JP2015129573A - belt-type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve problems in a conventional belt-type continuously variable transmission of a transport vehicle and the like, that as a motor shaft of an electric motor constituting a groove width adjustment mechanism of a variable pully, each of reduction shafts of a multistage gear reduction mechanism, and a pulley shaft of the variable pulley are disposed in parallel with each other in a state that shaft centers are not agreed with each other, the electric motor and the reduction gear are largely bulged in the direction at a right angle to the pulley shaft, which causes increase in size of the device.SOLUTION: A groove width adjustment device 43 includes an electric motor 44, a reduction gear 45 for decelerating motor power, and an expansion/contraction portion 46 for increasing and decreasing an interval between a pair of pulley halves 36A, 36B configuring a drive pulley 36 by deceleration power. The reduction gear 45 is constituted by a single axial gear mechanism configured by disposing external tooth bodies 59a, 59b and an internal tooth body 60 around a common reference axial line of an input shaft 56 and the internal tooth body 60, in adjacent to each other, and a motor shaft 44a of the electric motor 44 and a first pulley shaft 8 of the drive pulley 36 are disposed on the reference axial line 57.

Description

  The present invention includes a drive pulley provided on a first pulley shaft to which engine power from an engine is input, a driven pulley provided on a second pulley shaft from which the engine power is shifted and output, the driven pulley, A groove width adjusting mechanism for changing a groove width of the variable pulley, wherein at least one of the drive pulley and the driven pulley is a variable pulley whose groove width can be changed. More particularly, the present invention relates to a power transmission structure for operating the groove width adjusting mechanism.

Conventionally, in a belt-type continuously variable transmission mounted on a work vehicle such as a transport vehicle or a saddle-type traveling vehicle, a drive pulley driven by an engine and a transmission output shaft from the belt-type continuously variable transmission are provided. The V-belt is wound around the driven pulley and at least one of the two pulleys is made a variable pulley so that the groove width can be changed. (For example, see Patent Documents 1 and 2).
In any technique, the rotational power of the electric motor is transmitted from the gear type reduction gear to the movable pulley half of the pair of pulley halves constituting the variable pulley via the feed screw mechanism, and the movable By moving the pulley half in the axial direction to increase or decrease the distance from the fixed pulley half, the width of the groove formed between the two pulley halves is changed to change the pitch diameter of the V-belt and continuously variable transmission I can do it.

Japanese Patent No. 4531050 JP 2007-263230 A

However, in the groove width adjusting mechanism as described above, in order to increase the adjustment accuracy of the groove width, it is necessary to greatly reduce the rotational speed of the motor power from the electric motor. A multi-stage gear reduction mechanism using a reduction shaft and having a large reduction ratio is used. The plurality of reduction shafts of the multistage gear reduction mechanism, the motor shaft of the electric motor upstream of the reduction shaft, and the pulley shaft of the variable pulley downstream of the transmission shaft are all parallel to each other. It has an out-of-center arrangement.
Therefore, the electric motor and the speed reducer greatly swell in the direction perpendicular to the pulley shaft, that is, the longitudinal direction of the belt-type continuously variable transmission, and the belt-type continuously variable transmission becomes larger and the weight of the front and rear is increased. There was a problem that balance was easily lost. Furthermore, since the gear reduction mechanism is a multi-stage gear reduction mechanism, there are problems that the number of parts is large, the parts cost is increased, and the maintainability is poor.

The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described.
That is, in claim 1, a drive pulley provided on a first pulley shaft to which engine power from an engine is input, a driven pulley provided on a second pulley shaft from which the engine power is shifted and output, A driven pulley and a V belt wound between each groove of the drive pulley, wherein at least one of the drive pulley and the driven pulley is a variable pulley whose groove width can be changed, and a groove for changing the groove width of the variable pulley In the belt-type continuously variable transmission having a width adjusting mechanism, the groove width adjusting mechanism includes a motor, a speed reducer that decelerates motor power from the motor, and a pair of pulley halves constituting the variable pulley. And an expansion / contraction portion that increases or decreases the distance by the deceleration power from the reduction device, and the reduction device has a reduction gear around a common reference axis of the input shaft portion and the output shaft portion of the reduction device. Constituted by a single axis gear mechanism formed by closely arranged, to the reference axis, it is obtained by placing the pulley shaft of the motor shaft and the variable pulley of the motor.
According to a second aspect of the present invention, the speed reducer is accommodated in the extendable portion.
In Claim 3, the said expansion-contraction part is a feed screw mechanism which consists of a male screw member and a female screw member screwed together, and a slide member interlockingly connected to the moving side of the male screw member and the female screw member; The movable pulley half of the variable pulley is moved via the slide member.
According to a fourth aspect of the present invention, a male screw is screwed onto the outer periphery of the housing of the speed reduction device, and the housing is screwed into the female screw member, whereby the speed reduction device is accommodated in the telescopic portion.
In claim 5, the single-axis gear mechanism is an eccentric member having an input shaft portion that is not relatively rotatable around a reference axis with respect to the motor shaft, and a rotation center that is eccentric from the reference axis. An eccentric member that is not rotatable relative to the input shaft portion, an external tooth member that is supported by the eccentric member so as to be relatively rotatable, and an external tooth member having external teeth provided on an outer peripheral surface; An internal tooth member having an inner diameter larger than the outer diameter of the member, the internal tooth member engaging with the external tooth by a number of teeth different from the external tooth, and a reference axis line by the external tooth member A rotation component generation / extraction mechanism that generates and extracts the rotation component, and an output shaft that is rotationally driven around the reference axis by the rotation component generation / extraction mechanism.
7. The telescopic part according to claim 6, wherein the telescopic part is a feed screw mechanism composed of a male screw member and a female screw member that are screwed and rotated with each other, and a slide interlockingly connected to the moving side of the male screw member and the female screw member. A movable pulley half of the variable pulley is moved through the slide member, and a male screw is threaded on the outer periphery of the internal gear member of the reduction gear, and the internal gear member is The speed reducer is accommodated in the telescopic portion by being screwed into the female screw member as a member.

