WO2018051741A1 - Belt-type stepless transmission - Google Patents

Belt-type stepless transmission Download PDF

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Publication number
WO2018051741A1
WO2018051741A1 PCT/JP2017/029909 JP2017029909W WO2018051741A1 WO 2018051741 A1 WO2018051741 A1 WO 2018051741A1 JP 2017029909 W JP2017029909 W JP 2017029909W WO 2018051741 A1 WO2018051741 A1 WO 2018051741A1
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WO
WIPO (PCT)
Prior art keywords
plate
boss
belt
movable sheave
centrifugal
Prior art date
Application number
PCT/JP2017/029909
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French (fr)
Japanese (ja)
Inventor
隆士 渥美
晃尚 岡本
亮輔 淺井
圭宏 吉田
Original Assignee
武蔵精密工業株式会社
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Publication date
Application filed by 武蔵精密工業株式会社 filed Critical 武蔵精密工業株式会社
Publication of WO2018051741A1 publication Critical patent/WO2018051741A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
    • F16H9/16—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts
    • F16H9/18—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts only one flange of each pulley being adjustable

Definitions

  • the present invention relates to a continuously variable transmission, in particular, a belt-type non-transistor including a fixed sheave fixed to a rotating shaft, a movable sheave movable in the axial direction with respect to the rotating shaft, and a belt wound around the fixed sheave and the movable sheave.
  • the present invention relates to a step transmission.
  • Patent Document 1 discloses that the movable sheave is shifted in the axial direction by a first shift mechanism that shifts the movable sheave in the axial direction by an electric actuator and a centrifugal mechanism that uses a centrifugal weight.
  • a second shift mechanism is disclosed.
  • the centrifugal mechanism of the second shift mechanism includes a ramp plate that is fixed to the movable sheave, a cam member that is disposed on the opposite side of the bearing across the ramp plate, A centrifugal weight interposed between the ramp plate and the cam member, and the centrifugal force generated in the centrifugal weight with the rotation of the rotating shaft is converted into an axial driving force by the cam member to form the ramp plate. It is supposed to act.
  • Patent Document 1 has a structure in which the movable sheave is elongated in the axial direction because the action portions of the first and second shift mechanisms with respect to the movable sheave are arranged in series in the axial direction of the rotating shaft. Since the lamp plate is fastened to the boss portion of the movable sheave with a nut, the movable sheave further expands in the axial direction by an amount corresponding to the mounting space of the nut.
  • the cam member is provided with a recess that receives the nut, and the nut and the centrifugal weight overlap each other in the radial direction (that is, they are located in the same region in the axial direction).
  • the centrifugal weight is inevitably disposed on the radially outer side of the nut, so that the centrifugal mechanism (for example, the cam member that supports the centrifugal weight) expands in the radial direction.
  • the centrifugal mechanism for example, the cam member that supports the centrifugal weight
  • the present invention was made in view of such circumstances, and can directly connect the boss portion of the movable sheave and the lamp plate without a nut, and by suppressing the axial expansion of the movable sheave and the radial expansion of the centrifugal mechanism, It is an object of the present invention to provide a belt type continuously variable transmission that can be downsized in both the axial direction and the radial direction.
  • the present invention provides a fixed sheave fixed to a rotating shaft, a movable sheave having a boss portion through which the rotating shaft is inserted and movable in the axial direction with respect to the rotating shaft, and the fixed sheave. And a belt that is wound around the movable sheave, and a first shift mechanism that has an actuator that applies a first axial driving force to the boss portion via a bearing, and that shifts the movable sheave in the axial direction, A ramp mechanism that includes a centrifugal mechanism that applies a second axial driving force to the boss portion and that shifts the movable sheave in the axial direction, and the centrifugal mechanism is fixed to the movable sheave.
  • a cam member disposed on the opposite side of the bearing across the lamp plate and rotating integrally with the rotating shaft, and a centrifugal weight interposed between the lamp plate and the cam member
  • a belt-type continuously variable transmission that converts the centrifugal force of the centrifugal weight into the second axial driving force by the cam member and acts on the ramp plate.
  • a plate boss that surrounds the plate portion, and a plate body portion that projects radially outward from the plate boss and holds the centrifugal weight between the cam member and the boss portion and the plate boss.
  • the present invention has a second feature that at least a part of the plate boss and at least a part of the bearing overlap each other in the radial direction.
  • an inner peripheral portion of the bearing is attached to the plate boss so that the bearing is supported by the boss portion via the ramp plate.
  • a stepped portion facing the centrifugal mechanism side in the axial direction is formed on the outer peripheral surface of the boss portion.
  • a locking portion that holds the inner peripheral portion of the bearing in the axial direction between the stepped portion and the stepped portion.
  • the present invention is also a belt-type continuously variable transmission having any one of the first to fourth features mounted on a vehicle with the rotation shaft arranged in the vehicle width direction, wherein the actuator includes at least one An actuator body disposed on the outer side in the vehicle width direction with respect to the belt, and an output member extending from the actuator body to the inner side in the vehicle width direction with respect to the belt.
  • a member can output the first axial driving force to the movable sheave via a shift arm, and the shift arm includes a base fixed to an outer peripheral portion of the bearing, and a diameter of the movable sheave from the base.
  • axial direction refers to the direction along the axis of the rotation axis (input shaft 11 in the embodiment)
  • radial direction refers to the radial direction of a circle centered on the axis.
  • the ramp plate of the centrifugal mechanism integrally has a plate boss surrounding the boss portion of the movable sheave and a plate main body portion projecting radially outward from the plate boss to hold the centrifugal weight between the cam member. Since the opposing circumferential surfaces of the plate boss and the movable sheave boss are directly coupled to each other, there is no need to use a nut specially for coupling the movable sheave and the lamp plate.
  • the axial direction can be reduced.
  • the portion where the centrifugal weight is disposed can be set radially inward without being affected by the nut, so that the centrifugal mechanism including the cam member can be downsized in the radial direction. This is advantageous in reducing the size of the continuously variable transmission as a whole in both the axial direction and the radial direction.
  • the overlap of the movable sheave can be reduced in the axial direction.
  • the bearing since the inner peripheral portion of the bearing is mounted on the plate boss so that the bearing is supported on the boss portion of the movable sheave via the ramp plate, the bearing is pre-assembled on the plate boss in advance.
  • the bearing and the lamp plate can be assembled as a sub-assembly into the movable sheave at once, and the assembling work efficiency can be improved.
  • a stepped portion facing the centrifugal mechanism side in the axial direction is formed on the outer peripheral surface of the boss portion of the movable sheave, and the lamp plate has an inner peripheral portion of the bearing between the stepped portion and the ramp plate. Since it has a locking part that is clamped in the axial direction, the inner peripheral part of the bearing is connected between the stepped part and the locking part at the same time as the opposing peripheral surfaces of the movable sheave boss part and the plate boss are directly coupled to each other.
  • the bearing can be positioned and fixed by mechanically sandwiching. This eliminates the need for dedicated parts for positioning and fixing the bearing, which simplifies the structure and size of the movable sheave and simplifies and speeds up the positioning and fixing of the bearing. , Assembly work efficiency can be increased.
  • the actuator of the first shift mechanism includes at least a part of the actuator body disposed on the outer side in the vehicle width direction with respect to the belt, and the inner side in the vehicle width direction with respect to the belt.
  • a shift arm that transmits the output of the output member to the movable sheave, and extends from the base to the radially outer side of the movable sheave.
  • the shift arm is integrally provided with an intermediate portion and a tip portion extending inward in the vehicle width direction from the intermediate portion and connected to the output member, and at least when the lamp plate and the cam member are closest to each other in the axial direction.
  • the actuator protrudes outward in the vehicle width direction and the centrifugal mechanism extends inward in the vehicle width direction. Suppress both overhangs Bets can be, it can contribute to the vehicle width direction size of the continuously variable transmission. In this case, even if the tip of the shift arm and a part of the cam member overlap in the radial direction, the shift arm can be reduced in the radial direction based on the first feature as described above.
  • the intermediate part of the arm can be made as short as possible to increase the arm rigidity.
  • FIG. 1 is a plan sectional view of a power unit including a belt-type continuously variable transmission according to a first embodiment of the present invention.
  • FIG. 2 is an enlarged cross-sectional view (cross-sectional view taken along the line 2-2 in FIG. 3) of the main part of the belt-type continuously variable transmission, in particular, a part indicated by an arrow 2 in FIG. FIG.
  • FIG. 3 is a cross-sectional view (cross-sectional view taken along line 3-3 in FIG. 2) of the second shift mechanism (centrifugal mechanism) of the belt type continuously variable transmission.
  • FIG. 2 is an enlarged cross-sectional view (cross-sectional view taken along the line 2-2 in FIG. 3) of the main part of the belt-type continuously variable transmission, in particular, a part indicated by an arrow 2 in FIG. FIG.
  • FIG. 3 is a cross-sectional view (cross-sectional view taken along line 3-3 in FIG. 2) of the second shift mechanism (centrifugal mechanism) of the belt type continuously variable transmission
  • FIG. 4 is an enlarged cross-sectional view of the main part of the belt-type continuously variable transmission, showing a state in which the belt winding radius is maximum (corresponding to FIG. 2).
  • FIG. 5 is an enlarged cross-sectional view (corresponding to FIG. 2) of the main part of the belt type continuously variable transmission according to the second embodiment of the present invention.
  • a rear-wheel drive power unit U is pivotally supported on a body frame (not shown) of the motorcycle so that the rear-wheel drive can swing up and down.
  • the rear-wheel drive power unit U continuously outputs the engine E as a power source and the output of the engine E.
  • a belt type continuously variable transmission T that can be transmitted to the rear wheel W.
  • the belt type continuously variable transmission T includes an input shaft 11 to which power is transmitted from the crankshaft 10 of the engine E, an output shaft 12 that is disposed in parallel to the input shaft 11 and transmits power to the rear wheels W, and an input shaft. 11, a drive pulley 20 supported by the output shaft 12, a driven pulley 30 supported by the output shaft 12, an endless belt 14 wound around the pulleys 20, 30, the pulleys 20, 30 and the belt 14, and input / output A transmission case 15 that accommodates the shafts 11 and 12 and first and second shift mechanisms S1 and S2 that variably control the groove width of the drive pulley 20 are provided.
  • the input shaft 11 corresponds to the rotating shaft of the present invention.
  • the first and second shift mechanisms S1 and S2 may change the groove width of the driven pulley 30.
  • the mission case 15 is composed of, for example, first and second case halves 15a and 15b that are detachably coupled to each other.
  • a part of the first case half 15a on the inner side in the vehicle width direction constitutes a part of the crankcase of the engine E, and supports one end of the crankshaft 10 via the bearing 13 so as to be rotatable.
  • the cylinder block (not shown) of the engine E is detachably coupled.
  • the input and output shafts 11 and 12 are arranged to extend in the vehicle width direction.
  • the input shaft 11 is coaxially and integrally provided at the shaft end of the crankshaft 10 and extends into the mission case 15.
  • the input shaft 11 may be connected to the crankshaft 10 later as a separate body from the crankshaft 10, or may be linked and connected to the crankshaft 10 via a linkage mechanism.
  • the output shaft 12 is rotatably supported by the transmission case 15 on the vehicle rear side of the input shaft 11.
  • the drive pulley 20 includes a fixed sheave 21 that is fixed to the input shaft 11 and a movable sheave 22 that is supported by the input shaft 11 so as to be movable in the axial direction and not to be relatively rotatable.
  • the movable sheave 22 is shifted in the axial direction by the axial driving force output from the first and second shift mechanisms S1 and S2, so that the mutual interval between the movable sheave 22 and the fixed sheave 21, that is, the groove width of the driving pulley 20 is increased. Therefore, the belt winding radius can be changed.
  • the driven pulley 30 includes a fixed sheave 31 fixed to the output shaft 12, a movable sheave 32 supported on the output shaft 12 so as to be axially movable and relatively non-rotatable, and the movable sheave 32 on the fixed sheave 31 side (that is, the stationary sheave 31). And a return spring 33 that always urges the driven pulley 30 in the direction of narrowing the groove width.
  • the movable sheave 32 of the driven pulley 30 can move in the axial direction in accordance with the change in the tension of the belt 14 accompanying the change in the groove width of the drive pulley 20, thereby adjusting the groove width of the driven pulley 30.
  • the drive pulley 20 operates in a direction to narrow the groove width and increase the winding radius of the belt 14 based on the axial driving force of the first and second shift mechanisms S1 and S2 (thus increasing the belt tension).
  • the driven pulley 30 operates in a direction to increase the groove width and reduce the winding radius against the urging force of the return spring 33 in conjunction with the operation.
  • the driven pulley 30 is connected to the return spring 33 in conjunction with the operation. It operates in the direction of increasing the winding radius by narrowing the groove width by the urging force.
  • the movable sheave 22 of the drive pulley 20 includes a tapered movable sheave body 22a, and a cylindrical boss portion 22b that is integrally coupled to the central portion of the movable sheave body 22a (cast in this embodiment) and extends in the axial direction.
  • the boss portion 22b is fitted and supported on the input shaft 11 via the collar 18 fitted to the input shaft 11 so as to be slidable in the axial direction.
  • a pair of seal members 25 and 26 for enclosing lubricating oil between the fitting surfaces are interposed at intervals.
  • the collar 18 may be formed integrally with the fixed sheave 21.
