, is formed in a concave shape in a cross section orthogonal to the rotation axis,
The covering portion is formed such that the lowest point in a cross section perpendicular to the rotation axis faces a portion where wear is promoted by the stopper of the covering member in the radial direction of the primary sheave. Type continuously variable transmission. A belt-type continuously variable transmission comprising a primary sheave rotating around a rotation shaft, a secondary sheave, and a belt wound around the primary sheave and the secondary sheave,
The primary sheave is
A first sheave body;
A second sheave that is opposed to the first sheave body and is disposed so as to be relatively displaceable in the axial direction of the first sheave body, and forms a belt groove around which the belt is wound together with the first sheave body. Body,
A pressing member main body and a covering member that covers at least a part of the surface of the pressing body main body, swirling around the rotation axis as the second sheave body rotates, and by centrifugal force generated during the swiveling A pressing body that moves outward in the radial direction of the second sheave body while narrowing the width of the belt groove while pressing the second sheave body toward the first sheave body;
When the second sheave body reaches the minimum speed ratio position at which the width of the belt groove is most narrowed, the second sheave body comes into contact with the covering member of the pressing body so that the pressing body moves outward in the radial direction of the second sheave body. A stopper for regulating displacement,
The stopper has a contact surface that contacts the covering member of the pressing body, and a convex portion that is formed on the corresponding contact surface and protrudes toward the pressing body,
A concavo-convex portion including a convex portion or a concave portion that engages with the covering member is formed on at least a part of a portion of the surface of the pressing body that is covered with the covering member,
The covering portion of the surface of the pressing body, which is covered with the covering member, is formed in a concave shape in a cross section orthogonal to the rotation axis,
The covering portion is formed such that a lowest point in a cross section orthogonal to the rotation axis faces a portion of the covering member that contacts the convex portion of the stopper in the radial direction of the primary sheave. Type continuously variable transmission. A belt-type continuously variable transmission comprising a primary sheave rotating around a rotation shaft, a secondary sheave, and a belt wound around the primary sheave and the secondary sheave,
The primary sheave is
A first sheave body;
A second sheave that is opposed to the first sheave body and is disposed so as to be relatively displaceable in the axial direction of the first sheave body, and forms a belt groove around which the belt is wound together with the first sheave body. Body,
Centrifugal force generated at the time of turning, having a pressing body main body and a covering member that covers at least a part of the surface of the pressing body main body, swirling around the rotation axis with the rotation of the second sheave body By pressing the second sheave body toward the first sheave body, the pressing body moves outward in the radial direction of the second sheave body and narrows the width of the belt groove;
When the second sheave body reaches the minimum speed ratio position at which the width of the belt groove is most narrowed, the second sheave body comes into contact with the covering member of the pressing body so that the pressing body moves outward in the radial direction of the second sheave body. A stopper for regulating displacement,
The stopper has a shape that promotes wear of a part of the covering member,
A concavo-convex portion including a convex portion or a concave portion that engages with the covering member is formed on at least a part of a portion of the surface of the pressing body that is covered with the covering member,
The belt-type continuously variable transmission, wherein the covering member is formed such that the thickness of the portion whose wear is promoted by the stopper is larger than the thickness of the other portion. A belt-type continuously variable transmission comprising a primary sheave rotating around a rotation shaft, a secondary sheave, and a belt wound around the primary sheave and the secondary sheave,
The primary sheave is
A first sheave body;
A second sheave that is opposed to the first sheave body and is disposed so as to be relatively displaceable in the axial direction of the first sheave body, and forms a belt groove around which the belt is wound together with the first sheave body. Body,
A pressing member main body and a covering member that covers at least a part of the surface of the pressing body main body, swirling around the rotation axis as the second sheave body rotates, and by centrifugal force generated during the swiveling A pressing body that moves outward in the radial direction of the second sheave body while narrowing the width of the belt groove while pressing the second sheave body toward the first sheave body;
When the second sheave body reaches the minimum speed ratio position at which the width of the belt groove is most narrowed, the second sheave body comes into contact with the covering member of the pressing body so that the pressing body moves outward in the radial direction of the second sheave body. A stopper for regulating displacement,
The stopper has a contact surface that contacts the covering member of the pressing body, and a convex portion that is formed on the corresponding contact surface and protrudes toward the pressing body,
A concavo-convex portion including a convex portion or a concave portion that engages with the covering member is formed on at least a part of a portion of the surface of the pressing body that is covered with the covering member,
The belt-type continuously variable transmission, wherein the covering member is formed such that the thickness of the portion in contact with the convex portion of the stopper is greater than the thickness of the other portions. In the belt type continuously variable transmission according to any one of claims 1, 3, 7, and 9 ,
The said stopper is a belt-type continuously variable transmission which has the contact surface contact | abutted to the said coating | coated member, and the convex part which is formed in the applicable contact surface and protrudes toward the said press body. The belt-type continuously variable transmission according to any one of claims 2, 4, 8, 10, and 11 ,
The belt-type continuously variable transmission, wherein the covering member has a portion in contact with the convex portion whose thickness is greater than the height of the convex portion in the radial direction of the primary sheave. The belt-type continuously variable transmission according to any one of claims 2, 4, 8, 10, and 11 ,
The pressing body is a columnar or cylindrical shape extending in the circumferential direction of the primary sheave,
The belt-type continuously variable transmission in which the thickness of the portion of the covering member that comes into contact with the convex portion is 0.01 times or more the outer peripheral radius of the pressing body. In the belt type continuously variable transmission according to any one of claims 1 to 13 ,
The belt-type continuously variable transmission, wherein the pressing body is columnar or cylindrical, and the covering member is formed to cover the outer peripheral surface of the pressing body. In the belt-type continuously variable transmission as described in any one of Claims 1-14 ,
The covering member is a belt type continuously variable transmission whose hardness is lower than the hardness of the pressing body. A straddle-type vehicle comprising the belt-type continuously variable transmission according to any one of claims 1 to 15 .

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