Since this invention was comprised as mentioned above, there exists an effect shown below.
That is, according to claim 1, after the reduction gears are arranged centrally around the input shaft portion or the output shaft portion to reduce the size of the reduction gear in the radial direction, the pulley shaft and the input / output shaft are arranged on the common reference axis. And the motor shaft can be connected in series, and the motor and the speed reducer can be prevented from bulging in a direction perpendicular to the reference axis, that is, in the longitudinal direction of the belt type continuously variable transmission. It is possible to reduce the size and improve the front / rear weight balance. Furthermore, compared with the case where the conventional multistage gear reduction mechanism is used, the number of parts of the reduction gear can be reduced, and the parts cost can be reduced and the maintainability can be improved.
According to claim 2, the speed reducer can also prevent the belt type continuously variable transmission from bulging in the axial direction of the reference axis, that is, the thickness direction of the belt type continuously variable transmission, thereby further reducing the size of the belt type continuously variable transmission. be able to.
According to claim 3, with a simple configuration, the rotational power output from the speed reducer can be converted into linear power, and the movable pulley half can be moved in the reference axial direction via the slide member. It is possible to improve the reliability of the expansion / contraction operation, reduce the cost of parts by reducing the number of parts, and improve the maintainability.
According to the fourth aspect of the present invention, the speed reducer can also prevent the belt type continuously variable transmission from bulging out in the reference axis direction, that is, the thickness direction of the belt type continuously variable transmission, thereby further miniaturizing the belt type continuously variable transmission. it can. Furthermore, the housing of the speed reducer can also be used as a male screw member, so that it is not necessary to provide a male screw member separately, and it is possible to further reduce the component cost and improve the maintainability by reducing the number of components. it can.
According to claim 5, the single axis gear mechanism can be configured by a hypocycloid type reduction mechanism using a hypocycloid gear, and is not only small in the radial direction but also has a simple structure and a sufficient reduction ratio. A speed reducer is obtained.
According to claim 6, with a simple configuration, the rotational power output from the speed reducer can be converted into linear power, and the movable pulley half can be moved in the reference axis direction via the slide member. It is possible to improve the reliability of the expansion / contraction operation, reduce the cost of parts by reducing the number of parts, and improve the maintainability. Further, the speed reducer can be prevented from bulging in the reference axis direction, that is, the thickness direction of the belt type continuously variable transmission, and the belt type continuously variable transmission can be further reduced in size. In addition, the internal gear member of the speed reducer can also be used as a male screw member, eliminating the need for a separate male screw member, further reducing the number of parts and improving maintainability. Can be planned.

It is a plane partial sectional view showing the whole transportation vehicle provided with the belt type continuously variable transmission concerning the present invention. It is also a plane skeleton diagram. FIG. 6 is a partial cross-sectional view of a plane around a drive pulley in which a groove width adjusting device 43 is disposed. Similarly, it is a partially enlarged view. It is a plane partial cross section similarly at the time of expansion-contraction part expansion | extension. It is a partial plane sectional view of the periphery of the drive pulley in which another groove width adjusting device 43A is arranged. It is a plane partial sectional view of an electric unit. It is a plane partial cross section figure of the drive pulley periphery which has arrange | positioned the groove width adjusting device 43B of another form.

Hereinafter, embodiments of the present invention will be described in detail.
The direction indicated by the arrow F in FIG. 1 is the forward direction of the transport vehicle 1 as a work vehicle, and the positions and directions of the members described below are based on this forward direction.

First, an axle drive unit 2 of a transport vehicle 1 equipped with a belt type continuously variable transmission 4 according to the present invention will be described with reference to FIGS.
The axle drive unit 2 connects the engine 3, the axle drive device 5 that supports and drives the axles 7 and 7 to which the left and right wheels 6 and 6 are fixed, and connects the axle drive device 5 and the engine 3. And a belt type continuously variable transmission 4 as a main transmission mechanism for shifting engine power from the engine 3 and inputting it to the axle drive device 5.

  In the axle drive device 5, the input shaft 42 connected to the right end of the second pulley shaft 9 of the belt type continuously variable transmission 4 is horizontally mounted in the front of the axle drive case 41. In addition, the centrifugal governor 11 that detects the rotational speed of the input shaft 42, the auxiliary transmission mechanism 12 that performs an auxiliary transmission in conjunction with the operation of an auxiliary transmission lever (not shown), and the differential gear that differentially connects the axles 7 and 7. The apparatus 13 etc. are accommodated.

  Among them, the centrifugal governor 11 is attached to the input shaft 42 and rotates outward according to the centrifugal force to detect the rotational speed of the input shaft 42, and the governor weight 14. The lifter 15 is moved in the axial direction in linkage with the rotation to the outside, and the lifter 15 is connected to the throttle valve of the engine 3 and an appropriate link mechanism via the governor fork 16, the governor shaft 17 and the like. Are linked by.

  Thus, the fuel injection amount of the engine 3 is adjusted according to the rotational speed of the input shaft 42, and the output from the engine 3 can be changed as the rotational speed of the input shaft 42 increases or decreases.

  Further, in the auxiliary transmission mechanism 12, the input shaft 42 constitutes a driving side, and the forward gear 18 and the reverse gear 19 are fixed to the input shaft 42 in order from the right so as not to be relatively rotatable. Yes. The transmission shaft 10 is horizontally mounted in parallel with the input shaft 42, and the forward driven gear 20 and the reverse driven gear 21 are loosely fitted to the transmission shaft 10 in order from the right. The forward driven gear 20 is meshed with the forward gear 18, and the reverse driven gear 21 is meshed with the reverse gear 19 via a reverse gear 22 provided in an freely rotatable manner in the axle drive case 41. Yes.

  Further, a clutch slider 23 is provided between the forward driven gear 20 and the reverse driven gear 21 on the transmission shaft 10 so as not to be relatively rotatable and to be axially slidable. It is slid and displaced, and is engaged with one of the forward driven gear 20 or the reverse driven gear 21 to selectively apply a forward or reverse rotation to the transmission shaft 10, or the forward driven gear 20 / reverse driven A neutral position where no power is transmitted can be obtained without engaging with any of the gears 21.

  The clutch slider 23 is linked to a sub-transmission lever via a fork shaft (not shown), whereby the clutch slider 23 is moved forward, reverse, or neutral by a tilting operation of the sub-transmission lever. To enable forward shift, reverse shift, and neutral sub-shifting.

  The differential gear device 13 includes a hollow differential case 25 supported in the axle drive device 5 so as to have the same rotational axis as the axles 7 and 7, and a ring gear 26 fixed to the outer peripheral surface of the differential case 25. A pinion shaft 27 that is arranged orthogonally to the axles 7 and 7 in the differential case 25 and rotates integrally with the differential case 25; and pinions 28 and 28 that are bevel gears rotatably disposed at both ends of the pinion shaft 27; It is constituted by differential side gears 29 and 29 which are bevel gears fixed to the inner end side of the axles 7 and 7 and meshed with the pinions 28 and 28.

  The ring gear 26 is meshed with an output gear 24 provided near the right end side of the transmission shaft 10, so that the auxiliary transmission power from the auxiliary transmission mechanism 12 is input to the differential gear device 13. Then, it is transmitted as differential power to the left and right axles 7.

  In addition, friction type disc brake devices 30 and 30 are disposed on the axles 7 and 7, respectively, and a braking force by a foot brake is applied to the axles 7 and 7 by operating a brake pedal (not shown). It can be granted.

Next, the belt type continuously variable transmission 4 will be described with reference to FIGS.
As shown in FIGS. 1 and 2, in the belt-type continuously variable transmission 4, a first pulley shaft 8 is connected to an engine output shaft 35 protruding leftward from the engine 3, and the first pulley shaft 8, a drive pulley 36 capable of changing the groove width is disposed, and a groove width adjusting device 43 according to the present invention is disposed on the left side of the drive pulley 36.

