JPS58102854A - V-belt type stepless change gear - Google Patents

Abstract

PURPOSE:To prevent the V-belt from being applied with an excessive shocking load upon starting and prolong the life of the V-belt by a method wherein the V-belt is applied with a pre-tension while a hydraulic operating device is not yet operated and remove the slackening of the V-belt by the pre-tension. CONSTITUTION:The change gear Tm consists of principal elements such as a driving V-pulley 40, a floowing V-pulley 41 and the V-belt 42 suspended between both of the V-pulleys. The driving and following pulleys are equipped with half bodies 47, 59 of the movable pulleys, and they are operated by the hydraulic operating devices Hy1, H62 respectively. The hydraulic cylinders 50, 62 of the hydraulic operating device are equipped with springs 53, 67, energizing the half bodies 47, 59 of the movable pulleys toward advancing directions or the directions in which the effective radii thereof are expanded respectively. These springs give the pretension to the v-belt 42 and function to remove the slackening thereof while a hydraulic pressure is not yet introduced into each hydraulic cylinders 50, 62.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a driving r pulley and a driven r pulley each having movable pulley halves whose effective radius can be adjusted by axial movement.
The present invention relates to a V-belt type continuously variable transmission in which a V-belt is stretched between the pulleys, and the driving and driven V-boots are provided with hydraulic actuators that move the respective movable pulley halves.

In this type of continuously variable transmission, when both hydraulic actuators are not in operation, there is a risk that the r-belts may loosen due to their own weight, moving the movable pulley half in a direction that reduces the effective radius. If the V-belt is slack in this way, an excessive impact load will be applied to the V-belt when the vehicle is started, which will shorten its lifespan.

In view of the above, the present invention provides the V-belt type continuously variable transmission, which applies pre-tension to the V-belt when both hydraulic actuation devices are not in operation, thereby eliminating slack in the V-belt and prolonging its life. The purpose is to provide a machine.

Hereinafter, an embodiment in which the present invention is applied to a motorcycle will be described with reference to the drawings. First, in FIG. It consists of a T711L and a gear type auxiliary transmission Tα, and these are constructed in a casing C supported by a vehicle body (not shown).

As shown in FIG. 2, the casing C includes a main case C1 that accommodates the crank part of the crankshaft 1 of the engine E and the auxiliary transmission Tα, an auxiliary case C3 that accommodates the continuously variable transmission 7'711, and its auxiliary case C1. It is divided into a cover C8 that closes the outer surface of the case C7.

In addition, the crankshaft 1 and other various rotating shafts in the power unit pu are all arranged parallel to the axis of the rear wheel Wr that is supported by the vehicle body (not shown) behind the power unit Pμ, and the output shaft of the power unit Pμ, that is, the auxiliary gear shift The output 4#U141 of the machine Tα is transmitted to the rear wheel Wr via the chain transmission device M.
It is designed to drive.

Both the starting clutch Sc and the continuously variable transmission TrK are hydraulically operated. In order to supply hydraulic oil to them, a control oil passage Lc extending from the clutch valve Vc is connected to the starting clutch Sc and a hydraulic pump P driven by the engine E.
The first extension extended from. The second oil supply paths L1, L are connected to the driving and driven parts of the continuously variable transmission TrIL, respectively.

In FIG. 5, Vr is a relief valve of the hydraulic pump P, and R is an oil reservoir formed at the bottom of the casing C.

The configuration of each part of the power unit Pμ will be sequentially explained with reference to FIG. 2.3.

First, there is the starting clutch Sc, which is connected to the crankshaft 1.
It is provided on the crankshaft 1 adjacent to the outside of the oldest bearing 2 that supports the crankshaft. This starting clutch SC has a clutch outer 4 connected to the crankshaft IK spline 3, and a clutch inner 5 integrally formed with a fixed pulley half 44 of a drive r pulley 4°, which will be described later. Between 4 and 5 are a plurality of drive friction plates 6 which are slidably spline fitted to the clutch outer 4;
A plurality of driven friction plates 7 are slidably spline-fitted to the clutch inch 5 and are interposed by alternately overlapping each other, and restrain the outward movement of the driving friction plate 6 at the outermost position. The pressure receiving ring 8 is locked to the clutch outer 4. A hydraulic cylinder 9 is formed in the clutch outer 4 on the opposite side from the pressure receiving ring 8, and this cylinder 9 has a piston 11 facing the drive friction plate 6 at the innermost position with a disc-shaped buffer spring 10 sandwiched therebetween. It is rubbed together. This piston 11 is urged backward by a return spring 12 arranged inside the clutch inner 5, that is, in a direction away from the groups of friction plates 6 and 7. Hydraulic oil is supplied to the hydraulic chamber 13 of the hydraulic cylinder 9 from the control oil passage Lc through an oil passage 14 formed in the crankshaft 1.