  • the fixed sheave 21 of the drive pulley 20 integrally includes a fixed sheave body 21a having a reverse taper shape with respect to the movable sheave body 22a and an annular thick portion 21b positioned at the center of the fixed sheave body 21a.
  • the thick portion 21b is splined to the tip of the input shaft 11.
  • the belt 14 is wound around the fixed sheave main body 21a and the movable sheave main body 22a so as to straddle both.
  • a nut 16 is screwed to the tip of the input shaft 11.
  • the nut 16 integrally clamps and fastens the washer 17, the fixed sheave 21, the collar 18, and the cam member 42 of the centrifugal mechanism 40 described later with the outer peripheral step portion of the crankshaft 10. Accordingly, when the nut 16 is fastened, the fixed sheave 21, the collar 18 and the cam member 42 always rotate integrally with the crankshaft 10.
  • the first shift mechanism S1 includes an electronically controlled actuator 50 that applies a first axial driving force to the boss portion 22b of the movable sheave 22 via the bearing 24, and the first axial driving force described above.
  • the second shift mechanism S2 includes a centrifugal mechanism 40 that applies a second axial driving force to the boss portion 22b of the movable sheave 22, and the movable sheave 22 is fixed to the fixed sheave by the second axial driving force. 21 is shifted in the axial direction.
  • the centrifugal mechanism 40 of the second shift mechanism S2 includes a ramp plate 41 fixed to the movable sheave 22, the cam member 42 disposed on the opposite side of the bearing 24 across the lamp plate 41, the ramp plate 41, A plurality of centrifugal weights 43 are interposed between the cam members 42 and are arranged at intervals in the circumferential direction.
  • the centrifugal weight 43 is constituted by a cylindrical roller in this embodiment, but various forms (for example, balls) that can slide with respect to the lamp plate 41 and the cam member 42 can be selected in addition to the roller.
  • the cam member 42 is integrally provided with a generally disc-shaped cam member main body 42m and an outer peripheral cylindrical portion 42t that bends and extends from the outer peripheral end of the cam member main body 42m toward the lamp plate 41.
  • a plurality of cam groove portions 44 that respectively accommodate a plurality of centrifugal weights 43 are formed so as to extend in the radial direction at intervals in the circumferential direction. Is done.
  • each cam groove 44 (that is, the surface facing the lamp plate 41) is configured as a cam surface 44c that is inclined radially outward toward the lamp plate 41.
  • a radially inward rotation-stop protrusion 45 is provided so as to extend along the axis of the input shaft 11 between cam grooves 44 arranged in the circumferential direction. Is done.
  • the lamp plate 41 integrally includes a cylindrical plate boss 41b that concentrically surrounds the boss portion 22b of the movable sheave 22, and a plate body portion 41a that projects radially outward from one end of the plate boss 41b. .
  • the plate body 41a is formed so as to extend obliquely outward in the radial direction toward the cam member 42 in the axial direction (that is, the right side in FIG. 2).
  • the centrifugal weight 43 is slidably held between the plate main body 41a and the cam groove 44.
  • the inner peripheral portion of the bearing 24, that is, the inner race 24i is fitted and fixed to the outer peripheral surface of the plate boss 41b by press-fitting.
  • fixing means other than press fitting such as adhesion, caulking, welding, retaining rings (for example, circlip), etc., can be employed.
  • the mutually opposed peripheral surfaces of the plate boss 41 b and the boss portion 22 b of the movable sheave 22 are directly coupled 70.
  • the inner peripheral surface of the plate boss 41b is directly screwed and tightened to the outer peripheral surface of the boss portion 22b.
  • the lamp plate 41 has a locking portion 41as made of an annular flat surface or an arc surface orthogonal to the axis of the input shaft 11 at the radially inner end of the plate body 41a.
  • the locking portion 41as clamps the inner race 24i of the bearing 24 in the axial direction with the stepped portion 22bs.
  • a gap 46 in the axial direction is set between the end face and the step portion 22bs.
  • the plate main body portion 41a is interposed between a weight support portion 41aw that slidably holds the centrifugal weight 43 with the cam member 42 (cam groove portion 44), and a weight support portion 41aw arranged in the circumferential direction.
  • an engaging groove portion 41ag that is slidably engaged with the rotation stop protrusion 45 of the cam member 42 in the axial direction, and the engaging groove portion 41ag opens outward in the radial direction.
  • the resin guide member 47 with a groove for preventing the engagement groove portion 41ag from directly contacting the anti-rotation protrusion 45 and smoothing the relative sliding therebetween is integrated with the engagement groove portion 41ag. To be applied.
  • the mutual engagement between the rotation protrusion 45 and the engagement groove 41ag (and hence the guide member 47) restricts the relative rotation of the movable sheave 22 with respect to the cam member 42 (and hence the input shaft 11) and allows axial sliding. Is done.
  • the boss portion 22b of the movable sheave 22 and the collar 18 may be spline-fitted in place of the above-described detent structure with respect to the input shaft 11 of the movable sheave 22, and in particular, the collar 18 is omitted and the boss is omitted.
  • the boss portion 22b may be directly splined to the outer periphery of the input shaft 11.
  • the centrifugal mechanism 40 of the second shift mechanism S2 operates as follows, for example.
  • the centrifugal weight 43 is The cam surface 44c slides in an oblique direction outward in the radial direction toward the lamp plate 41.
  • the centrifugal weight 43 applies an axial driving force that moves the movable sheave 22 toward the fixed sheave 21 against the tension of the belt 14 via the ramp plate 41, whereby the driving pulley 20 is grooved. Narrow the width to increase the belt wrap radius.
  • the cam member 42 converts the centrifugal force of the centrifugal weight 43 into the axial driving force with respect to the movable sheave 22, and acts on the lamp plate 41. Then, the converted axial driving force changes in accordance with the increase / decrease change in the centrifugal force of the centrifugal weight 43 (that is, the rotational speed of the input shaft 11).
  • the actuator 50 of the first shift mechanism S1 includes an actuator main body 50m at least a part (most part in the present embodiment) disposed on the outer side in the vehicle width direction (left side in FIG. 1) than the belt 14, and an actuator
  • the main body 50m has an output rod 50a as an output member extending inward in the vehicle width direction (right side in FIG. 1) from the belt 14 and the output rod 50a is connected to the movable sheave 22 via the shift arm 60.
  • Axial driving force can be output.
  • the actuator body 50m has an actuator case 51 that is detachably attached to the second case half 15b of the mission case 15 and can be divided into a plurality of case elements.
  • the actuator case 51 includes, for example, an electric motor 52, a reduction gear mechanism 53 that reduces and transmits the output rotation of the electric motor 52, and a feed screw that converts the output rotation of the reduction gear mechanism 53 into axial movement of the output rod 50a.
  • a mechanism 54 is incorporated.
  • the output rod 50 a is interlocked with the feed screw mechanism 54 (in this embodiment, integrally coupled to the output screw shaft 54 a of the feed screw mechanism 54) and extends into the mission case 15 through the inner wall of the actuator case 51.
  • An engaging recess 55 as an engaged portion with respect to the shift arm 60 is provided at the distal end portion of the output rod 50a.
  • the shift arm 60 includes an outer peripheral portion of the bearing 24, that is, an annular base portion 60b fitted and fixed to the outer race 24o, an intermediate portion 60a extending from the base portion 60b to the radially outer side of the movable sheave 22, and an intermediate portion 60a. And a tip portion 60c that bends and extends inwardly in the vehicle width direction (right side in FIG. 2) from the front end. A proximal end of a connecting member 65 extending radially outward is fixed to the front portion 60c (in this embodiment, press-fitted).
  • the outer race 24o is fixed to the base 60b of the shift arm 60 so as to be detachable with a locking tool 27 such as a circlip.
  • the tip portion of the connecting member 65 is fitted and connected to the engaging recess 55 at the tip of the output rod 50a so as to be swingable.
  • the engaging recess 55 and the connecting member 65 of the output rod 50a are illustrated as fitting and connected so as to be able to swing in cooperation with each other.
  • the output rod 50a and the connecting member 65 are linked together. Therefore, the output rod 50a and the connecting member 65 may be coupled to each other by a coupling means different from the embodiment.
  • At least the lamp plate 41 and the cam member 42 are closest to each other in the axial direction (see FIG. 2), at least a part (most part in the present embodiment) of the tip 60c of the shift arm 60, and a centrifugal mechanism At least a part of the 40 cam members 42 (most part of the outer peripheral cylindrical portion 42t in this embodiment) overlaps each other in the radial direction, that is, is located in the same region in the axial direction.
  • the output rotation of the electric motor 52 is transmitted to the output rod 50a via the reduction gear mechanism 53 and the feed screw mechanism 54 in the actuator 50, and the shift arm 60, It is transmitted as an axial driving force to the boss portion 22 b of the movable sheave 22 via the bearing 24 and the lamp plate 41.
  • an on-vehicle electronic control device controls the operation of the actuator 50 (specifically, the electric motor 52) in accordance with the operating state of the motorcycle, the operating state of the engine E, etc.
  • the groove width (belt wrapping radius) of the driving pulley 20 is variably controlled, and the speed change between the output shafts 11 and 12 is performed.
  • the centrifugal mechanism 40 increases the axial driving force with respect to the movable sheave 22 in accordance with the increase in the rotational speed of the engine E (accordingly, the increase in the centrifugal force of the centrifugal weight 43).
  • the movable sheave 22 of the drive pulley 20 is shifted by the sum of the axial driving forces output by the first and second shift mechanisms S1 and S2, the power load on the actuator 50 can be reduced. Further, since the axial driving force with respect to the movable sheave 22 is increased, a quick shift up is possible, and the fuel consumption is improved. On the other hand, by controlling the axial driving force of the first shift mechanism S1 so as to suppress the axial driving force of the second shift mechanism S2, shift up is suppressed and acceleration performance is improved.
  • the ramp plate 41 of the centrifugal mechanism 40 protrudes radially outward from the plate boss 41b concentrically surrounding the boss portion 22b of the movable sheave 22 and the plate boss 41b.
  • the plate body portion 41a for holding the centrifugal weight 43 is integrally formed with the cam member 42, and the opposing circumferential surfaces of the boss portion 22b and the plate boss 41b are directly coupled 70 (implementation). The form is screwed).
  • the inner race 24i of the bearing 24 is mounted (press-fitted) on the plate boss 41b.
  • the bearing 24 and the lamp plate 41 can be assembled as a sub-assembly into the movable sheave 22 at once, and the assembling work efficiency is improved accordingly.
  • a step portion 22bs that faces the centrifugal mechanism 40 in the axial direction is formed on the outer peripheral surface of the boss portion 22b of the movable sheave 22, and the inner race 24i of the bearing 24 between the lamp plate 41 and the step portion 22bs is formed. Is provided at the radially inner end of the plate body 41a.
  • the opposing peripheral surfaces of the boss portion 22b of the movable sheave 22 and the plate boss 41b of the lamp plate 41 are directly coupled 70 (screw tightening in the embodiment), and at the same time, the step portion 22bs and the locking portion 41as Since the inner race 24i is mechanically sandwiched between the two, the bearing 24 can be positioned and fixed, so that no dedicated parts for positioning and fixing the bearing 24 are required, and the structure of the movable sheave 22 is simplified and reduced in size. In addition, the positioning and fixing work of the bearing 24 is simplified and speeded up.
  • the actuator 50 of the first shift mechanism S1 of the present embodiment is mostly an actuator main body 50m disposed on the outer side in the vehicle width direction (left side in FIG. 1) than the belt 14, and the actuator main body 50m to the belt 14 And an output rod 50a extending inward in the vehicle width direction (right side in FIG. 1), and a shift arm 60 that transmits the output of the output rod 50a to the movable sheave 22 is an outer race 24o of the bearing 24.
  • the lamp plate 41 and the cam member 42 are closest to each other in the axial direction, and a part of the tip 60c and the outer peripheral cylindrical portion 42 of the cam member 42 are provided. Some of the have overlap each other in the radial direction.
  • the extension of the actuator 50 to the outer side in the vehicle width direction and the extension of the centrifugal mechanism 40 to the inner side in the vehicle width direction are both effectively suppressed, and the continuously variable transmission T can be reduced in the vehicle width direction. Is achieved.
  • the cam member 42 can be downsized in the radial direction as described above.
  • the intermediate portion 60a of the arm 60 can be made as short as possible in the radial direction, and the arm rigidity can be increased accordingly.
  • the plate boss 41b of the lamp plate 41 extends to the side opposite to the cam member 42 with respect to the plate body 41a, and the inner race 24i of the bearing 24 is fitted on the outer peripheral surface of the plate boss 41b.
  • the plate boss 41b 'of the lamp plate 41' extends toward the cam member 42 with respect to the plate body 41a ', and the inner surface of the bearing 24 is formed on the outer peripheral surface of the boss 22b of the movable sheave 22.
  • the race 24i is different from the first embodiment in that the race 24i is fitted to the plate boss 41b 'in an axially adjacent state.
  • the opposing circumferential surfaces of the plate boss 41b ′ and the boss portion 22b of the movable sheave 22 are directly coupled 70, and as a coupling means, the boss portion 22b is the same as in the first embodiment.