  The drive pulley 36 includes a fixed-side pulley half 36A that is fitted and fixed to the right portion of the first pulley shaft 8, and a movable-side pulley half that is movable in the axial direction on the first pulley shaft 8. 36B, and a groove 62 for winding the V-belt 38 is formed between the conical surfaces of the movable pulley half 36B and the fixed pulley half 36A facing each other.

  On the other hand, a driven pulley 37 whose groove width can be changed is disposed on the right half of the second pulley shaft 9, and a pulley case 39 in which a compression coil spring 40 and the like are accommodated is disposed on the left side of the driven pulley 37. Has been placed.

  The driven pulley 37 also includes a fixed pulley half 37A that is fitted and fixed to the right portion of the second pulley shaft 9, and a movable pulley half that is movable in the axial direction on the second pulley shaft 9. 37B, and a groove 31 for winding the V-belt 38 is formed between the conical surfaces of the movable pulley half 37B and the fixed pulley half 37A facing each other.

  In such a configuration, the movable pulley half 37 </ b> B is constantly urged toward the fixed pulley half 37 </ b> A by the compression coil spring 40, and the groove 62 of the drive pulley 36 and the groove 31 of the driven pulley 37. The driven pulley 37 is rotated in conjunction with the rotation of the V belt 38 wound therebetween.

  Further, as shown in FIG. 3, in the drive pulley 36, a shaft center hole 8a is drilled in the shaft center of the first pulley shaft 8 in which the stationary pulley half 36A is fitted and fixed to the right end. A tapered portion 35a at the left end of the engine output shaft 35 is inserted into the shaft hole 8a, and a lock nut 47 is screwed into the protruding end thereof. The stationary pulley half 36A is connected to the engine output shaft. It is fixed to 35 so that it does not move in the axial direction.

  On the other hand, the movable pulley half 36B is formed with a cylindrical boss portion through which the first pulley shaft 8 passes, and a cylindrical sleeve 49 is provided between the boss portion and the first pulley shaft 8. Is installed.

  The sleeve 49 is fitted to the outer periphery of the first pulley shaft 8 through a spline 49a, and the left and right end surfaces of the sleeve 49 are the right surface of the fixing ring 50 and the fixed pulley half 36A, respectively. The sleeve 49 is sandwiched by the left end surface so that the sleeve 49 can rotate integrally with the first pulley shaft 8.

  The movable pulley half 36B is externally fitted to the outer periphery of the sleeve 49 via the spline 36B1, so that the movable pulley half 36B can be moved in the axial direction. It can move in the axial direction while rotating integrally with the first pulley shaft 8.

  In the configuration as described above, when the movable pulley half 36B of the drive pulley 36 is moved by being pushed and pulled in the axial direction by the groove width adjusting device 43, the groove 62 is set to a predetermined groove width. The tension of the V belt 38 is changed, and the groove width of the groove 31 of the driven pulley 37 in which the space between the pulley halves 37A and 37B is always urged in the proximity direction by the compression coil spring 40 is also automatically changed. Thus, even if the moving length in the axial direction of the movable pulley half 36B is small, a large gear ratio can be obtained.

Next, a detailed configuration of the groove width adjusting device 43 will be described with reference to FIGS.
As shown in FIGS. 3 and 4, the groove width adjusting device 43 includes an electric motor 44, a speed reducing device 45 that decelerates the motor power from the electric motor 44, the fixed-side pulley half 36 </ b> A, and the movable-side pulley. An expansion / contraction section 46 is provided that adjusts the distance between the half bodies 36B by increasing / decreasing the deceleration power from the reduction gear 45.

  Of these, the electric motor 44 is housed in a motor case 55, and the motor case 55 is fastened and fixed to a pedestal 53 by a plurality of fixing bolts 54, and the pedestal 53 is a device of the belt type continuously variable transmission 4. The case 51 is fixed to the front left side surface by a plurality of fixing bolts 52.

  A motor shaft 44a extends rightward from the electric motor 44, penetrates into the device case 51 via the pedestal 53, and is connected to the input shaft 56 to the speed reducer 45 on a common reference axis 57. It is connected with.

  Thereby, the motor power of the electric motor 44 is input to the input shaft 56 of the reduction gear 45 from the motor shaft 44a as rotational power. In the embodiments described below, all electric motors are used. However, hydraulic motors that use hydraulic pressure as a drive source may be used. It is not limited.

  The speed reduction device 45 is constituted by a hypocycloid type speed reduction mechanism, and cannot rotate relative to the motor shaft 44a on the same axis as the motor shaft 44a positioned on the reference axis 57. A pair of eccentric members 58a and 58b having a rotational center that is eccentric from the input shaft 56 and the reference axis 57, and are not rotatable relative to the input shaft 56, and the eccentric members A pair of external tooth bodies 59a and 59b, which are externally rotatably mounted on 58a and 58b, and an inner diameter larger than the outer diameter of the external tooth bodies 59a and 59b, and a position covering the external tooth bodies 59a and 59b Rotating component generating / extracting mechanism 6 for generating and extracting a rotating component around the reference axis 57 of the cylindrical inner tooth body 60 and the outer tooth bodies 59a and 59b provided rotatably. If, the output shaft unit rotating around the reference axis 57 by the rotational component generated takeout mechanism 61, in the present embodiment and the internal toothed element 60 are provided.

  Each of the external tooth bodies 59a and 59b and the internal tooth body 60 is formed as a hypocycloid gear. The hypocycloid gear includes a normal involute gear and an arc gear.

  Of these, the input shaft 56 is separate from the motor shaft 44a in this embodiment, but may be integrally formed. The eccentric members 58a and 58b are formed in order from the left in a single eccentric body 58 provided on the reference axis 57, and each axis is displaced by a predetermined amount with respect to the reference axis 57. The eccentric members 58a and 58b can be eccentrically rotated according to the rotation of the input shaft 56 around the reference axis 57.

  The eccentric members 58a and 58b are displaced by 180 degrees in the rotational direction with respect to the reference axis 57, so that the eccentric torque associated with the rotation of the eccentric members 58a and 58b is offset, and the input shaft 56 Can be rotated stably around the reference axis 57.

  The external tooth bodies 59a and 59b are arranged corresponding to the eccentric members 58a and 58b, respectively. The external teeth 59a and 59b extend to the external teeth 63a and 63b provided on the outer peripheral surface in parallel with the reference axis 57 and are drilled at substantially the same position in the circumferential direction with reference to the reference axis 57. Cam holes 64a and 64b are provided, and a plurality of the cam holes 64a and 64b are formed around the reference axis 57 in each of the external tooth bodies 59a and 59b.