When high-pressure hydraulic oil is supplied to the hydraulic chamber 13, the piston 11 receives the hydraulic pressure and moves forward while compressing the return spring 12. By pressing the friction plates 6 and 7 together, the friction plates 6 and 7 can be frictionally connected through a half-clutch state. In this clutch connected state, the crankshaft 1. The power transmitted to the clutch outer 4 is transmitted to the clutch inner 5 via both friction plates 6.1, and then to the next continuously variable transmission Tm. Furthermore, when the hydraulic oil in the hydraulic cylinder 9 is discharged, the piston 11 retreats due to the elastic force of the return spring 12, so the frictional connection between the two friction plates 6sT is released (clutch disengaged state), and the above-mentioned power transmission is stopped. Pause.

The starting clutch Sc employs a wet type in which both friction plates 6.7 are cooled with hydraulic oil. By the way, if too much cooling oil is supplied to both friction plates 6 and 7, a dragging phenomenon will occur between both friction plates 6 and 7 due to the viscosity of the cooling oil when the clutch is disengaged, and when the clutch is connected, both friction plates 6 and 7. On the other hand, if there is too little cooling oil, each friction plate 6, 7 tends to overheat when the clutch is half-engaged, which generates a large amount of frictional heat. Therefore, the supply of cooling oil The amount is.

It is required to control the flow to zero or a small amount when the clutch is disengaged and engaged, and to a large amount when the clutch is half-engaged, and a flow control valve 15 is provided for such control.

The flow control valve 15 has a cylindrical shape and is slid into the oil passage 14 of the crankshaft 1. The left end face of the valve 15 receives the oil pressure of the oil passage 14, and the right end face receives atmospheric pressure and return. spring 16
The elastic forces of the two act on each other. The flow control valve 15 has a valve hole 17 that communicates with the oil passage 14, and when the valve 15 moves to a predetermined rightward movement position, an oil hole 19 with an orifice 18 that communicates with the valve hole 17 is connected to the crankshaft 1. An oil hole 20 is formed in the clutch outer 4 to constantly communicate the oil hole 19 with the inside of the clutch inner 5 via the spline connection 3.

When the clutch is disconnected due to low pressure in the oil passage 14, the control valve 15 is held at the leftmost limit of movement by the force of the return spring 16, so that the valve hole 17 and the oil hole 19 are disconnected from each other as shown in the figure. , or the communication thereof is appropriately throttled, whereby the amount of cooling oil supplied from the oil passage 14 to the starting clutch Sc is adjusted to zero or a small amount.

When the oil pressure in the oil passage 14 rises to the point where it brings about a half-clutch state, the control valve 15 receives the oil pressure and releases the return spring 16.
is moved to the right while compressing the valve, thereby communicating the valve hole 17 with the oil hole 19, thereby connecting the oil passage 14 to the valve hole IT, oil holes 19 and 20.
Cooling oil is sufficiently supplied to the starting clutch Sc through the starting clutch Sc. The maximum flow rate of the cooling oil at this time is regulated by the orifice 18.

Furthermore, when the oil pressure in the oil passage 14 rises to the point where the clutch is engaged and the control valve 15 moves further to the right, the valve hole 1
7 and the oil hole 19 are again cut off, or their communication is appropriately throttled, whereby the supply amount of cooling oil is again adjusted to zero or a small amount.

In FIG. 1, the clutch valve VcK for operating the starting clutch Sc will be explained. A cylindrical valve surface 25 with one end closed has a return spring 26, a spool valve 27. A pressure regulating spring λ8 and a pressing plate 29 are inserted in sequence, and one end of an operating lever 31 whose central part is supported by a fixed support shaft 30 is connected to the outermost pressing plate 29, and a steering handle is connected to the other end. An operating wire 33 connected to a clutch lever 32 attached to H is connected to an operating spring 34.

The operating spring 34 has a stronger spring force than the pressure regulating spring 28 (
As the clutch lever 32 is released, the pressure regulating spring 21L is pressed via the operating lever 31 and the suppressing plate 29, and the set load thereof can be increased.

The valve surface 25 has first to fourth boats 35. ~354, with the first boat 35. is connected to the oil sump R, a control oil passage Lc is extended from the second port 35m, and the third port 35. is hydraulic pump P
and communicates with the fourth port 35. is in communication with the control oil passage Lc via the orifice 36, and also with the reaction force hydraulic chamber 38 which accommodates the return spring 26 within the valve face 25. On the other hand,
The spool valve 2T is connected to the second boat 35. and 1st boat 3L or 3rd boat 35. It has an annular groove 39 that can switch the communication with.

As shown in FIG. 1, by pulling the clutch lever 32 toward the steering handle H@, the operating spring 3 is released.
4, the spool valve 2T is moved to the right by the return spring 26 and the third port 35.4 is moved to the right by the return spring 26. 35. .

35. Make the spaces communicate. As a result, the pressure in the hydraulic cylinder 9 of the starting clutch Sc is released to the oil reservoir R, so the starting clutch Sc becomes in a disconnected state.