  • the inner periphery of the plate boss 41b ' is directly screwed to the outer periphery. Then, due to the screw tightening, the inner race 24i of the bearing 24 existing on the outer periphery of the boss portion 22b causes the rising step portion 22bs of the boss portion 22b and the radially inner end portion (engagement) of the plate main body portion 41a of the lamp plate 41 ′. It is clamped and fixed between the stop portions 41as ′).
  • each component member is the same as the corresponding component member of the first embodiment and has a specific structure. Description is omitted. And according to 2nd Embodiment, the effect similar to the above-described effect of 1st Embodiment can be achieved.
  • the belt type continuously variable transmission T is illustrated as being mounted on a motorcycle.
  • the belt type continuously variable transmission of the present invention is applicable to various vehicles other than motorcycles, such as a motor tricycle. Is also applicable.
  • screwing means screw fixing
  • various coupling methods other than screwing can be applied. For example, directly press-fitting between the opposed peripheral surfaces, or directly press-fitting a spline fitting portion after spline-fitting between the opposed peripheral surfaces, or adhering or welding the opposed peripheral surfaces. Or may be combined directly.
  • the concave and convex engaging portions that bite into the opposed peripheral surfaces may be formed by caulking the end surfaces of the plate bosses 41 b and 41 b ′ of the lamp plates 41 and 41 ′ and the boss portion 22 b of the movable sheave 22.
  • the joint strength may be further strengthened by further crimping the end faces to those directly joined by screwing, press-fitting, spline press-fitting, adhesion or welding between the opposed peripheral surfaces.
  • the inner race 24i of the bearing 24 is provided on the outer peripheral surface of the plate boss 41b before the plate boss 41b is screwed and fastened to the boss 22b (that is, before the plate boss 41b is assembled to the boss 22b).
  • the inner race 24i of the bearing 24 is fitted to the outer peripheral surface of the plate boss 41b without being press-fitted, and the fitting position is fixed to the plate boss 41b. This may be performed by screwing and tightening to the boss portion 22b.
  • the actuator 50 of 1st shift mechanism S1 illustrated what used the electric motor 51 as an output source, as an actuator, various electromagnetic devices (for example, linear solenoid) other than an electric motor are used as an output source. You may use the actuator to do.
  • the actuator 50 of the first shift mechanism S1 is exemplified as an electric type, but a hydraulic actuator may be used as the actuator.

Abstract

This belt-type stepless transmission is configured so that, in order to axially shift the movable sheave of the belt-type stepless transmission, a first shift mechanism which has an actuator and a second shift mechanism which has a centrifugal mechanism are used in combination. The ramp plate (41) of the centrifugal mechanism (40) integrally has: a plate boss (41b) surrounding the boss section (22b) of the movable sheave (22); and a plate body section (41a) protruding radially outward from the plate boss (41b) and holding a centrifugal weight (43) between the plate body section (41a) and the cam member (42) of the centrifugal mechanism (40). A peripheral surface of the boss section (22b) of the movable sheave (22) and a peripheral surface of the plate boss (41b), the peripheral surfaces facing each other, are directly joined (70). As a result of this configuration, the boss section of the movable sheave and the ramp plate of the centrifugal mechanism can be directly connected without nut to prevent the axial enlargement of the movable sheave and the radial enlargement of the centrifugal mechanism, and the stepless transmission can be made axially and radially compact.

Description

ベルト式無段変速機Belt type continuously variable transmission
　本発明は、無段変速機、特に回転軸に固定される固定シーブと、回転軸に対し軸方向移動可能な可動シーブと、固定シーブ及び可動シーブに巻き掛けられるベルトとを備えたベルト式無段変速機に関する。 The present invention relates to a continuously variable transmission, in particular, a belt-type non-transistor including a fixed sheave fixed to a rotating shaft, a movable sheave movable in the axial direction with respect to the rotating shaft, and a belt wound around the fixed sheave and the movable sheave. The present invention relates to a step transmission.
　上記ベルト式無段変速機に関し、例えば特許文献１には、電動のアクチュエータによって可動シーブを軸方向にシフトさせる第１シフト機構と、遠心重錘を利用した遠心機構によって可動シーブを軸方向にシフトさせる第２シフト機構とを備えたものが開示されている。 Regarding the belt type continuously variable transmission, for example, Patent Document 1 discloses that the movable sheave is shifted in the axial direction by a first shift mechanism that shifts the movable sheave in the axial direction by an electric actuator and a centrifugal mechanism that uses a centrifugal weight. A second shift mechanism is disclosed.
　そして、特許文献１の無段変速機においては、第２シフト機構の遠心機構が、可動シーブに固定されるランププレートと、ランププレートを挟んで軸受とは反対側に配置されるカム部材と、ランププレート及びカム部材間に介装される遠心重錘とを有しており、回転軸の回転に伴い遠心重錘に生じた遠心力をカム部材で軸方向駆動力に変換してランププレートに作用させるようになっている。 In the continuously variable transmission of Patent Document 1, the centrifugal mechanism of the second shift mechanism includes a ramp plate that is fixed to the movable sheave, a cam member that is disposed on the opposite side of the bearing across the ramp plate, A centrifugal weight interposed between the ramp plate and the cam member, and the centrifugal force generated in the centrifugal weight with the rotation of the rotating shaft is converted into an axial driving force by the cam member to form the ramp plate. It is supposed to act.
日本特許第５８６４３８８号公報Japanese Patent No. 5864388
　特許文献１の無段変速機は、可動シーブに対する第１，第２シフト機構の各作用部が回転軸の軸方向に直列に配置されるため、可動シーブが軸方向に長くなる構造である上、ランププレートを可動シーブのボス部にナットで締結しているため、ナットの取付スペース分だけ可動シーブが軸方向に更に拡大してしまう構造である。 The continuously variable transmission of Patent Document 1 has a structure in which the movable sheave is elongated in the axial direction because the action portions of the first and second shift mechanisms with respect to the movable sheave are arranged in series in the axial direction of the rotating shaft. Since the lamp plate is fastened to the boss portion of the movable sheave with a nut, the movable sheave further expands in the axial direction by an amount corresponding to the mounting space of the nut.
　そこで特許文献１の無段変速機では、カム部材に、ナットを受容する凹部を設け、ナットと遠心重錘とが径方向で互いにオーバラップする（即ち軸方向で互いに同一の領域に位置する）レイアウトを採用することにより、遠心機構の軸方向拡大を抑えている。 Therefore, in the continuously variable transmission of Patent Document 1, the cam member is provided with a recess that receives the nut, and the nut and the centrifugal weight overlap each other in the radial direction (that is, they are located in the same region in the axial direction). By adopting the layout, the axial expansion of the centrifugal mechanism is suppressed.
　ところが上記レイアウトを採用すると、遠心重錘が必然的にナットの径方向外方側に配置されるため、遠心機構（例えば遠心重錘を支持するカム部材）が径方向に拡大してしまい、結局のところ、遠心機構、延いては無段変速機の軸方向拡大と径方向拡大を同時に抑えることが困難であった。 However, when the above-described layout is adopted, the centrifugal weight is inevitably disposed on the radially outer side of the nut, so that the centrifugal mechanism (for example, the cam member that supports the centrifugal weight) expands in the radial direction. However, it has been difficult to simultaneously suppress the axial expansion and radial expansion of the centrifugal mechanism, and thus the continuously variable transmission.
　本発明は、かかる事情に鑑みてなされたもので、可動シーブのボス部とランププレートとをナット無しで直結可能として、可動シーブの軸方向拡大、並びに遠心機構の径方向拡大を抑えることで、無段変速機を軸方向にも径方向にも小型化可能としたベルト式無段変速機を提供することを目的とする。 The present invention was made in view of such circumstances, and can directly connect the boss portion of the movable sheave and the lamp plate without a nut, and by suppressing the axial expansion of the movable sheave and the radial expansion of the centrifugal mechanism, It is an object of the present invention to provide a belt type continuously variable transmission that can be downsized in both the axial direction and the radial direction.
　上記目的を達成するために、本発明は、回転軸に固定される固定シーブと、前記回転軸を挿通させるボス部を有すると共に該回転軸に対し軸方向移動可能な可動シーブと、前記固定シーブ及び前記可動シーブに巻き掛けられるベルトと、前記ボス部に軸受を介して第１の軸方向駆動力を付与するアクチュエータを有して前記可動シーブを軸方向にシフトさせる第１シフト機構と、前記ボス部に第２の軸方向駆動力を付与する遠心機構を有して前記可動シーブを軸方向にシフトさせる第２シフト機構とを備え、前記遠心機構は、前記可動シーブに固定されるランププレートと、前記ランププレートを挟んで前記軸受とは反対側に配置されて前記回転軸と一体に回転するカム部材と、前記ランププレート及び前記カム部材間に介装される遠心重錘とを有し、前記遠心重錘の遠心力を前記カム部材で前記第２の軸方向駆動力に変換して前記ランププレートに作用させるベルト式無段変速機において、前記ランププレートは、前記ボス部を囲繞するプレートボスと、前記プレートボスから径方向外方へ張り出して前記カム部材との間で前記遠心重錘を保持するプレート本体部とを一体に有し、前記ボス部と前記プレートボスとの相対向する周面相互が直接結合されることを第１の特徴とする。 In order to achieve the above object, the present invention provides a fixed sheave fixed to a rotating shaft, a movable sheave having a boss portion through which the rotating shaft is inserted and movable in the axial direction with respect to the rotating shaft, and the fixed sheave. And a belt that is wound around the movable sheave, and a first shift mechanism that has an actuator that applies a first axial driving force to the boss portion via a bearing, and that shifts the movable sheave in the axial direction, A ramp mechanism that includes a centrifugal mechanism that applies a second axial driving force to the boss portion and that shifts the movable sheave in the axial direction, and the centrifugal mechanism is fixed to the movable sheave. A cam member disposed on the opposite side of the bearing across the lamp plate and rotating integrally with the rotating shaft, and a centrifugal weight interposed between the lamp plate and the cam member A belt-type continuously variable transmission that converts the centrifugal force of the centrifugal weight into the second axial driving force by the cam member and acts on the ramp plate. A plate boss that surrounds the plate portion, and a plate body portion that projects radially outward from the plate boss and holds the centrifugal weight between the cam member and the boss portion and the plate boss The first feature is that the circumferential surfaces facing each other are directly coupled to each other.
　また本発明は、第１の特徴に加えて、前記プレートボスの少なくとも一部と、前記軸受の少なくとも一部とが径方向で互いにオーバラップすることを第２の特徴とする。 In addition to the first feature, the present invention has a second feature that at least a part of the plate boss and at least a part of the bearing overlap each other in the radial direction.
　また本発明は、第１又は第２の特徴に加えて、前記軸受を前記ランププレートを介して前記ボス部に支持させるべく、前記軸受の内周部が前記プレートボスに装着されることを第３の特徴とする。 According to the present invention, in addition to the first or second feature, an inner peripheral portion of the bearing is attached to the plate boss so that the bearing is supported by the boss portion via the ramp plate. Three features.
　また本発明は、第１～第３の何れかの特徴に加えて、前記ボス部の外周面には、軸方向で前記遠心機構側を向く段部が形成されており、前記ランププレートは、前記段部との間で前記軸受の内周部を軸方向に挟持する係止部を有することを第４の特徴とする。 Further, according to the present invention, in addition to any one of the first to third features, a stepped portion facing the centrifugal mechanism side in the axial direction is formed on the outer peripheral surface of the boss portion. According to a fourth aspect of the present invention, there is provided a locking portion that holds the inner peripheral portion of the bearing in the axial direction between the stepped portion and the stepped portion.
　また本発明は、前記回転軸を車幅方向に配して車両に搭載される、第１～第４の何れかの特徴を有するベルト式無段変速機であって、前記アクチュエータは、少なくとも一部が前記ベルトよりも車幅方向外方側に配設されるアクチュエータ本体と、前記アクチュエータ本体から前記ベルトよりも車幅方向内方側に延出する出力部材とを有していて、該出力部材がシフトアームを介して前記可動シーブに前記第１の軸方向駆動力を出力可能であり、前記シフトアームは、前記軸受の外周部に固定される基部と、前記基部から前記可動シーブの径方向外方側へ延出する中間部と、前記中間部から車幅方向内方側に延び且つ前記出力部材が連結される先部とを一体に有し、少なくとも前記ランププレートと前記カム部材とが軸方向で最接近したときに、前記シフトアームの前記先部の少なくとも一部と、前記カム部材の少なくとも一部とが径方向で互いにオーバラップすることを第５の特徴とする。 The present invention is also a belt-type continuously variable transmission having any one of the first to fourth features mounted on a vehicle with the rotation shaft arranged in the vehicle width direction, wherein the actuator includes at least one An actuator body disposed on the outer side in the vehicle width direction with respect to the belt, and an output member extending from the actuator body to the inner side in the vehicle width direction with respect to the belt. A member can output the first axial driving force to the movable sheave via a shift arm, and the shift arm includes a base fixed to an outer peripheral portion of the bearing, and a diameter of the movable sheave from the base. An intermediate portion extending outward in the direction of the vehicle, and a tip portion extending inward in the vehicle width direction and connected to the output member from the intermediate portion, and at least the lamp plate and the cam member Is the closest in the axial direction To, at least a portion of the tip portion of the shift arm, a fifth feature that overlap each other at least in part and the radial direction of the cam member.