  The internal tooth body 60 is disposed on the same reference axis 57 as the external tooth bodies 59a and 59b. In the inner tooth body 60, inner teeth 60b that mesh with the outer teeth 63a and 63b are provided on the inner peripheral surface of a cylindrical main body 60a having an axis on the reference axis 57, The internal teeth 60b are set to have a different number of teeth from the external teeth 63a and 63b.

  The rotation component generation / extraction mechanism 61 includes the inner teeth 60b, left and right bearings 66 and 67 fitted to the inner peripheral surface of the main body 60a at the left and right positions sandwiching the inner teeth 60b, and the bearings 66 67 and the left and right disc-shaped supports 68 and 69 sandwiched between the eccentric members 58a and 58b and the external teeth 59a and 59b, respectively, and the reference in the left support 68. A fixed guide pin 70 slidably inserted into a guide hole 68b drilled in parallel to the axis 57 and the support bodies 68 and 69 are fastened, and a middle portion is inserted into both the cam holes 64a and 64b. And a connecting bolt 71.

  Boss holes 68a and 69a are formed in the left and right support bodies 68 and 69, respectively, and the eccentric body 58 is rotated through the left and right bearings 72 and 73 in the boss holes 68a and 69a. Both ends are supported as possible.

  Further, the left end of the fixed guide pin 70 slidable on the left support body 68 is inserted and fixed in the pin hole 53a of the pedestal 53, and the left and right support bodies 68 and 69 are connected to the both support bodies 68. -While the eccentric members 58a and 58b and the external tooth bodies 59a and 59b are sandwiched between 69, it is possible to move in the axial direction along the fixed guide pin 70 without relative rotation around the reference axis line 57. .

  In addition, the connecting bolt 71 has a smaller diameter than the cam holes 64a and 64b by an amount corresponding to the amount of eccentricity of the eccentric members 58a and 58b with respect to the reference axis 57. Here, as described above, since the plurality of cam holes 64a and 64b are formed in the outer tooth bodies 59a and 59b at substantially the same positions in the circumferential direction, the connecting bolt 71 is also provided with the support bodies 68 and 69. There are multiple intervening between them.

  In such a reduction gear 45, when the input shaft 56 rotates around the reference axis 57 by the rotational power from the electric motor 44, and the eccentric members 58a and 58b rotate eccentrically around the same reference axis 57, the external tooth body 59a and 59b also try to rotate eccentrically with respect to the reference axis 57 together with the eccentric members 58a and 58b. At this time, since the external teeth 63a and 63b are engaged with the internal teeth 60b, the external tooth bodies 59a and 59b are decelerated defined by the number of teeth of the external teeth 63a and 63b and the number of teeth of the internal teeth 60b. Attempts to rotate at a reduced speed.

  However, since both the supports 68 and 69 are set so as not to be relatively rotatable and slidable in the axial direction around the reference axis 57 as described above, the connection for fastening the two supports 68 and 69 is fastened. The external tooth bodies 59a and 59b through which the bolts 71 are inserted through the cam holes 64a and 64b also revolve without rotating, with the external teeth 63a and 63b meshing with the internal teeth 60b.

  On the other hand, since the internal tooth body 60 provided with the internal teeth 60b is provided so as to be relatively rotatable around the support bodies 68 and 69 via the bearings 66 and 67 as described above, the external tooth body 59a is provided. When 59b revolves, the internal teeth 60b are pushed in the revolving direction by the external teeth 63a and 63b of the external tooth bodies 59a and 59b, and the internal tooth body 60 rotates. In this way, the external tooth bodies 59a and 59b can generate and take out the revolution component around the reference axis 57, and can be output from the internal tooth body 60 of the speed reducer 45 as rotational power.

  The expansion / contraction part 46 includes a feed screw mechanism 75 that converts the rotational power output from the speed reducer 45 into linear power, and the linear power from the feed screw mechanism 75 to move the movable pulley half of the drive pulley 36. And a slider 76 that moves the movable pulley half 36 </ b> B in the axial direction of the reference axis 57.

  Of these, the feed screw mechanism 75 includes the internal tooth body 60 and a cylindrical female screw body 74 disposed concentrically around the internal tooth body 60, and the left end of the female screw body 74 is The base 53 is fastened and fixed by a plurality of fixing bolts 52.

  A male screw 60c is threaded on the outer peripheral surface of the inner tooth body 60. In the female screw body 74, an inner peripheral surface of a cylindrical main body 74a having an axis on the reference axis 57. A female screw 74b that meshes with the male screw 60c is threaded, and by inserting the male screw 60c into the female screw 74b, the internal tooth body 60 and the female screw body 74 are screwed together. It can be rotated together.

  The slider 76 includes a multi-stage cylindrical main body 76a having an axis on the reference axis 57, and a flange 76b having a diameter larger than the main body 76a. The right end of the flange 76b has a disc shape. Thus, it is connected to the left side of the movable pulley half 36B of the drive pulley 36 via a cylindrical connecting body 77 having an axis on the reference axis 57.

  The inner peripheral surface of the main body portion 76a is spline-coupled to the outer peripheral surface of the left half portion of the first pulley shaft 8 so as not to rotate relative to the axial direction and is slidable in the axial direction, and the outer peripheral surface of the main body portion 76a. Is provided on the inner peripheral surface of the right end portion of the internal tooth body 60 via a bearing 78 so as to be relatively rotatable.

  In such a stretchable part 46, when the inner tooth body 60 tries to rotate around the reference axis 57, the female screw body 74 side screwed to the inner tooth body 60 is fastened and fixed to the base 53. The inner tooth body 60 side moves in the axial direction while rotating around the reference axis 57.

  However, as described above, in the speed reducer 45, the two support bodies 68 and 69 have the shafts without relative rotation around the reference axis line 57 with the external tooth bodies 59a and 59b sandwiched therebetween. The internal tooth body 60 can be rotated relative to the support bodies 68 and 69 through the bearings 66 and 67 while sliding in the direction.

  Therefore, the internal tooth body 60 extends and contracts in the axial direction starting from the female screw body 74 while rotating around the reference axis 57 while the speed reducer 45 is housed in a non-rotating state. be able to. Thereby, the rotational power can be converted into the straight power, and the movable pulley half 36B can be moved in the axial direction of the reference axis 57 via the slider 76 provided with the connecting body 77.

  The connecting body 77 has a plurality of restricting holes 79 penetrating in the radial direction. A restricting bolt 48 protruding in the radial direction from the first pulley shaft 8 is inserted into the restricting hole 79. The restriction bolt 48 restricts the axial movement range of the connecting body 77 with respect to the first pulley shaft 8 so that the adjustment range of the groove width can be set to a predetermined range.

  In the configuration as described above, when the electric motor 44 is driven, rotational power is transmitted to the input shaft 56 via the motor shaft 44a, and the eccentric members 58a and 58b rotate eccentrically around the reference axis 57 in the reduction gear 45. Then, the external tooth bodies 59a and 59b revolve with the external teeth 63a and 63b meshing with the internal teeth 60b.

  Then, the internal tooth body 60 provided with the internal teeth 60 b rotates, and the male screw 60 c provided on the outer peripheral surface of the internal tooth body 60 in the extendable portion 46 is fixed to the base 53 by the female screw body 74. It rotates in the screw 74b, and the internal tooth body 60 expands and contracts in the axial direction from the female screw body 74.

  At this time, for example, as shown in FIGS. 3 and 5, when the internal tooth body 60 is extended from the position 80 to the position 81, the movable pulley half 36 </ b> B is also positioned on the first pulley shaft 8 in conjunction therewith. It moves from 133 to the position 134, the interval with the fixed pulley half 36A is reduced, the groove width is narrowed, and the pulley diameter of the drive pulley 36 is enlarged to increase the speed.

  That is, a drive pulley 36 provided on the first pulley shaft 8 to which engine power from the engine 3 is input, a driven pulley 37 provided on the second pulley shaft 9 from which the engine power is shifted and output, and the driven pulley A pulley 37 and a V-belt 38 wound between the grooves 62 and 31 of the drive pulley 36. In this embodiment, at least one of the drive pulley 36 and the driven pulley 37, both pulleys 36 and 37 have a groove width. In the belt-type continuously variable transmission 4 provided with a variable pulley, a variable pulley, a groove width adjusting device 43 which is a groove width adjusting mechanism for changing the groove width of the driving pulley 36 in this embodiment, the groove width The adjustment device 43 includes an electric motor 44 that is a motor, a speed reduction device 45 that decelerates the motor power from the electric motor 44, and a pair of pulley halves 36A and 36A constituting the drive pulley 36. 6B is provided with an expansion / contraction section 46 that increases / decreases the interval between 6B by the deceleration power from the reduction gear 45, and the reduction gear 45 is an input shaft 56 that is an input shaft portion of the reduction gear 45 and an output shaft portion. Around the common reference axis 57 of the internal tooth body 60, it is constituted by a single axis gear mechanism in which the external tooth bodies 59a and 59b as the reduction gears and the internal tooth body 60 are arranged close to each other, and on the reference axis line 57, Since the motor shaft 44a of the electric motor 44 and the first pulley shaft 8 which is the pulley shaft of the drive pulley 36 are arranged, the external tooth body is provided around the input shaft portion or the output shaft portion, in this embodiment around the input shaft 56. 59a and 59b and the internal tooth body 60 are arranged in a concentrated manner to reduce the size of the reduction gear 45 in the radial direction, and then the first pulley shaft 8, the input shaft 56, the internal tooth body 60, And connecting the motor shaft 44a continuously Thus, the electric motor 44 and the speed reducer 45 are prevented from bulging in the direction perpendicular to the reference axis 57, that is, in the longitudinal direction of the belt type continuously variable transmission 4, in this embodiment, the belt type continuously variable transmission. It is possible to reduce the size of the device 4 and improve the front / rear weight balance. Furthermore, compared with the case where the conventional multistage gear reduction mechanism is used, the number of parts of the reduction gear 45 can be reduced, and the part cost can be reduced and the maintainability can be improved.

  Further, since the speed reducer 45 is accommodated in the telescopic part 46, the speed reducer 45 is in the axial direction of the reference axis 57, that is, in the thickness direction of the belt-type continuously variable transmission 4, in the left-right direction in this embodiment. The belt type continuously variable transmission 4 can be further reduced in size.

  In addition, the expansion / contraction portion 46 includes a feed screw mechanism 75 including an internal tooth body 60 that is a male screw member and a female screw body 74 that is a female screw member, and the internal tooth body 60 and the female screw body. 74, a slider 76 that is a slide member that is interlocked and connected to the internal tooth body 60 in this embodiment, and a movable pulley half of the drive pulley 36 that is the variable pulley via the slider 76. 36B is moved, the rotational power output from the reduction gear 45 is converted into linear power with a simple configuration, and the movable pulley half 36B is moved in the axial direction of the reference axis 57 via the slider 76. Thus, the reliability of the expansion / contraction operation in the expansion / contraction part 46 can be improved, the cost of parts can be reduced and the maintainability can be improved by reducing the number of parts.

  Then, a male screw 60c is threaded on the outer periphery of the housing of the reduction gear 45, in this embodiment, the internal tooth body 60, and the internal tooth body 60 is screwed into the female screw body 74 which is the female screw member. Thus, the speed reducer 45 is accommodated in the telescopic part 46, so that the speed reducer 45 moves in the axial direction of the reference axis 57, that is, in the thickness direction of the belt-type continuously variable transmission 4, in this embodiment, in the left-right direction. Swelling can also be prevented, and the belt-type continuously variable transmission 4 can be further reduced in size. Further, the internal gear 60 of the speed reducer 45 can be used also as a male screw member, so that it is not necessary to provide a male screw member separately, and the number of parts is further reduced, thereby further reducing the parts cost and improving the maintainability. Can be achieved.

  Further, the single axis gear mechanism includes an input shaft 56 that is an input shaft portion that cannot rotate relative to the motor shaft 44 a around the reference axis 57, and an eccentric member that has a rotation center that is eccentric from the reference axis 57. 58a and 58b, which are eccentric members 58a and 58b which are not rotatable relative to the input shaft 56, and external tooth bodies 59a and 59b which are external teeth members which are supported by the eccentric members 58a and 58b so as to be relatively rotatable. An external tooth body 59a and 59b having external teeth 63a and 63b provided on the outer peripheral surface, and an internal tooth body 60 that is an internal tooth member having an inner diameter larger than the outer diameter of the external tooth bodies 59a and 59b. The internal teeth 60b meshing with the external teeth 63a and 63b are provided with the number of teeth different from that of the external teeth 63a and 63b, and the rotational components around the reference axis 57 by the external teeth 59a and 59b. Produces Since the rotation component generation / extraction mechanism 61 to be taken out and the output shaft portion that is rotationally driven around the reference axis 57 by the rotation component generation / extraction mechanism 61, in this embodiment, the internal tooth body 60, the single axis gear The mechanism can be constituted by a hypocycloid type reduction mechanism using a hypocycloid gear, and a reduction device 45 that is not only small in the radial direction but also has a simple structure and a sufficient reduction ratio can be obtained.