　本発明において、「軸方向」とは、回転軸（実施形態で入力軸１１）の軸線に沿う方向をいい、また「径方向」とは、前記軸線を中心とした円の半径方向をいう。 In the present invention, “axial direction” refers to the direction along the axis of the rotation axis (input shaft 11 in the embodiment), and “radial direction” refers to the radial direction of a circle centered on the axis.
　本発明の第１の特徴によれば、可動シーブを軸方向にシフトさせるために、アクチュエータを有する第１シフト機構と、遠心機構を有する第２シフト機構とを併せ持つベルト式無段変速機において、遠心機構のランププレートは、可動シーブのボス部を囲繞するプレートボスと、プレートボスから径方向外方へ張り出してカム部材との間で遠心重錘を保持するプレート本体部とを一体に有し、プレートボスと可動シーブのボス部との相対向する周面相互が直接結合されるので、可動シーブとランププレート相互の結合のために従来のようにナットを特別に用いる必要はなくなり、ナットの省略により可動シーブ（ボス部）を軸方向に小型化できる。しかも、ナットの省略により、遠心重錘の配設部位をナットに影響されずに径方向内方寄りに設定可能となるため、カム部材を含む遠心機構の径方向小型化も併せて達成できる。これにより、全体として無段変速機を軸方向にも径方向にも小型化する上で有利となる。 According to a first aspect of the present invention, in the belt-type continuously variable transmission having both the first shift mechanism having an actuator and the second shift mechanism having a centrifugal mechanism in order to shift the movable sheave in the axial direction, The ramp plate of the centrifugal mechanism integrally has a plate boss surrounding the boss portion of the movable sheave and a plate main body portion projecting radially outward from the plate boss to hold the centrifugal weight between the cam member. Since the opposing circumferential surfaces of the plate boss and the movable sheave boss are directly coupled to each other, there is no need to use a nut specially for coupling the movable sheave and the lamp plate. By omitting the movable sheave (boss part), the axial direction can be reduced. In addition, by omitting the nut, the portion where the centrifugal weight is disposed can be set radially inward without being affected by the nut, so that the centrifugal mechanism including the cam member can be downsized in the radial direction. This is advantageous in reducing the size of the continuously variable transmission as a whole in both the axial direction and the radial direction.
　また第２の特徴によれば、プレートボスの少なくとも一部と、軸受の少なくとも一部とが径方向で互いにオーバラップするので、そのオーバラップにより可動シーブの軸方向小型化を図ることができる。 Further, according to the second feature, since at least a part of the plate boss and at least a part of the bearing overlap each other in the radial direction, the overlap of the movable sheave can be reduced in the axial direction.
　また第３の特徴によれば、軸受をランププレートを介して可動シーブのボス部に支持させるべく、軸受の内周部がプレートボスに装着されるので、軸受を予めプレートボスに前組みすることで、軸受及びランププレートをサブアッシーとして可動シーブに一挙に組付け可能となり、組付け作業効率を高めることができる。 Further, according to the third feature, since the inner peripheral portion of the bearing is mounted on the plate boss so that the bearing is supported on the boss portion of the movable sheave via the ramp plate, the bearing is pre-assembled on the plate boss in advance. Thus, the bearing and the lamp plate can be assembled as a sub-assembly into the movable sheave at once, and the assembling work efficiency can be improved.
　また第４の特徴によれば、可動シーブのボス部の外周面には、軸方向で遠心機構側を向く段部が形成され、ランププレートは、段部との間で軸受の内周部を軸方向に挟持する係止部を有するので、可動シーブのボス部とプレートボスとの対向周面相互を直接結合するのと同時に、段部と係止部との間に軸受の内周部を機械的に挟み込んで、軸受を位置決め・固定可能となる。これにより、軸受の位置決め・固定のための専用部品が不要となって、可動シーブの構造簡素化及び小型化が達成され、しかも軸受の位置決め・固定作業が頗る簡素化され且つ迅速化されるので、組付作業効率を高めることができる。 Further, according to the fourth feature, a stepped portion facing the centrifugal mechanism side in the axial direction is formed on the outer peripheral surface of the boss portion of the movable sheave, and the lamp plate has an inner peripheral portion of the bearing between the stepped portion and the ramp plate. Since it has a locking part that is clamped in the axial direction, the inner peripheral part of the bearing is connected between the stepped part and the locking part at the same time as the opposing peripheral surfaces of the movable sheave boss part and the plate boss are directly coupled to each other. The bearing can be positioned and fixed by mechanically sandwiching. This eliminates the need for dedicated parts for positioning and fixing the bearing, which simplifies the structure and size of the movable sheave and simplifies and speeds up the positioning and fixing of the bearing. , Assembly work efficiency can be increased.
　また第５の特徴によれば、第１シフト機構のアクチュエータは、少なくとも一部がベルトよりも車幅方向外方側に配設されるアクチュエータ本体と、ベルトよりも車幅方向内方側に延出する出力部材とを有しており、出力部材の出力を可動シーブに伝達するシフトアームは、軸受の外周部に固定される基部と、基部から可動シーブの径方向外方側へ延出する中間部と、中間部から車幅方向内方側に延び且つ出力部材が連結される先部とを一体に有し、少なくともランププレートとカム部材とが軸方向で最接近したときに、シフトアームの先部の少なくとも一部と、カム部材の少なくとも一部とが径方向で互いにオーバラップするので、アクチュエータの車幅方向外方側への張出しと、遠心機構の車幅方向内方側への張出しとを何れも抑えることができ、無段変速機の車幅方向小型化に寄与することができる。この場合、シフトアームの先部とカム部材の一部とが径方向にオーバラップしても、前述の如く第１の特徴に基づきカム部材を径方向に小型化可能であることから、シフトアームの中間部を極力短かくできて、アーム剛性を高めることができる。 According to the fifth feature, the actuator of the first shift mechanism includes at least a part of the actuator body disposed on the outer side in the vehicle width direction with respect to the belt, and the inner side in the vehicle width direction with respect to the belt. A shift arm that transmits the output of the output member to the movable sheave, and extends from the base to the radially outer side of the movable sheave. The shift arm is integrally provided with an intermediate portion and a tip portion extending inward in the vehicle width direction from the intermediate portion and connected to the output member, and at least when the lamp plate and the cam member are closest to each other in the axial direction. Since at least a part of the front part and at least a part of the cam member overlap each other in the radial direction, the actuator protrudes outward in the vehicle width direction and the centrifugal mechanism extends inward in the vehicle width direction. Suppress both overhangs Bets can be, it can contribute to the vehicle width direction size of the continuously variable transmission. In this case, even if the tip of the shift arm and a part of the cam member overlap in the radial direction, the shift arm can be reduced in the radial direction based on the first feature as described above. The intermediate part of the arm can be made as short as possible to increase the arm rigidity.
図１は本発明の第１実施形態に係るベルト式無段変速機を含むパワーユニットの平断面図である。（第１の実施の形態）FIG. 1 is a plan sectional view of a power unit including a belt-type continuously variable transmission according to a first embodiment of the present invention. (First embodiment) 図２は前記ベルト式無段変速機の要部、特に図１の２矢視部の拡大断面図（図３の２－２線断面図）であって、ベルト巻き掛け半径が最小の状態を示す図である。（第１の実施の形態）FIG. 2 is an enlarged cross-sectional view (cross-sectional view taken along the line 2-2 in FIG. 3) of the main part of the belt-type continuously variable transmission, in particular, a part indicated by an arrow 2 in FIG. FIG. (First embodiment) 図３は前記ベルト式無段変速機の第２シフト機構（遠心機構）の断面図（図２の３－３線断面図）である。（第１の実施の形態）FIG. 3 is a cross-sectional view (cross-sectional view taken along line 3-3 in FIG. 2) of the second shift mechanism (centrifugal mechanism) of the belt type continuously variable transmission. (First embodiment) 図４は前記ベルト式無段変速機の要部の拡大断面図であって、ベルト巻き掛け半径が最大の状態を示す（図２対応図）図である。（第１の実施の形態）FIG. 4 is an enlarged cross-sectional view of the main part of the belt-type continuously variable transmission, showing a state in which the belt winding radius is maximum (corresponding to FIG. 2). (First embodiment) 図５は本発明の第２実施形態に係るベルト式無段変速機の要部の拡大断面図（図２対応図）である。（第２の実施の形態）FIG. 5 is an enlarged cross-sectional view (corresponding to FIG. 2) of the main part of the belt type continuously variable transmission according to the second embodiment of the present invention. (Second Embodiment)
Ｓ１，Ｓ２・・第１，第２シフト機構
１１・・・・・入力軸（回転軸）
１４・・・・・ベルト
２１・・・・・固定シーブ
２２・・・・・可動シーブ
２２ｂ・・・・ボス部
２２ｂｓ・・・段部
２４・・・・・軸受
２４ｉ・・・・インナレース（軸受の内周部）
２４ｏ・・・・アウタレース（軸受の外周部）
４０・・・・・遠心機構
４１，４１′・・・・ランププレート
４１ａ，４１ａ′・・プレート本体部
４１ａｓ，４１ａｓ′・・係止部
４１ｂ，４１ｂ′・・プレートボス
４２・・・・・カム部材
４３・・・・・遠心重錘
５０・・・・・アクチュエータ
５０ａ・・・・出力ロッド（出力部材）
５０ｍ・・・・アクチュエータ本体
６０・・・・・シフトアーム
６０ａ，６０ｂ，６０ｃ・・シフトアームの中間部，基部，先部
７０・・・・・直接結合 S1, S2,..., First and second shift mechanism 11... Input shaft (rotary shaft)
14... Belt 21... Fixed sheave 22... Movable sheave 22 b... Boss portion 22 bs. (Bearing inner circumference)
24o ... Outer race (outer periphery of bearing)
40 ... Centrifugal mechanism 41, 41 '... Lamp plate 41a, 41a' ... Plate body 41as, 41as '... Locking parts 41b, 41b' ... Plate boss 42 ... Cam member 43 ... Centrifugal weight 50 ... Actuator 50a ... Output rod (output member)
50m ··· Actuator body 60 ··· Shift arms 60a, 60b, 60c ··· Middle portion, base portion, tip portion 70 ··· of direct connection of shift arms
　添付図面に基づいて、本発明の実施の形態を以下に説明する。 Embodiments of the present invention will be described below based on the attached drawings.
第１の実施の形態First embodiment
　本発明のベルト式無段変速機を自動二輪車に適用した第１実施形態を、図１～図４に基づいて以下に説明する。 A first embodiment in which the belt type continuously variable transmission of the present invention is applied to a motorcycle will be described below with reference to FIGS.
　自動二輪車の図示しない車体フレームには、後輪駆動用パワーユニットＵが上下揺動可能に軸支されており、後輪駆動用パワーユニットＵは、動力源たるエンジンＥと、エンジンＥの出力を無段階に変速して後輪Ｗに伝達可能なベルト式無段変速機Ｔとを備える。 A rear-wheel drive power unit U is pivotally supported on a body frame (not shown) of the motorcycle so that the rear-wheel drive can swing up and down. The rear-wheel drive power unit U continuously outputs the engine E as a power source and the output of the engine E. And a belt type continuously variable transmission T that can be transmitted to the rear wheel W.
　ベルト式無段変速機Ｔは、エンジンＥのクランク軸１０から動力が伝達される入力軸１１と、入力軸１１に平行に配置されて後輪Ｗに動力を伝達する出力軸１２と、入力軸１１に支持される駆動プーリ２０と、出力軸１２に支持される従動プーリ３０と、両プーリ２０，３０に巻き掛けられる無端状のベルト１４と、両プーリ２０，３０及びベルト１４並びに入，出力軸１１，１２を収容するミッションケース１５と、駆動プーリ２０の溝幅を可変制御する第１，第２シフト機構Ｓ１，Ｓ２とを備える。そして、入力軸１１は、本発明の回転軸に対応する。 The belt type continuously variable transmission T includes an input shaft 11 to which power is transmitted from the crankshaft 10 of the engine E, an output shaft 12 that is disposed in parallel to the input shaft 11 and transmits power to the rear wheels W, and an input shaft. 11, a drive pulley 20 supported by the output shaft 12, a driven pulley 30 supported by the output shaft 12, an endless belt 14 wound around the pulleys 20, 30, the pulleys 20, 30 and the belt 14, and input / output A transmission case 15 that accommodates the shafts 11 and 12 and first and second shift mechanisms S1 and S2 that variably control the groove width of the drive pulley 20 are provided. The input shaft 11 corresponds to the rotating shaft of the present invention.
　尚、第１，第２シフト機構Ｓ１，Ｓ２は、従動プーリ３０の溝幅を変更するものであってもよい。 The first and second shift mechanisms S1 and S2 may change the groove width of the driven pulley 30.
　ミッションケース１５は、例えば相互に着脱可能に結合される第１，第２ケース半体１５ａ，１５ｂより分割構成される。車幅方向内方側の第１ケース半体１５ａの一部は、エンジンＥのクランクケースの一部を構成していて、クランク軸１０の一端部を軸受１３を介して回転自在に支持すると共に、エンジンＥのシリンダブロック（図示せず）に着脱可能に結合される。 The mission case 15 is composed of, for example, first and second case halves 15a and 15b that are detachably coupled to each other. A part of the first case half 15a on the inner side in the vehicle width direction constitutes a part of the crankcase of the engine E, and supports one end of the crankshaft 10 via the bearing 13 so as to be rotatable. The cylinder block (not shown) of the engine E is detachably coupled.