  In addition, the expansion / contraction part 46 includes a feed screw mechanism 75 including an internal tooth body 60 that is a male screw member that is screwed together and a female screw body 74 that is a female screw member, and the internal tooth body 60. And a slider 76 that is a slide member that is interlocked and connected to the internal tooth body 60 that is the moving side of the female screw body 74, and the movable pulley half of the drive pulley 36 that is the variable pulley via the slider 76. 36B is moved, and a male screw 60c is threaded on the outer periphery of the internal tooth body 60 which is an internal tooth member of the reduction gear 45, and the internal tooth body 60 is screwed into the female screw body 74 as a male screw member. By doing so, the speed reduction device 45 is accommodated in the expansion / contraction portion 46, so that the rotational power output from the speed reduction device 45 is converted into linear power with a simple configuration, and the movable pulley half body via the slider 76 is converted. 36B is the axial direction of the reference axis 57 Can be moved to the reliability improvement of the stretching operation in the stretchable portion 46, it is possible to reduce increase of parts cost reduction and maintenance due to parts. Further, the speed reducer 45 can be prevented from bulging in the axial direction of the reference axis 57, that is, in the thickness direction of the belt type continuously variable transmission 4, in this embodiment, the belt type continuously variable transmission. The device 4 can be further reduced in size. In addition, the internal tooth body 60 of the speed reducer 45 can be used also as a male screw member, so that it is not necessary to provide a male screw member separately. Improvements can be made.

Next, another embodiment of the groove width adjusting device 43 will be described with reference to FIGS.
In the groove width adjusting device 43A shown in FIGS. 6 and 7, the electric motor 83, the speed reducer 84, and the expansion / contraction portion 85 are arranged on a common reference axis 57A as in the groove width adjusting device 43. Unlike the groove width adjusting device 43, the speed reducer 84 is integrated with the electric motor 83 without being housed in the expansion / contraction part 85, thereby improving the ease of assembly and maintenance. It is.

The electric unit 86 is configured by housing an electric motor 83 and a speed reducer 84 connected in the axial direction in a unit case 87.
In the electric motor 83, an annular stator 88 having a plurality of armature windings arranged annularly in parallel is fixed to the inner peripheral surface of the left part of the unit case 87, and the rotor 89 is disposed in the stator 88. Has been. An annular permanent magnet 90 is fixed to the outer peripheral surface of the rotor 89, and the permanent magnet 90 is disposed opposite to the inner peripheral surface of the stator 88 with a predetermined gap.

  Further, the rotor 89 is fixed on a motor shaft 92 located on a common reference axis 57A with the output shaft 91 of the speed reducer 84 so as to be integrally rotatable with the motor shaft 92. The motor shaft 92 is pivotally supported by a bearing 93 provided in a partition wall 87a that partitions the electric motor 83 and the speed reducer 84 in the unit case 87 to the left and right, and is an input shaft to the speed reducer 84. The motor power of the electric motor 83 is input from the motor shaft 92 into the speed reducer 84 as rotational power.

  Similar to the speed reduction device 45, the speed reduction device 84 is configured by a hypocycloid type speed reduction mechanism, and the axis line with respect to the motor shaft 92 is on the same axis line as the motor shaft 92 positioned on the reference axis line 57A. Eccentric members 95a and 95b having an input shaft 94 that cannot rotate relative to each other and a rotation center that is eccentric from the reference axis 57A, and each of the eccentric members 95a and 95b that cannot rotate relative to the input shaft 94. A pair of external teeth bodies 96a and 96b which are externally rotatably mounted on the eccentric members 95a and 95b, and have an inner diameter larger than the outer diameter of the external teeth bodies 96a and 96b. A rotation component around the reference axis 57A is generated by a cylindrical inner tooth body 104 provided so as not to rotate at a position covering 96b and the outer tooth bodies 96a and 96b. And for rotation component generating takeout mechanism 97, an output shaft 98 for rotation about the reference axis 57A is provided by the rotational component generated takeout mechanism 97.

  Of these, the input shaft 94 is the same as the input shaft 56. However, unlike the eccentric members 58a and 58b, the eccentric members 95a and 95b are formed separately from each other, and are arranged in parallel from the left along the axial direction of the reference axis 57A. The input shaft 94 is externally fitted and fixed so as to be displaced by a predetermined amount with respect to the axis 57A, and the eccentric members 95a and 95b can be eccentrically rotated according to the rotation of the input shaft 94 around the reference axis 57A. I have to.

  The eccentric members 95a and 95b are also displaced by 180 degrees in the rotational direction with respect to the reference axis 57A, so that the eccentric torque accompanying the rotation of the eccentric members 95a and 95b is offset.

  Similarly to the external tooth bodies 59a and 59b, the external tooth bodies 96a and 96b also have external teeth 100a and 100b provided on the outer peripheral surface, and a plurality of cam holes 99a and 99b around the reference axis 57A, respectively. 99b. However, unlike the internal tooth body 60, the internal tooth body 104 is a cylindrical body that is incorporated and fixed in a portion covering the outer periphery of the external tooth bodies 96a and 96b with the unit case 87, and is formed on the inner peripheral surface thereof. The internal teeth 104a meshing with the external teeth 100a and 100b are provided, and the internal teeth 104a are set to have a different number of teeth from the external teeth 100a and 100b.

  The rotation component generation / extraction mechanism 97 supports the inner teeth 104a, the inner teeth body 104, the cam holes 99a and 99b, the carrier pins 101 that pass through both the cam holes 99a and 99b, and the carrier pins 101 and the reference. The flange portion 102 is configured to freely rotate around the axis 57A. The external teeth 96a and 96b are caused to generate and take out revolution components around the reference axis 57A so that they can be output from the output shaft 91.

  Of these, unlike the speed reducer 45, the carrier pin 101 is supported by the relatively rotatable flange portion 102 as described above, and the external tooth bodies 96a and 96b can freely rotate around the reference axis 57A. The internal teeth 104a meshing with the external teeth 100a and 100b of the external teeth bodies 96a and 96b are provided on the internal teeth body 104 constituting a part of the unit case 87.

  Therefore, the external teeth 96 a and 96 b can revolve while rotating, with the external teeth 100 a and 100 b meshing with the internal teeth 104 a of the internal teeth 104.

  The output shaft portion 98 includes the carrier pin 101, a flange portion 102, and the output shaft 91 that rotates around the reference axis 57A together with the flange portion 102.

  Of these, the carrier pin 101 is formed to have a smaller diameter than the cam holes 99a and 99b by an amount corresponding to the eccentric amount of the eccentric members 95a and 95b with respect to the reference axis 57A, similarly to the connecting bolt 71. Further, the output shaft 91 and the flange portion 102 that supports the carrier pin 101 and is formed by expanding the left end portion of the output shaft 91 are respectively connected to the unit case 87 via bearings 103 and 106. Is supported on the inner peripheral surface thereof so as to be relatively rotatable.

  In such a reduction gear 84, when the input shaft 94 rotates around the reference axis 57A by the rotational power from the electric motor 83 and the eccentric members 95a and 95b rotate eccentrically around the reference axis 57A, the external tooth body 96a. 96b also rotates eccentrically with respect to the reference axis 57A together with the eccentric members 95a and 95b. At the same time, since the external teeth 100a and 100b are meshed with the internal teeth 104a, the external teeth bodies 96a and 96b have a reduction ratio defined by the number of teeth of the external teeth 100a and 100b and the number of teeth of the internal teeth 104a. It is decelerated and rotated.

  When the external tooth bodies 96a and 96b are decelerated eccentrically in this way, the carrier pin 101 revolves around the reference axis 57A while rolling on the inner peripheral surfaces of the cam holes 99a and 99b. The output shaft 91 is rotated by the revolution force around the reference axis 57 </ b> A, and the rotational power is output from the electric unit 86.

  The expansion / contraction section 85 includes a feed screw mechanism 107 that converts the rotational power output from the electric unit 86 into linear power, and the straight-side power from the feed screw mechanism 107 to the movable pulley half 136A of the drive pulley 136. The slider 108 and the feed screw mechanism 107 are accommodated in a drive case 109 provided on the left side of the drive pulley 136. In the groove width adjusting device 43A of this embodiment, contrary to the case of the groove width adjusting device 43, the movable pulley half 136A is on the engine 3 side (right side) and the fixed pulley half is on the opposite side of the engine 3. The body 136B is used.

  The feed screw mechanism 107 includes a cylindrical male screw body 111 concentrically disposed around a bottomed cylindrical drive body 110 having an axis on the reference axis 57A, and the male screw body 111. And a cylindrical female screw body 112 disposed concentrically around the inner periphery of the screw.

  Here, the drive case 109 is formed so as to cover a disc-shaped support plate 109b centering on the reference axis 57A from the left side with an arm-shaped lid 109a. The driving body 110 is rotatably inserted into the left opening. The right end of the output shaft 91 is connected to the center of the bottom plate of the left end of the driving body 110 in the side view, and the left end of the first pulley shaft 8A is connected to the bearing 113 in the right opening of the driving body 110. It is inserted so as to be rotatable relative to each other.

  Furthermore, the inner peripheral surface of the left half portion of the male screw body 111 is spline fitted to the outer peripheral surface of the driving body 110 so as not to move in the axial direction, and the outer peripheral surface of the male screw body 111 is A male thread 111a is threaded. In the female screw body 112, a female screw 112b is threaded on the inner peripheral surface of a cylindrical main body 112a having an axis on the reference axis 57A, and the male screw 111a is inserted into the female screw 112b. By screwing, the male screw body 111 and the female screw body 112 can be screwed together.

  The slider 108 includes a multi-stage cylindrical main body portion 108a having an axis on the reference axis 57A, and a flange portion 108b having a diameter larger than that of the main body portion 108a. The right end of the flange portion 108b has a disc shape. Thus, it is connected to the left side of the movable pulley half 136A of the drive pulley 136 via a cylindrical connecting body 114 having an axis on the reference axis 57A.

  The inner peripheral surface of the main body portion 108a is spline-coupled to the outer peripheral surface of the left half portion of the first pulley shaft 8A so as not to rotate relative to the axial direction and to freely slide in the axial direction, and the outer peripheral surface of the main body portion 108a. Is installed in the inner peripheral surface of the mounting ring 125 fixed to the right end of the female screw body 112 via a bearing 116 so as to be relatively rotatable.

  The mounting ring 125 is fastened to a bottom plate portion 115a of a bottomed cylindrical guide body 115 having an axial center on a reference axis 57A and opened to the left. The guide body 115 is a support plate in the drive case 109. It is inserted in a through hole 109b1 passing through the axis of 109b so as to be axially slidable.

  Therefore, when the male screw body 111 is rotated by the rotation of the driving body 110 connected to the output shaft 91 in the extendable / contracting portion 85, the female screw body 112 screwed to the male screw body 111 is Without rotating around the reference axis 57A, the guide body 115 guides the guide body 115 to expand and contract in the axial direction. Thereby, rotational power can be converted into straight power, and the movable pulley half 136A can be moved in the direction of the reference axis 57A via the slider 108 provided with the connecting body 114.

  In the configuration as described above, when the electric motor 83 is driven and the motor power is decelerated by the reduction gear 84 and then output from the output shaft 91, it is combined with the driving body 110 connected to the output shaft 91. The male threaded body 111 rotates, the female threaded body 112 expands and contracts in the axial direction starting from the male threaded body 111 in the expansion / contraction section 85, and the movable pulley half 136A moves in the direction of the reference axis 57A to move the pulley half The distance of the groove 118 between 136A and 136B can be adjusted.

  In the groove width adjusting device 43B shown in FIG. 8, unlike the groove width adjusting devices 43 and 43A, the electric motor 83 and the speed reducer 84 are on the first reference axis 129, and the telescopic portion 119 is on the second reference axis 130. By using the electric unit 86 that is arranged on different reference axes, but in which the electric motor 83 and the speed reduction device 84 are connected in the axial direction, the electric motor 83, the speed reduction device 84, and the expansion / contraction portion as in the conventional case are used. Compared with the case where all of 119 are parallel to each other and arranged with the axis shifted, the swelling from the belt type continuously variable transmission 4 is reduced.

  The electric unit 86 is fixed to the left side surface of the front part of the drive case 128 provided on the left side of the drive pulley 136. The drive case 128 is formed so as to cover the right disk-shaped support plate 128b from the left side with an arm-shaped lid 128a, and is connected to the output shaft 91 coaxially. 131 penetrates through the lid 128a and enters the case, and its tip is rotatably supported by a support recess 128b1 provided in the support plate 128b. A small-diameter gear 126 is integrally formed on the drive shaft 131 that is supported at both ends in the drive case 128 in this way.

  The telescopic part 119 transmits the rotational power output from the electric unit 86 to linear power, and the linear power from the feed screw mechanism 120 is transmitted to the movable pulley half 136A. The slider 121 is moved in the direction of the second reference axis 130, and the slider 121 and the feed screw mechanism 120 are accommodated in the rear portion of the drive case 128. In the groove width adjusting device 43B of this embodiment, the engine 3 side (right side) is the movable pulley half 136A and the opposite side of the engine 3 is the fixed pulley half 136B, as in the groove width adjusting device 43A. Yes.

  The feed screw mechanism 120 includes a cylindrical male screw body 123 concentrically disposed around a cylindrical support body 132 having an axis on the second reference axis 130, and the male screw body 123. And a cylindrical female screw body 124 arranged concentrically around the left and right ends of the female screw body 124 is fixed to the left side wall of the lid body 128a.

  The left end of the support body 132 is also inserted and fixed in the left opening of the lid body 128a, and the left end of the first pulley shaft 8A is connected to the right opening of the support body 132 via a bearing 113. It is inserted so as to be relatively rotatable.

  Further, the inner peripheral surface of the left half of the male screw body 123 is externally fitted to the outer peripheral surface of the support 132 so as to be relatively rotatable, and the male screw 123 a is provided on the outer peripheral surface of the male screw body 123. It is threaded. In the female screw body 124, a female screw 124b is threaded on the inner peripheral surface of a cylindrical main body 124a having an axis on the second reference axis 130, and the male screw 124b is in the male screw 124b. By screwing in 123a, the male screw body 123 and the female screw body 124 can be screwed together.