　入，出力軸１１，１２は、車幅方向に延びるように配置される。入力軸１１は、本実施形態ではクランク軸１０の軸端に同軸且つ一体に突設されていて、ミッションケース１５内に延出している。尚、入力軸１１を、クランク軸１０とは別体としてクランク軸１０に後付けで結合してもよいし、或いは、クランク軸１０に連動機構を介して連動、連結してもよい。また、出力軸１２は、入力軸１１よりも車両後方側でミッションケース１５に回転自在に支持される。 The input and output shafts 11 and 12 are arranged to extend in the vehicle width direction. In this embodiment, the input shaft 11 is coaxially and integrally provided at the shaft end of the crankshaft 10 and extends into the mission case 15. The input shaft 11 may be connected to the crankshaft 10 later as a separate body from the crankshaft 10, or may be linked and connected to the crankshaft 10 via a linkage mechanism. The output shaft 12 is rotatably supported by the transmission case 15 on the vehicle rear side of the input shaft 11.
　駆動プーリ２０は、入力軸１１に固定される固定シーブ２１と、入力軸１１に軸方向移動可能且つ相対回転不能に支持される可動シーブ２２とを備える。そして、第１，第２シフト機構Ｓ１，Ｓ２が出力する軸方向駆動力により可動シーブ２２を軸方向にシフトさせることで、可動シーブ２２及び固定シーブ２１の相互間隔、即ち駆動プーリ２０の溝幅（従ってベルト巻き掛け半径）を変更可能である。 The drive pulley 20 includes a fixed sheave 21 that is fixed to the input shaft 11 and a movable sheave 22 that is supported by the input shaft 11 so as to be movable in the axial direction and not to be relatively rotatable. The movable sheave 22 is shifted in the axial direction by the axial driving force output from the first and second shift mechanisms S1 and S2, so that the mutual interval between the movable sheave 22 and the fixed sheave 21, that is, the groove width of the driving pulley 20 is increased. Therefore, the belt winding radius can be changed.
　一方、従動プーリ３０は、出力軸１２に固定される固定シーブ３１と、出力軸１２に軸方向移動可能且つ相対回転不能に支持される可動シーブ３２と、可動シーブ３２を固定シーブ３１側（即ち従動プーリ３０の溝幅を狭める方向）に常に付勢する戻しばね３３とを備える。そして、従動プーリ３０の可動シーブ３２は、駆動プーリ２０の溝幅変更に伴うベルト１４の張力変化に応じて軸方向に移動可能であり、これにより、従動プーリ３０の溝幅を調整可能である。 On the other hand, the driven pulley 30 includes a fixed sheave 31 fixed to the output shaft 12, a movable sheave 32 supported on the output shaft 12 so as to be axially movable and relatively non-rotatable, and the movable sheave 32 on the fixed sheave 31 side (that is, the stationary sheave 31). And a return spring 33 that always urges the driven pulley 30 in the direction of narrowing the groove width. The movable sheave 32 of the driven pulley 30 can move in the axial direction in accordance with the change in the tension of the belt 14 accompanying the change in the groove width of the drive pulley 20, thereby adjusting the groove width of the driven pulley 30. .
　而して、駆動プーリ２０が第１、第２シフト機構Ｓ１，Ｓ２の軸方向駆動力に基づいて溝幅を狭めてベルト１４の巻き掛け半径を増大させる方向に作動（従ってベルト張力が増大）すれば、その作動に連動して従動プーリ３０は、戻しばね３３の付勢力に抗して溝幅を拡げて巻き掛け半径を減少させる方向に作動する。また反対に、駆動プーリ２０が溝幅を拡げてベルト１４の巻き掛け半径を減少させる方向に作動（従ってベルト張力が減少）すれば、その作動に連動して従動プーリ３０は、戻しばね３３の付勢力により溝幅を狭めて巻き掛け半径を増大させる方向に作動する。 Thus, the drive pulley 20 operates in a direction to narrow the groove width and increase the winding radius of the belt 14 based on the axial driving force of the first and second shift mechanisms S1 and S2 (thus increasing the belt tension). In this case, the driven pulley 30 operates in a direction to increase the groove width and reduce the winding radius against the urging force of the return spring 33 in conjunction with the operation. On the other hand, if the drive pulley 20 increases the groove width and operates in a direction to decrease the winding radius of the belt 14 (and therefore the belt tension decreases), the driven pulley 30 is connected to the return spring 33 in conjunction with the operation. It operates in the direction of increasing the winding radius by narrowing the groove width by the urging force.
　このようにして駆動プーリ２０及び従動プーリ３０相互の巻き掛け半径比を変更することで、入，出力軸１１，１２間の変速比を無段階に変速可能である。 In this way, by changing the winding radius ratio between the drive pulley 20 and the driven pulley 30, the speed ratio between the input and output shafts 11 and 12 can be changed steplessly.
　次に駆動プーリ２０及び第１、第２シフト機構Ｓ１，Ｓ２の具体例を説明する。 Next, specific examples of the drive pulley 20 and the first and second shift mechanisms S1 and S2 will be described.
　駆動プーリ２０の可動シーブ２２は、テーパ状の可動シーブ本体２２ａと、可動シーブ本体２２ａの中心部に一体に結合（本実施形態では鋳包み）されて軸方向に延びる円筒状のボス部２２ｂとを有する。ボス部２２ｂは、入力軸１１に嵌合したカラー１８を介して入力軸１１に軸方向摺動可能に嵌合、支持される。カラー１８とボス部２２ｂとの嵌合面間には、嵌合面間に潤滑油を封入するための一対のシール部材２５，２６が相互に間隔をおいて介装される。尚、カラー１８は、固定シーブ２１と一体に構成してもよい。 The movable sheave 22 of the drive pulley 20 includes a tapered movable sheave body 22a, and a cylindrical boss portion 22b that is integrally coupled to the central portion of the movable sheave body 22a (cast in this embodiment) and extends in the axial direction. Have The boss portion 22b is fitted and supported on the input shaft 11 via the collar 18 fitted to the input shaft 11 so as to be slidable in the axial direction. Between the fitting surfaces of the collar 18 and the boss portion 22b, a pair of seal members 25 and 26 for enclosing lubricating oil between the fitting surfaces are interposed at intervals. The collar 18 may be formed integrally with the fixed sheave 21.
　また駆動プーリ２０の固定シーブ２１は、可動シーブ本体２２ａとは逆テーパ状の固定シーブ本体２１ａと、固定シーブ本体２１ａの中心部に位置する環状の厚肉部２１ｂとを一体に有する。厚肉部２１ｂは、入力軸１１の先部にスプライン嵌合される。そして、固定シーブ本体２１ａと可動シーブ本体２２ａとには、両者に跨がらせてベルト１４が巻き掛けられる。 Further, the fixed sheave 21 of the drive pulley 20 integrally includes a fixed sheave body 21a having a reverse taper shape with respect to the movable sheave body 22a and an annular thick portion 21b positioned at the center of the fixed sheave body 21a. The thick portion 21b is splined to the tip of the input shaft 11. The belt 14 is wound around the fixed sheave main body 21a and the movable sheave main body 22a so as to straddle both.
　入力軸１１の先端部にはナット１６が螺合される。ナット１６は、ワッシャ１７、固定シーブ２１、カラー１８、及び後述する遠心機構４０のカム部材４２をクランク軸１０の外周段部との間で一体的に挟持、締結する。従って、ナット１６の締結状態では、固定シーブ２１、カラー１８及びカム部材４２はクランク軸１０と常に一体に回転する。 A nut 16 is screwed to the tip of the input shaft 11. The nut 16 integrally clamps and fastens the washer 17, the fixed sheave 21, the collar 18, and the cam member 42 of the centrifugal mechanism 40 described later with the outer peripheral step portion of the crankshaft 10. Accordingly, when the nut 16 is fastened, the fixed sheave 21, the collar 18 and the cam member 42 always rotate integrally with the crankshaft 10.
　ところで第１シフト機構Ｓ１は、可動シーブ２２のボス部２２ｂに軸受２４を介して第１の軸方向駆動力を付与する電子制御のアクチュエータ５０を有しており、上記第１の軸方向駆動力により可動シーブ２２を固定シーブ２１に対し軸方向にシフトさせる。また第２シフト機構Ｓ２は、可動シーブ２２のボス部２２ｂに第２の軸方向駆動力を付与する遠心機構４０を有しており、上記第２の軸方向駆動力により可動シーブ２２を固定シーブ２１に対し軸方向にシフトさせる。 Incidentally, the first shift mechanism S1 includes an electronically controlled actuator 50 that applies a first axial driving force to the boss portion 22b of the movable sheave 22 via the bearing 24, and the first axial driving force described above. As a result, the movable sheave 22 is shifted in the axial direction with respect to the fixed sheave 21. The second shift mechanism S2 includes a centrifugal mechanism 40 that applies a second axial driving force to the boss portion 22b of the movable sheave 22, and the movable sheave 22 is fixed to the fixed sheave by the second axial driving force. 21 is shifted in the axial direction.
　第２シフト機構Ｓ２の遠心機構４０は、可動シーブ２２に固定されるランププレート４１と、ランププレート４１を挟んで軸受２４とは反対側に配置される上記したカム部材４２と、ランププレート４１及びカム部材４２間に介装されて周方向に互いに間隔をおいて並ぶ複数の遠心重錘４３とを有する。遠心重錘４３は、本実施形態では円柱状のローラより構成されるが、ローラの他、ランププレート４１及びカム部材４２に対し摺動可能な種々の形態（例えばボール）を選定可能である。 The centrifugal mechanism 40 of the second shift mechanism S2 includes a ramp plate 41 fixed to the movable sheave 22, the cam member 42 disposed on the opposite side of the bearing 24 across the lamp plate 41, the ramp plate 41, A plurality of centrifugal weights 43 are interposed between the cam members 42 and are arranged at intervals in the circumferential direction. The centrifugal weight 43 is constituted by a cylindrical roller in this embodiment, but various forms (for example, balls) that can slide with respect to the lamp plate 41 and the cam member 42 can be selected in addition to the roller.
　カム部材４２は、概ね円盤状のカム部材本体４２ｍと、カム部材本体４２ｍの外周端よりランププレート４１側に屈曲して延びる外周筒部４２ｔとを一体に備える。そしてカム部材４２の、ランププレート４１側の対向側面には、複数の遠心重錘４３をそれぞれ収容する複数のカム溝部４４が、互いに周方向に間隔をおいて且つ各々径方向に延びるように形成される。 The cam member 42 is integrally provided with a generally disc-shaped cam member main body 42m and an outer peripheral cylindrical portion 42t that bends and extends from the outer peripheral end of the cam member main body 42m toward the lamp plate 41. On the opposite side surface of the cam member 42 on the lamp plate 41 side, a plurality of cam groove portions 44 that respectively accommodate a plurality of centrifugal weights 43 are formed so as to extend in the radial direction at intervals in the circumferential direction. Is done.
　各カム溝部４４の底面（即ちランププレート４１との対向面）は、ランププレート４１に向かって径方向外方側に傾斜したカム面４４ｃに構成される。またカム部材４２の外周筒部４２ｔの内周面には、周方向に並ぶカム溝部４４の間に、径方向内向きの回止め突条４５が、入力軸１１の軸線に沿うように突設される。 The bottom surface of each cam groove 44 (that is, the surface facing the lamp plate 41) is configured as a cam surface 44c that is inclined radially outward toward the lamp plate 41. On the inner peripheral surface of the outer peripheral cylindrical portion 42 t of the cam member 42, a radially inward rotation-stop protrusion 45 is provided so as to extend along the axis of the input shaft 11 between cam grooves 44 arranged in the circumferential direction. Is done.
　一方、ランププレート４１は、可動シーブ２２のボス部２２ｂを同心状に囲繞する円筒状のプレートボス４１ｂと、プレートボス４１ｂの一端から径方向外方に張出すプレート本体部４１ａとを一体に有する。プレート本体部４１ａは、径方向外方に向かって、軸方向でカム部材４２側（即ち図２で右方側）に傾斜して延びるように形成される。そして、プレート本体部４１ａとカム溝部４４との間で遠心重錘４３が摺動可能に保持される。 On the other hand, the lamp plate 41 integrally includes a cylindrical plate boss 41b that concentrically surrounds the boss portion 22b of the movable sheave 22, and a plate body portion 41a that projects radially outward from one end of the plate boss 41b. . The plate body 41a is formed so as to extend obliquely outward in the radial direction toward the cam member 42 in the axial direction (that is, the right side in FIG. 2). The centrifugal weight 43 is slidably held between the plate main body 41a and the cam groove 44.
　プレートボス４１ｂの外周面には、軸受２４の内周部、即ちインナレース２４ｉが圧入により嵌合固定される。尚、プレートボス４１ｂに対するインナレース２４ｉの固定手段として、圧入以外の固定手段、例えば接着、カシメ、溶接、止め輪（例えばサークリップ）等も採用可能である。 The inner peripheral portion of the bearing 24, that is, the inner race 24i is fitted and fixed to the outer peripheral surface of the plate boss 41b by press-fitting. As the means for fixing the inner race 24i to the plate boss 41b, fixing means other than press fitting, such as adhesion, caulking, welding, retaining rings (for example, circlip), etc., can be employed.
　プレートボス４１ｂと可動シーブ２２のボス部２２ｂとの相対向する周面相互間は直接結合７０される。直接結合７０のための結合手段として、本実施形態ではボス部２２ｂ外周面にプレートボス４１ｂの内周面を直接螺合、緊締している。 The mutually opposed peripheral surfaces of the plate boss 41 b and the boss portion 22 b of the movable sheave 22 are directly coupled 70. As a coupling means for the direct coupling 70, in this embodiment, the inner peripheral surface of the plate boss 41b is directly screwed and tightened to the outer peripheral surface of the boss portion 22b.
　また可動シーブ２２のボス部２２ｂの外周面には、軸方向で遠心機構４０側（即ち図２で右方側）を向く立ち上がり段部２２ｂｓが形成される。一方、ランププレート４１は、プレート本体部４１ａの径方向内端部において、入力軸１１の軸線と直交する環状平坦面又は円弧面よりなる係止部４１ａｓを有する。そして、係止部４１ａｓは、上記段部２２ｂｓとの間で軸受２４のインナレース２４ｉを軸方向に挟着するが、その挟着をガタなく確実に行わせるために、プレートボス４１ｂの他端の端面と段部２２ｂｓとの間には軸方向空隙４６が設定されている。 Further, on the outer peripheral surface of the boss portion 22b of the movable sheave 22, a rising step portion 22bs that faces the centrifugal mechanism 40 side (that is, the right side in FIG. 2) in the axial direction is formed. On the other hand, the lamp plate 41 has a locking portion 41as made of an annular flat surface or an arc surface orthogonal to the axis of the input shaft 11 at the radially inner end of the plate body 41a. The locking portion 41as clamps the inner race 24i of the bearing 24 in the axial direction with the stepped portion 22bs. A gap 46 in the axial direction is set between the end face and the step portion 22bs.
　またプレートボス４１ｂの少なくとも一部（本実施形態では大部分）と、軸受２４の少なくとも一部（本実施形態では大部分）とが、径方向に互いにオーバラップし、即ち軸方向で互いに同一の領域に位置している。これにより、可動シーブ２２の軸方向小型化が図られる。 Further, at least a part (most part in the present embodiment) of the plate boss 41b and at least a part (most part in the present embodiment) of the bearing 24 overlap each other in the radial direction, that is, the same in the axial direction. Located in the area. Thereby, the axial direction size reduction of the movable sheave 22 is achieved.
　また、プレート本体部４１ａは、カム部材４２（カム溝部４４）との間で遠心重錘４３を摺動可能に挟持する重錘支持部４１ａｗと、周方向に並ぶ重錘支持部４１ａｗの間に在ってカム部材４２の回止め突条４５に軸方向摺動可能に係合する係合溝部４１ａｇとを有し、係合溝部４１ａｇは径方向外向きに開口している。本実施形態では、係合溝部４１ａｇが回止め突条４５が直接接触するのを回避して両者の相対摺動を円滑化するための溝付きの樹脂製ガイド部材４７が係合溝部４１ａｇに一体的に被着される。 Further, the plate main body portion 41a is interposed between a weight support portion 41aw that slidably holds the centrifugal weight 43 with the cam member 42 (cam groove portion 44), and a weight support portion 41aw arranged in the circumferential direction. And an engaging groove portion 41ag that is slidably engaged with the rotation stop protrusion 45 of the cam member 42 in the axial direction, and the engaging groove portion 41ag opens outward in the radial direction. In the present embodiment, the resin guide member 47 with a groove for preventing the engagement groove portion 41ag from directly contacting the anti-rotation protrusion 45 and smoothing the relative sliding therebetween is integrated with the engagement groove portion 41ag. To be applied.
　回止め突条４５及び係合溝部４１ａｇ（従ってガイド部材４７）相互の係合によれば、カム部材４２（従って入力軸１１）に対する可動シーブ２２の相対回転が規制され且つ軸方向摺動が許容される。尚、可動シーブ２２の入力軸１１に対する上記のような回り止め構造に代えて、可動シーブ２２のボス部２２ｂとカラー１８とをスプライン嵌合させてもよく、また特にカラー１８を省略してボス部２２ｂを入力軸１１外周に直接嵌合させる場合は、ボス部２２ｂを入力軸１１外周に直接、スプライン嵌合させてもよい。 The mutual engagement between the rotation protrusion 45 and the engagement groove 41ag (and hence the guide member 47) restricts the relative rotation of the movable sheave 22 with respect to the cam member 42 (and hence the input shaft 11) and allows axial sliding. Is done. Note that the boss portion 22b of the movable sheave 22 and the collar 18 may be spline-fitted in place of the above-described detent structure with respect to the input shaft 11 of the movable sheave 22, and in particular, the collar 18 is omitted and the boss is omitted. When the portion 22b is directly fitted to the outer periphery of the input shaft 11, the boss portion 22b may be directly splined to the outer periphery of the input shaft 11.
　而して、第２シフト機構Ｓ２の遠心機構４０は、例えば次のように作動する。エンジンＥの低速運転域（図２参照）よりクランク軸１０従って入力軸１１の回転速度が上昇して遠心重錘４３の遠心力が増大すると、遠心重錘４３は、遠心力でカム部材４２のカム面４４ｃ上をランププレート４１に向かって径方向外方側に斜め方向に摺動する。そのとき、遠心重錘４３は、ランププレート４１を介して可動シーブ２２をベルト１４の張力に抗して固定シーブ２１側に移動させる軸方向駆動力を作用させ、これにより、駆動プーリ２０は溝幅を狭めてベルト巻き掛け半径を増大させる。 Thus, the centrifugal mechanism 40 of the second shift mechanism S2 operates as follows, for example. When the rotational speed of the crankshaft 10 and hence the input shaft 11 is increased from the low speed operation range of the engine E (see FIG. 2) and the centrifugal force of the centrifugal weight 43 is increased, the centrifugal weight 43 is The cam surface 44c slides in an oblique direction outward in the radial direction toward the lamp plate 41. At that time, the centrifugal weight 43 applies an axial driving force that moves the movable sheave 22 toward the fixed sheave 21 against the tension of the belt 14 via the ramp plate 41, whereby the driving pulley 20 is grooved. Narrow the width to increase the belt wrap radius.
　一方、エンジンＥの高速運転域（図４参照）よりクランク軸１０の回転速度が下降して遠心重錘４３の遠心力が減少すると、遠心重錘４３が可動シーブ２２に作用させる軸方向駆動力よりもベルト１４の張力が上回るようになるため、駆動プーリ２０が溝幅を拡げてベルト巻き掛け半径を減少させる。 On the other hand, when the rotational speed of the crankshaft 10 decreases from the high-speed operating range of the engine E (see FIG. 4) and the centrifugal force of the centrifugal weight 43 decreases, the axial driving force that the centrifugal weight 43 acts on the movable sheave 22 Since the tension of the belt 14 exceeds that of the belt 14, the drive pulley 20 widens the groove width to reduce the belt winding radius.
　このようにして第２シフト機構Ｓ２の遠心機構４０は、カム部材４２が遠心重錘４３の遠心力を可動シーブ２２に対する軸方向駆動力に変換してランププレート４１に作用させる。そして、その変換された軸方向駆動力は、遠心重錘４３の遠心力（即ち入力軸１１の回転速度）の増減変化に応じて増減変化する。 In this way, in the centrifugal mechanism 40 of the second shift mechanism S2, the cam member 42 converts the centrifugal force of the centrifugal weight 43 into the axial driving force with respect to the movable sheave 22, and acts on the lamp plate 41. Then, the converted axial driving force changes in accordance with the increase / decrease change in the centrifugal force of the centrifugal weight 43 (that is, the rotational speed of the input shaft 11).
　ところで第１シフト機構Ｓ１のアクチュエータ５０は、少なくとも一部（本実施形態では大部分）がベルト１４よりも車幅方向外方側（図１で左側）に配設されるアクチュエータ本体５０ｍと、アクチュエータ本体５０ｍからベルト１４よりも車幅方向内方側（図１で右側）に延出する出力部材としての出力ロッド５０ａとを有しており、出力ロッド５０ａがシフトアーム６０を介して可動シーブ２２に軸方向駆動力を出力可能である。 By the way, the actuator 50 of the first shift mechanism S1 includes an actuator main body 50m at least a part (most part in the present embodiment) disposed on the outer side in the vehicle width direction (left side in FIG. 1) than the belt 14, and an actuator The main body 50m has an output rod 50a as an output member extending inward in the vehicle width direction (right side in FIG. 1) from the belt 14 and the output rod 50a is connected to the movable sheave 22 via the shift arm 60. Axial driving force can be output.
　アクチュエータ本体５０ｍは、ミッションケース１５の第２ケース半体１５ｂに着脱可能に装着されて複数のケース要素に分割可能なアクチュエータケース５１を有する。アクチュエータケース５１には、例えば電動モータ５２と、電動モータ５２の出力回転を減速して伝達する減速歯車機構５３と、減速歯車機構５３の出力回転を出力ロッド５０ａの軸方向移動に変換する送り螺子機構５４とが内蔵される。 The actuator body 50m has an actuator case 51 that is detachably attached to the second case half 15b of the mission case 15 and can be divided into a plurality of case elements. The actuator case 51 includes, for example, an electric motor 52, a reduction gear mechanism 53 that reduces and transmits the output rotation of the electric motor 52, and a feed screw that converts the output rotation of the reduction gear mechanism 53 into axial movement of the output rod 50a. A mechanism 54 is incorporated.
　出力ロッド５０ａは、送り螺子機構５４に連動連結（本実施形態では送り螺子機構５４の出力螺子軸５４ａに一体に結合）されてアクチュエータケース５１の内側壁を通してミッションケース１５内に延出する。そして、出力ロッド５０ａの先端部には、シフトアーム６０に対する被係合部としての係合凹部５５が設けられる。 The output rod 50 a is interlocked with the feed screw mechanism 54 (in this embodiment, integrally coupled to the output screw shaft 54 a of the feed screw mechanism 54) and extends into the mission case 15 through the inner wall of the actuator case 51. An engaging recess 55 as an engaged portion with respect to the shift arm 60 is provided at the distal end portion of the output rod 50a.
　シフトアーム６０は、軸受２４の外周部、即ちアウタレース２４ｏに嵌合固定される環状の基部６０ｂと、基部６０ｂから可動シーブ２２の径方向外方側へ延出する中間部６０ａと、中間部６０ａの先端から車幅方向内方側（図２で右側）に屈曲して延びる先部６０ｃとを一体に有する。先部６０ｃには、径方向外方に延びる連結部材６５の基端が固着（本実施形態では圧入）される。アウタレース２４ｏは、例えばサークリップ等の係止具２７を以て着脱可能にシフトアーム６０の基部６０ｂに固定される。 The shift arm 60 includes an outer peripheral portion of the bearing 24, that is, an annular base portion 60b fitted and fixed to the outer race 24o, an intermediate portion 60a extending from the base portion 60b to the radially outer side of the movable sheave 22, and an intermediate portion 60a. And a tip portion 60c that bends and extends inwardly in the vehicle width direction (right side in FIG. 2) from the front end. A proximal end of a connecting member 65 extending radially outward is fixed to the front portion 60c (in this embodiment, press-fitted). The outer race 24o is fixed to the base 60b of the shift arm 60 so as to be detachable with a locking tool 27 such as a circlip.
　連結部材６５の先部は、出力ロッド５０ａ先端の係合凹部５５に首振り可能に嵌合連結される。尚、本実施形態では、出力ロッド５０ａの係合凹部５５及び連結部材６５が互いに協働して首振り可能に嵌合連結するものを例示したが、出力ロッド５０ａ及び連結部材６５相互を連動連結するために、出力ロッド５０ａ及び連結部材６５相互を、実施形態とは別の結合手段で結合してもよい。 The tip portion of the connecting member 65 is fitted and connected to the engaging recess 55 at the tip of the output rod 50a so as to be swingable. In the present embodiment, the engaging recess 55 and the connecting member 65 of the output rod 50a are illustrated as fitting and connected so as to be able to swing in cooperation with each other. However, the output rod 50a and the connecting member 65 are linked together. Therefore, the output rod 50a and the connecting member 65 may be coupled to each other by a coupling means different from the embodiment.
　また少なくともランププレート４１とカム部材４２とが軸方向で最接近したとき（図２を参照）には、シフトアーム６０の先部６０ｃの少なくとも一部（本実施形態では大部分）と、遠心機構４０のカム部材４２の少なくとも一部（本実施形態では外周筒部４２ｔの大部分）とは、径方向で互いにオーバラップし、即ち軸方向で互いに同一の領域に位置する。 When at least the lamp plate 41 and the cam member 42 are closest to each other in the axial direction (see FIG. 2), at least a part (most part in the present embodiment) of the tip 60c of the shift arm 60, and a centrifugal mechanism At least a part of the 40 cam members 42 (most part of the outer peripheral cylindrical portion 42t in this embodiment) overlaps each other in the radial direction, that is, is located in the same region in the axial direction.
　而して、第１シフト機構Ｓ１においては、電動モータ５２の出力回転がアクチュエータ５０内で減速歯車機構５３及び送り螺子機構５４を介して出力ロッド５０ａに伝達され、出力ロッド５０ａからシフトアーム６０、軸受２４及びランププレート４１を介して可動シーブ２２のボス部２２ｂに軸方向駆動力として伝達される。 Thus, in the first shift mechanism S1, the output rotation of the electric motor 52 is transmitted to the output rod 50a via the reduction gear mechanism 53 and the feed screw mechanism 54 in the actuator 50, and the shift arm 60, It is transmitted as an axial driving force to the boss portion 22 b of the movable sheave 22 via the bearing 24 and the lamp plate 41.