  The slider 121 includes a multistage cylindrical main body 121a having an axis on the second reference axis 130, and a flange 121b. The right end of the flange 121b has an axis on the second reference axis 130. Is connected to the left side of the movable pulley half 136A of the drive pulley 136 through a cylindrical connecting body 114 having

  The inner peripheral surface of the main body 121a is spline-coupled to the outer peripheral surface of the left half portion of the first pulley shaft 8A so as not to rotate relative to the axial direction and to freely slide in the axial direction, and the outer peripheral surface of the main body 121a. Is provided on the inner peripheral surface of the right end portion of the male screw body 123 via a bearing 116 so as to be relatively rotatable.

  The male screw body 123 is fixed to the bottom plate portion 115a of the guide body 115 having an axis on the second reference axis 130, and the guide body 115 passes through the axis of the support plate 128b in the drive case 128. In the through hole 128b2, it is inserted so as to be axially slidable and relatively rotatable.

  Further, a large diameter gear 127 having an axis on the second reference axis 130 is fastened and fixed to the left end of the guide body 115, and the large diameter gear 127 meshes with a small diameter gear 126 formed on the drive shaft 131. Thus, the rotational power of the drive shaft 131 is transmitted to the guide body 115 via the reduction gear train 122 including the small diameter gear 126 and the large diameter gear 127.

  Accordingly, when the male screw body 123 is rotated through the guide body 115 by the rotation of the drive shaft 131 connected to the output shaft 91 in such an extendable / contracting portion 119, as described above, Since the female screw body 124 to be screwed is fixed to the drive case 128, the male screw body 123 expands and contracts in the axial direction while rotating around the second reference axis 130 together with the guide body 115. . As a result, the rotational power can be converted into straight power, and the movable pulley half 136A can be moved in the axial direction of the second reference axis 130 via the slider 121 provided with the connecting body 114.

  In the configuration as described above, when the electric motor 83 is driven and the motor power is decelerated by the reduction gear 84 and then output from the output shaft 91, the drive shaft 131 and the reduction gear train 122 are connected to the output shaft 91. The male threaded body 123 rotates together with the guide body 115 connected via the movable body, and the male threaded body 123 expands and contracts in the axial direction starting from the female threaded body 124 at the expansion / contraction portion 119, thereby moving the movable pulley half 136A. Can be moved in the direction of the second reference axis 130 to adjust the spacing of the groove 118 between the pulley halves 136A and 136B.

  The present invention includes a drive pulley provided on a first pulley shaft to which engine power from an engine is input, a driven pulley provided on a second pulley shaft from which the engine power is shifted and output, the driven pulley, And a V-belt wound between each groove of the driving pulley, and at least one of the driving pulley and the driven pulley is a variable pulley whose groove width can be changed, and a groove width adjusting mechanism for changing the groove width of the variable pulley. It can be applied to all belt-type continuously variable transmissions provided.

3 Engine 4 Belt type continuously variable transmission 8 · 8A First pulley shaft 9 Second pulley shaft 31 · 62 · 118 Groove 36 · 136 Drive pulley (variable pulley)
36A / 136B Fixed pulley half 36B / 136A Movable pulley half 37 Driven pulley 38 V belt 43 / 43A Groove width adjusting device (groove width adjusting mechanism)
44 ・ 133 Electric motor (motor)
44a / 92 Motor shaft 45/84 Deceleration device 46/85 Telescopic part 56/94 Input shaft (input shaft part)
57 / 57A Reference axis 58a / 58b / 95a / 95b Eccentric member 59a / 59b / 96a / 96b External tooth body (external tooth member / reduction gear)
60 Internal teeth (output shaft, internal teeth, reduction gear, male screw)
60b / 104a Inner teeth 60c / 111a Male screw 61 Rotation component generating / extracting mechanism 63a / 63b External teeth 74/112 Female screw body (female screw member)
75/107 Feed screw mechanism 76/108 Slider
98 Output shaft 104 Internal tooth body (Internal tooth member, reduction gear)
111 Male thread body (Male thread member)

Claims (6)

  A drive pulley provided on a first pulley shaft to which engine power from the engine is input, a driven pulley provided on a second pulley shaft from which the engine power is shifted and output, and each of the driven pulley and the drive pulley A belt type provided with a V-belt wound between grooves, at least one of the driving pulley and the driven pulley as a variable pulley whose groove width can be changed, and a groove width adjusting mechanism for changing the groove width of the variable pulley In the continuously variable transmission, the groove width adjusting mechanism includes a motor, a speed reducer that decelerates the motor power from the motor, and a distance between a pair of pulley halves constituting the variable pulley from the speed reducer. A single axis gear comprising an expansion / contraction portion that is increased / decreased by deceleration power, and wherein the reduction gear is disposed in the vicinity of a common reference axis of the input shaft portion and the output shaft portion of the reduction gear. Constituted by structure, to the reference axis, the belt-type continuously variable transmission, characterized in that a pulley shaft of the motor shaft and the variable pulley of the motor.   The belt-type continuously variable transmission according to claim 1, wherein the reduction gear is housed in the telescopic portion.   The extendable portion includes a feed screw mechanism including a male screw member and a female screw member that are screwed to each other, and a slide member that is interlocked and connected to the moving side of the male screw member and the female screw member. 2. The belt-type continuously variable transmission according to claim 1, wherein the movable pulley half of the variable pulley is moved via a belt.   The said reduction gear is accommodated in an expansion-contraction part by screwing a male screw in the outer periphery of the housing of the said reduction gear, and screwing this housing in the said female screw member. Belt type continuously variable transmission.   The single-axis gear mechanism is an eccentric member having an input shaft portion that is not rotatable relative to the motor shaft around a reference axis, and a rotation center that is eccentric from the reference axis, and with respect to the input shaft portion. An eccentric member that is relatively non-rotatable, an external tooth member that is supported by the eccentric member so as to be relatively rotatable, an external tooth member having external teeth on the outer peripheral surface, and an outer diameter that is larger than the outer diameter of the external tooth member An internal tooth member having an inner diameter, in which internal teeth meshing with the external teeth are provided by a number of teeth different from the external teeth, and a rotational component around a reference axis is generated by the external tooth member. The belt-type continuously variable transmission according to claim 1, further comprising: a rotation component generation / extraction mechanism that is extracted and an output shaft that is rotationally driven around the reference axis by the rotation component generation / extraction mechanism.   The extendable portion includes a feed screw mechanism including a male screw member and a female screw member that are screwed and rotated with each other, and a slide member that is interlocked and connected to the moving side of the male screw member and the female screw member, The movable pulley half of the variable pulley is moved through a slide member, and a male screw is threaded on the outer periphery of the internal gear member of the speed reducer, and the female screw member is used as a male screw member. 6. The belt-type continuously variable transmission according to claim 5, wherein the speed reducer is accommodated in the telescopic portion by being screwed into the belt.

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