　次に、第１実施形態の作用を説明する。ベルト式無段変速機Ｔにおいては、入，出力軸１１，１２間の変速のために可動シーブ２２をシフトさせるに当たり、電動式の第１シフト機構Ｓ１に加えて、遠心式の第２シフト機構Ｓ２を併用している。 Next, the operation of the first embodiment will be described. In the belt type continuously variable transmission T, in order to shift the movable sheave 22 for shifting between the input and output shafts 11 and 12, in addition to the electric first shift mechanism S1, a centrifugal second shift mechanism is provided. S2 is used together.
　この場合、特に第１シフト機構Ｓ１では、自動二輪車の運転状況やエンジンＥの運転状態等に応じて車載の電子制御装置がアクチュエータ５０（具体的には電動モータ５２）を作動制御して可動シーブ２２の軸方向駆動力を制御することで、駆動プーリ２０の溝幅（ベルト巻き掛け半径）が可変制御されて入，出力軸１１，１２間の変速が行われる。一方、第２シフト機構Ｓ２では、エンジンＥの回転速度上昇（従って遠心重錘４３の遠心力増大）に応じて遠心機構４０が可動シーブ２２に対する軸方向駆動力を増大させる。 In this case, particularly in the first shift mechanism S1, an on-vehicle electronic control device controls the operation of the actuator 50 (specifically, the electric motor 52) in accordance with the operating state of the motorcycle, the operating state of the engine E, etc. By controlling the axial driving force 22, the groove width (belt wrapping radius) of the driving pulley 20 is variably controlled, and the speed change between the output shafts 11 and 12 is performed. On the other hand, in the second shift mechanism S2, the centrifugal mechanism 40 increases the axial driving force with respect to the movable sheave 22 in accordance with the increase in the rotational speed of the engine E (accordingly, the increase in the centrifugal force of the centrifugal weight 43).
　そして、駆動プーリ２０の可動シーブ２２は、第１，第２シフト機構Ｓ１，Ｓ２が各々出力する軸方向駆動力の総和によりシフトさせられることから、アクチュエータ５０の電力負荷の軽減が図られる。また可動シーブ２２に対する軸方向駆動力の増強がなされることで迅速なシフトアップが可能となり、燃費の向上が図られる。一方、第２シフト機構Ｓ２の軸方向駆動力を抑制するように第１シフト機構Ｓ１の軸方向駆動力を制御することで、シフトアップが抑制され、加速性能の向上が図られる。 Since the movable sheave 22 of the drive pulley 20 is shifted by the sum of the axial driving forces output by the first and second shift mechanisms S1 and S2, the power load on the actuator 50 can be reduced. Further, since the axial driving force with respect to the movable sheave 22 is increased, a quick shift up is possible, and the fuel consumption is improved. On the other hand, by controlling the axial driving force of the first shift mechanism S1 so as to suppress the axial driving force of the second shift mechanism S2, shift up is suppressed and acceleration performance is improved.
　ところで本実施形態の第２シフト機構Ｓ２においては、遠心機構４０のランププレート４１が、可動シーブ２２のボス部２２ｂを同心状に囲繞するプレートボス４１ｂと、プレートボス４１ｂから径方向外方へ張り出してカム部材４２との間で遠心重錘４３を保持するプレート本体部４１ａとを一体に有していて、ボス部２２ｂとプレートボス４１ｂとの相対向する周面相互間が直接結合７０（実施形態は螺合）される。これにより、可動シーブ２２とランププレート４１との結合のために、特許文献１の従来技術の如くナットを特別に用いる必要はなくなり、ナットの省略により可動シーブ２２（ボス部２２ｂ）を軸方向に小型化可能となる。しかもナット省略により、遠心重錘４３の配設位置をナットに影響されずに径方向内方寄りに設定可能となるため、遠心重錘４３を保持するカム部材４２を含む遠心機構４０の径方向小型化も併せて達成可能となる。その結果、全体として可動シーブ２２及び第２シフト機構Ｓ２の組立体（延いては無段変速機Ｔ）を軸方向にも径方向にも小型化する上で有利となる。 By the way, in the second shift mechanism S2 of the present embodiment, the ramp plate 41 of the centrifugal mechanism 40 protrudes radially outward from the plate boss 41b concentrically surrounding the boss portion 22b of the movable sheave 22 and the plate boss 41b. The plate body portion 41a for holding the centrifugal weight 43 is integrally formed with the cam member 42, and the opposing circumferential surfaces of the boss portion 22b and the plate boss 41b are directly coupled 70 (implementation). The form is screwed). As a result, it is not necessary to use a nut specially as in the prior art of Patent Document 1 for coupling the movable sheave 22 and the lamp plate 41, and the movable sheave 22 (boss portion 22b) can be moved in the axial direction by omitting the nut. Miniaturization is possible. In addition, since the nut is omitted, the disposition position of the centrifugal weight 43 can be set inward in the radial direction without being affected by the nut, and thus the radial direction of the centrifugal mechanism 40 including the cam member 42 that holds the centrifugal weight 43. Miniaturization can also be achieved. As a result, it is advantageous to downsize the assembly of the movable sheave 22 and the second shift mechanism S2 (and hence the continuously variable transmission T) as a whole in both the axial direction and the radial direction.
　また本実施形態では、軸受２４のインナレース２４ｉが、プレートボス４１ｂに装着（圧入）されている。これにより、軸受２４を予めプレートボス４１ｂに前組みしておくことで、軸受２４及びランププレート４１をサブアッシーとして可動シーブ２２に一挙に組付け可能となり、それだけ組付け作業効率が向上する。 In this embodiment, the inner race 24i of the bearing 24 is mounted (press-fitted) on the plate boss 41b. Thus, by pre-assembling the bearing 24 to the plate boss 41b in advance, the bearing 24 and the lamp plate 41 can be assembled as a sub-assembly into the movable sheave 22 at once, and the assembling work efficiency is improved accordingly.
　しかも可動シーブ２２のボス部２２ｂの外周面には、軸方向で遠心機構４０側を向く段部２２ｂｓが形成されており、ランププレート４１は、段部２２ｂｓとの間で軸受２４のインナレース２４ｉを軸方向に挟持する係止部４１ａｓをプレート本体部４１ａの径方向内端部に有している。これにより、可動シーブ２２のボス部２２ｂとランププレート４１のプレートボス４１ｂとの対向周面相互を直接結合７０（実施形態では螺合緊締）するのと同時に、段部２２ｂｓと係止部４１ａｓとの間にインナレース２４ｉを機械的に挟み込んで、軸受２４を位置決め・固定可能となるため、軸受２４の位置決め・固定のための専用部品が不要となって、可動シーブ２２の構造簡素化及び小型化が達成され、しかも軸受２４の位置決め・固定作業が頗る簡素化され且つ迅速化される。 In addition, a step portion 22bs that faces the centrifugal mechanism 40 in the axial direction is formed on the outer peripheral surface of the boss portion 22b of the movable sheave 22, and the inner race 24i of the bearing 24 between the lamp plate 41 and the step portion 22bs is formed. Is provided at the radially inner end of the plate body 41a. As a result, the opposing peripheral surfaces of the boss portion 22b of the movable sheave 22 and the plate boss 41b of the lamp plate 41 are directly coupled 70 (screw tightening in the embodiment), and at the same time, the step portion 22bs and the locking portion 41as Since the inner race 24i is mechanically sandwiched between the two, the bearing 24 can be positioned and fixed, so that no dedicated parts for positioning and fixing the bearing 24 are required, and the structure of the movable sheave 22 is simplified and reduced in size. In addition, the positioning and fixing work of the bearing 24 is simplified and speeded up.
　また本実施形態の第１シフト機構Ｓ１のアクチュエータ５０は、大部分がベルト１４よりも車幅方向外方側（図１で左側）に配設されるアクチュエータ本体５０ｍと、アクチュエータ本体５０ｍからベルト１４よりも車幅方向内方側（図１で右側）に延出する出力ロッド５０ａとを有しており、出力ロッド５０ａの出力を可動シーブ２２に伝達するシフトアーム６０が、軸受２４のアウタレース２４ｏに固定される基部６０ｂと、基部６０ｂから可動シーブ２２の径方向外方側へ延出する中間部６０ａと、中間部６０ａの先端から車幅方向内方側に延び且つ出力ロッド５０ａが連結される先部６０ｃとを一体に有し、ランププレート４１とカム部材４２とが軸方向で最接近したときには、先部６０ｃの一部と、カム部材４２の外周筒部４２ｔの一部とが、径方向に互いにオーバラップしている。これにより、アクチュエータ５０の車幅方向外方側への張出しと、遠心機構４０の車幅方向内方側への張出しとが共に効果的に抑えられて、無段変速機Ｔの車幅方向小型化が図られる。この場合、シフトアーム６０の先部６０ｃとカム部材４２の外周筒部４２ｔとが径方向にオーバラップしても、前述のようにカム部材４２を径方向に小型化可能としたことから、シフトアーム６０の中間部６０ａを径方向に極力短かくでき、それだけアーム剛性が高められる。 Further, the actuator 50 of the first shift mechanism S1 of the present embodiment is mostly an actuator main body 50m disposed on the outer side in the vehicle width direction (left side in FIG. 1) than the belt 14, and the actuator main body 50m to the belt 14 And an output rod 50a extending inward in the vehicle width direction (right side in FIG. 1), and a shift arm 60 that transmits the output of the output rod 50a to the movable sheave 22 is an outer race 24o of the bearing 24. A base portion 60b fixed to the base portion 60b, an intermediate portion 60a extending from the base portion 60b to the radially outer side of the movable sheave 22, and an output rod 50a extending from the tip of the intermediate portion 60a to the inner side in the vehicle width direction. And the lamp plate 41 and the cam member 42 are closest to each other in the axial direction, and a part of the tip 60c and the outer peripheral cylindrical portion 42 of the cam member 42 are provided. Some of the have overlap each other in the radial direction. Thus, the extension of the actuator 50 to the outer side in the vehicle width direction and the extension of the centrifugal mechanism 40 to the inner side in the vehicle width direction are both effectively suppressed, and the continuously variable transmission T can be reduced in the vehicle width direction. Is achieved. In this case, even if the tip portion 60c of the shift arm 60 and the outer peripheral cylindrical portion 42t of the cam member 42 overlap in the radial direction, the cam member 42 can be downsized in the radial direction as described above. The intermediate portion 60a of the arm 60 can be made as short as possible in the radial direction, and the arm rigidity can be increased accordingly.
第２の実施の形態Second embodiment
　次に図５を参照して、本発明の第２実施形態を説明する。第１実施形態では、ランププレート４１のプレートボス４１ｂがプレート本体部４１ａに対しカム部材４２とは反対側に延出し、且つプレートボス４１ｂの外周面に軸受２４のインナレース２４ｉを嵌着しているが、第２実施形態は、ランププレート４１′のプレートボス４１ｂ′がプレート本体部４１ａ′に対しカム部材４２側に延出し、且つ可動シーブ２２のボス部２２ｂ外周面上に軸受２４のインナレース２４ｉが、プレートボス４１ｂ′とは軸方向に隣接した状態で嵌合される点で、第１実施形態と相違している。 Next, a second embodiment of the present invention will be described with reference to FIG. In the first embodiment, the plate boss 41b of the lamp plate 41 extends to the side opposite to the cam member 42 with respect to the plate body 41a, and the inner race 24i of the bearing 24 is fitted on the outer peripheral surface of the plate boss 41b. However, in the second embodiment, the plate boss 41b 'of the lamp plate 41' extends toward the cam member 42 with respect to the plate body 41a ', and the inner surface of the bearing 24 is formed on the outer peripheral surface of the boss 22b of the movable sheave 22. The race 24i is different from the first embodiment in that the race 24i is fitted to the plate boss 41b 'in an axially adjacent state.
　第２実施形態でも、プレートボス４１ｂ′と可動シーブ２２のボス部２２ｂとの相対向する周面相互間は直接結合７０されており、その結合手段として、第１実施形態と同様、ボス部２２ｂ外周にプレートボス４１ｂ′の内周を直接、螺合緊締している。そして、その螺合緊締により、ボス部２２ｂ外周上に存する軸受２４のインナレース２４ｉが、ボス部２２ｂの立ち上がり段部２２ｂｓと、ランププレート４１′のプレート本体部４１ａの径方向内端部（係止部４１ａｓ′）との間に挟持、固定される。 Also in the second embodiment, the opposing circumferential surfaces of the plate boss 41b ′ and the boss portion 22b of the movable sheave 22 are directly coupled 70, and as a coupling means, the boss portion 22b is the same as in the first embodiment. The inner periphery of the plate boss 41b 'is directly screwed to the outer periphery. Then, due to the screw tightening, the inner race 24i of the bearing 24 existing on the outer periphery of the boss portion 22b causes the rising step portion 22bs of the boss portion 22b and the radially inner end portion (engagement) of the plate main body portion 41a of the lamp plate 41 ′. It is clamped and fixed between the stop portions 41as ′).
　第２実施形態のその他の構成は、第１実施形態と基本的に同じであるため、各構成部材には、第１実施形態の対応する構成部材と参照符号と同じにして、具体的な構造説明を省略する。そして、第２実施形態によれば、第１実施形態の上記した作用効果と同様の作用効果を達成可能である。 Since the other configuration of the second embodiment is basically the same as that of the first embodiment, each component member is the same as the corresponding component member of the first embodiment and has a specific structure. Description is omitted. And according to 2nd Embodiment, the effect similar to the above-described effect of 1st Embodiment can be achieved.
　以上、本発明の実施形態について説明したが、本発明は上記実施形態に限定されるものではなく、本発明の要旨を逸脱することなく種々の設計変更を行うことが可能である。 As mentioned above, although embodiment of this invention was described, this invention is not limited to the said embodiment, A various design change is possible without deviating from the summary of this invention.
　例えば、前記実施形態では、ベルト式無段変速機Ｔを自動二輪車に搭載したものを例示したが、本発明のベルト式無段変速機は、自動二輪車以外の種々の車両、例えば自動三輪車等にも適用可能である。 For example, in the above-described embodiment, the belt type continuously variable transmission T is illustrated as being mounted on a motorcycle. However, the belt type continuously variable transmission of the present invention is applicable to various vehicles other than motorcycles, such as a motor tricycle. Is also applicable.
　また前記実施形態では、ランププレート４１，４１′のプレートボス４１ｂ，４１ｂ′と可動シーブ２２のボス部２２ｂとの対向周面間を直接結合７０するための結合手段として、螺合手段（ネジ止め）を採用したものを例示したが、本発明では、螺合以外の種々の結合手法を適用可能である。例えば、上記対向周面間を直接圧入したり、或いは、上記対向周面間をスプライン嵌合させた上でスプライン嵌合部を直接圧入したり、或いはまた、上記対向周面間を接着又は溶接で直接結合したりしてもよい。更には、ランププレート４１，４１′のプレートボス４１ｂ，４１ｂ′と可動シーブ２２のボス部２２ｂの端面をカシメ加工することで上記対向周面に相互に食い込む凹凸係合部を形成してもよい。また、上記対向周面間を螺合、圧入、スプライン圧入、接着又は溶接により直接結合したものに対して更に上記端面のカシメ加工を施すことで結合強度をより強固にするようにしてもよい。 Further, in the above-described embodiment, as the coupling means for directly coupling 70 between the opposed peripheral surfaces of the plate bosses 41b, 41b 'of the lamp plates 41, 41' and the boss portion 22b of the movable sheave 22, screwing means (screw fixing) However, in the present invention, various coupling methods other than screwing can be applied. For example, directly press-fitting between the opposed peripheral surfaces, or directly press-fitting a spline fitting portion after spline-fitting between the opposed peripheral surfaces, or adhering or welding the opposed peripheral surfaces. Or may be combined directly. Further, the concave and convex engaging portions that bite into the opposed peripheral surfaces may be formed by caulking the end surfaces of the plate bosses 41 b and 41 b ′ of the lamp plates 41 and 41 ′ and the boss portion 22 b of the movable sheave 22. . Further, the joint strength may be further strengthened by further crimping the end faces to those directly joined by screwing, press-fitting, spline press-fitting, adhesion or welding between the opposed peripheral surfaces.
　また第１実施形態では、プレートボス４１ｂのボス部２２ｂへの螺合緊締前（即ちプレートボス４１ｂのボス部２２ｂへの組付け前）に、プレートボス４１ｂの外周面に軸受２４のインナレース２４ｉを圧入その他の固着手段で固着するものを示したが、本発明では、プレートボス４１ｂの外周面に軸受２４のインナレース２４ｉを圧入せずに嵌合させ、嵌合位置の固定をプレートボス４１ｂのボス部２２ｂへの螺合緊締により行うようにしてもよい。 In the first embodiment, the inner race 24i of the bearing 24 is provided on the outer peripheral surface of the plate boss 41b before the plate boss 41b is screwed and fastened to the boss 22b (that is, before the plate boss 41b is assembled to the boss 22b). In the present invention, the inner race 24i of the bearing 24 is fitted to the outer peripheral surface of the plate boss 41b without being press-fitted, and the fitting position is fixed to the plate boss 41b. This may be performed by screwing and tightening to the boss portion 22b.
　また前記実施形態では、第１シフト機構Ｓ１のアクチュエータ５０が電動モータ５１を出力源とするものを例示したが、アクチュエータとしては、電動モータ以外の種々の電磁機器（例えばリニアソレノイド）を出力源とするアクチュエータを用いてもよい。 Moreover, in the said embodiment, although the actuator 50 of 1st shift mechanism S1 illustrated what used the electric motor 51 as an output source, as an actuator, various electromagnetic devices (for example, linear solenoid) other than an electric motor are used as an output source. You may use the actuator to do.
　また前記実施形態では、第１シフト機構Ｓ１のアクチュエータ５０が電動式のものを例示したが、アクチュエータとしては、油圧式のアクチュエータを用いてもよい。 In the above-described embodiment, the actuator 50 of the first shift mechanism S1 is exemplified as an electric type, but a hydraulic actuator may be used as the actuator.

Claims (5)

  1. 　回転軸（１１）に固定される固定シーブ（２１）と、前記回転軸（１１）を挿通させるボス部（２２ｂ）を有すると共に該回転軸（１１）に対し軸方向移動可能な可動シーブ（２２）と、前記固定シーブ（２１）及び前記可動シーブ（２２）に巻き掛けられるベルト（１４）と、前記ボス部（２２ｂ）に軸受（２４）を介して第１の軸方向駆動力を付与するアクチュエータ（５０）を有して前記可動シーブ（２２）を軸方向にシフトさせる第１シフト機構（Ｓ１）と、前記ボス部（２２ｂ）に第２の軸方向駆動力を付与する遠心機構（４０）を有して前記可動シーブ（２２）を軸方向にシフトさせる第２シフト機構（Ｓ２）とを備え、
    　前記遠心機構（４０）は、前記可動シーブ（２２）に固定されるランププレート（４１，４１′）と、前記ランププレート（４１，４１′）を挟んで前記軸受（２４）とは反対側に配置されて前記回転軸（１１）と一体に回転するカム部材（４２）と、前記ランププレート（４１，４１′）及び前記カム部材（４２）間に介装される遠心重錘（４３）とを有し、前記遠心重錘（４３）の遠心力を前記カム部材（４２）で前記第２の軸方向駆動力に変換して前記ランププレート（４１，４１′）に作用させるベルト式無段変速機において、
    　前記ランププレート（４１，４１′）は、前記ボス部（２２ｂ）を囲繞するプレートボス（４１ｂ，４１ｂ′）と、前記プレートボス（４１ｂ，４１ｂ′）から径方向外方へ張り出して前記カム部材（４２）との間で前記遠心重錘（４３）を保持するプレート本体部（４１ａ，４１ａ′）とを一体に有し、
    　前記ボス部（２２ｂ）と前記プレートボス（４１ｂ，４１ｂ′）との相対向する周面相互が直接結合（７０）されることを特徴とするベルト式無段変速機。     A movable sheave (22) having a fixed sheave (21) fixed to the rotating shaft (11) and a boss portion (22b) through which the rotating shaft (11) is inserted and movable in the axial direction relative to the rotating shaft (11). ), A belt (14) wound around the fixed sheave (21) and the movable sheave (22), and a first axial driving force to the boss portion (22b) via a bearing (24). A first shift mechanism (S1) having an actuator (50) for shifting the movable sheave (22) in the axial direction, and a centrifugal mechanism (40) for applying a second axial driving force to the boss portion (22b). And a second shift mechanism (S2) that shifts the movable sheave (22) in the axial direction.
    The centrifugal mechanism (40) has a lamp plate (41, 41 ') fixed to the movable sheave (22) and a side opposite to the bearing (24) across the lamp plate (41, 41'). A cam member (42) which is arranged and rotates integrally with the rotating shaft (11), and a centrifugal weight (43) interposed between the lamp plate (41, 41 ') and the cam member (42); A belt-type stepless converter that converts the centrifugal force of the centrifugal weight (43) into the second axial driving force by the cam member (42) and acts on the ramp plate (41, 41 '). In the transmission,
    The ramp plate (41, 41 ′) projects from the plate boss (41b, 41b ′) surrounding the boss portion (22b) and the plate boss (41b, 41b ′) radially outward to the cam member. (42) integrally having a plate body (41a, 41a ′) for holding the centrifugal weight (43),
    A belt type continuously variable transmission characterized in that the circumferential surfaces facing each other of the boss portion (22b) and the plate boss (41b, 41b ') are directly coupled (70).
  2. 　前記プレートボス（４１ｂ）の少なくとも一部と、前記軸受（２４）の少なくとも一部とが径方向で互いにオーバラップすることを特徴とする、請求項１に記載のベルト式無段変速機。 The belt-type continuously variable transmission according to claim 1, wherein at least a part of the plate boss (41b) and at least a part of the bearing (24) overlap each other in the radial direction.
  3. 　前記軸受（２４）を前記ランププレート（４１）を介して前記ボス部（２２ｂ）に支持させるべく、前記軸受（２４）の内周部（２４ｉ）が前記プレートボス（４１ｂ）に装着されることを特徴とする、請求項１又は２に記載のベルト式無段変速機。 An inner peripheral portion (24i) of the bearing (24) is mounted on the plate boss (41b) so that the bearing (24) is supported by the boss portion (22b) via the lamp plate (41). The belt-type continuously variable transmission according to claim 1 or 2, characterized in that.
  4. 　前記ボス部（２２ｂ）の外周面には、軸方向で前記遠心機構（４０）側を向く段部（２２ｂｓ）が形成されており、
    　前記ランププレート（４１，４１′）は、前記段部（２２ｂｓ）との間で前記軸受（２４）の内周部（２４ｉ）を軸方向に挟持する係止部（４１ａｓ，４１ａｓ′）を有することを特徴とする、請求項１～３の何れか１項に記載のベルト式無段変速機。     On the outer peripheral surface of the boss portion (22b), a step portion (22bs) facing the centrifugal mechanism (40) side in the axial direction is formed.
    The lamp plate (41, 41 ′) includes a locking portion (41as, 41as ′) that clamps the inner peripheral portion (24i) of the bearing (24) in the axial direction between the ramp plate (41bs). The belt-type continuously variable transmission according to any one of claims 1 to 3, wherein
  5. 　前記回転軸（１１）を車幅方向に配して車両に搭載される、請求項１～４の何れか１項に記載のベルト式無段変速機であって、
    　前記アクチュエータ（５０）は、少なくとも一部が前記ベルト（１４）よりも車幅方向外方側に配設されるアクチュエータ本体（５０ｍ）と、前記アクチュエータ本体（５０ｍ）から前記ベルト（１４）よりも車幅方向内方側に延出する出力部材（５０ａ）とを有していて、該出力部材（５０ａ）がシフトアーム（６０）を介して前記可動シーブ（２２）に前記第１の軸方向駆動力を出力可能であり、
    　前記シフトアーム（６０）は、前記軸受（２４）の外周部（２４ｏ）に固定される基部（６０ｂ）と、前記基部（６０ｂ）から前記可動シーブ（２２）の径方向外方側へ延出する中間部（６０ａ）と、前記中間部（６０ａ）から車幅方向内方側に延び且つ前記出力部材（５０ａ）が連結される先部（６０ｃ）とを一体に有し、
    　少なくとも前記ランププレート（４１，４１′）と前記カム部材（４２）とが軸方向で最接近したときに、前記シフトアーム（６０）の前記先部（６０ｃ）の少なくとも一部と、前記カム部材（４２）の少なくとも一部とが径方向で互いにオーバラップすることを特徴とするベルト式無段変速機。     The belt-type continuously variable transmission according to any one of claims 1 to 4, wherein the rotary shaft (11) is arranged in a vehicle width direction and is mounted on a vehicle.
    The actuator (50) includes at least a part of the actuator body (50m) disposed on the outer side in the vehicle width direction from the belt (14), and the actuator body (50m) to the belt (14). An output member (50a) extending inward in the vehicle width direction, and the output member (50a) is connected to the movable sheave (22) via the shift arm (60) in the first axial direction. Drive power can be output,
    The shift arm (60) includes a base (60b) fixed to the outer peripheral portion (24o) of the bearing (24), and extends from the base (60b) to the radially outer side of the movable sheave (22). An intermediate portion (60a), and a tip portion (60c) extending inward in the vehicle width direction from the intermediate portion (60a) and connected to the output member (50a),
    When at least the ramp plate (41, 41 ') and the cam member (42) are closest to each other in the axial direction, at least a part of the tip (60c) of the shift arm (60) and the cam member A belt type continuously variable transmission characterized in that at least a part of (42) overlaps each other in the radial direction.
PCT/JP2017/029909 2016-09-16 2017-08-22 Belt-type stepless transmission WO2018051741A1 (en)

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014055648A (en) * 2012-09-13 2014-03-27 Honda Motor Co Ltd V-belt type continuously variable transmission
JP2015172382A (en) * 2014-03-11 2015-10-01 武蔵精密工業株式会社 Belt continuously variable transmission

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014055648A (en) * 2012-09-13 2014-03-27 Honda Motor Co Ltd V-belt type continuously variable transmission
JP2015172382A (en) * 2014-03-11 2015-10-01 武蔵精密工業株式会社 Belt continuously variable transmission

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