As the operating force of the clutch lever 32 is gradually released, the pressing plate 29 presses the pressure regulating spring 28 by the force of the operating spring 34 (and the spool valve 27 moves to the left to close the first port 35).
．． and the second and third boats 35. ．． 35a are communicated with each other, so that the oil discharged from the hydraulic pump P is connected to the control oil path L.
c. When the oil pressure of the control oil passage Lc increases accordingly, the oil pressure reaches the orifice 36tj! :: Since the reaction force is then introduced into the hydraulic pressure chamber 38, the spool valve 27j (right side) is pushed back to the point where the pressing force due to the hydraulic pressure and the set load of the pressure regulating spring 28 are balanced. Therefore, the oil pressure of the control oil passage Lc, that is, the connection oil pressure of the starting clutch Sc can be increased in accordance with the increase in the set load of the pressure regulating spring 2B as the clutch lever 32 is returned.

When using the latch valve Vc like this, the clutch lever
Even if the operating force of 32 is set to a light level, the connection hydraulic pressure of the starting clutch Sc can be set to a sufficiently large level regardless of the operating force, which makes it possible to downsize the starting clutch Sc. Further, by providing the starting clutch Sc on the crankshaft 1 which has the highest rotational speed (and lowest torque) in the power unit pu, its miniaturization is further promoted.

Next, the continuously variable transmission Tm will be explained.

This transmission Tm includes a driving r pulley 40 provided on the crankshaft 1 adjacent to the right side of the starting clutch Sty, a driven r pulley 41 located adjacent to the rear thereof, and both V-boots +J.
The main element is an r-belt 42 suspended between 40 and 41.

The drive r pulley 40 is a fixed pulley half 4 rotatably supported on the right end of the crankshaft 1 via a bearing 43.
4, and a movable pulley half 47' that is slidably connected to a cylindrical drive pulley shaft 45 integral with the fixed pulley half 44 via two ball keys 46. The body 47 is equipped with a piston 49 fixed to its back surface with a screw 48, and a rear wall plate 50α of a hydraulic cylinder 50 that accommodates the piston 49 is supported by the casing C via a ball bearing 51, and the drive pulley shaft 45
is connected by a stop ring 52. The piston 49 moves inside the hydraulic cylinder 50 into a first hydraulic chamber 50 on the V-belt 42 side. and the second hydraulic chamber 50 on the opposite side (the piston 4
9, the first hydraulic chamber 50i side is the second hydraulic chamber 50.
It is formed to be narrower than the sides.

Therefore, when the same hydraulic pressure is introduced into the meat pond pressure chambers 50te50t, the piston 49 receives the differential hydraulic pressure caused by the difference in the left and right pressure receiving areas, moves to the left, and moves the movable pulley half 47 to the fixed pulley half 44. The effective radius of the driving r pulley 40, that is, the contact radius with the r belt 42 can be expanded. Also, the first hydraulic chamber 50. With hydraulic pressure applied to the second hydraulic chamber 50. If the hydraulic pressure is released, the piston 49
is the first hydraulic chamber 50. It is possible to move the movable pulley half 4T to the right by the hydraulic pressure and move the movable pulley half 4T away from the fixed pulley half 44, thereby reducing the effective radius of the drive r pulley 40.

(Thus, the piston 4! &... and the hydraulic cylinder 5° are a hydraulic actuating device H that moves the movable pulley half 4T in the axial direction.
Configure yt.

A first control valve r1 is provided within the drive pulley shaft 45 for hydraulically operating the piston 49 as described above, and the details thereof will be described later.

Since the rear wall plate 50α of the hydraulic cylinder 50 is connected to the drive pulley shaft 45 via the stop ring 52 as described above, the hydraulic cylinder 50 is also placed in an integral connection relationship with the fixed pulley half 44. In this way, the thrust load acting between the stationary pulley half 44 and the hydraulic cylinder 50 due to the hydraulic operation of the piston 49 can be transmitted to and supported by the drive pulley shaft 45, and as a result, the hydraulic cylinder 50 can be freely rotated. The load on the ball bearing 51 supported by the ball bearing 51 is reduced.

The driven V pulley 41 is formed by a fixed pulley half 57 formed integrally with the driven pulley shaft 56, and is axially slidable on the driven pulley shaft 56 via three ball keys 58, and the fixed pulley half 5T is Movable pulley half 4T of drive pulley 40
The movable bobbin half 59 is connected to the fixed pulley half 4
4 and adjacent to each other. The movable pulley half 59 has a piston 6 fixed to its back surface with a screw 60.
1, and a hydraulic cylinder 6 that accommodates this piston 61.
The second rear wall plate 62α is connected to the driven pulley shaft 56 via a stop ring 63. The bis-ton 61 moves inside the hydraulic cylinder 62 into a first hydraulic chamber 621 on the r-belt 42 side and a second hydraulic chamber 62 on the opposite side. divided into.

The pressure receiving surface of the piston 61 is connected to the first hydraulic chamber 62 . The side is the second hydraulic chamber 62. It is formed to be narrower than the sides. Therefore, the meat pond pressure chamber 62. , 621 , right and left 1, the piston 61 moves to the right in response to the differential hydraulic pressure due to the difference in the pressure receiving areas on the left and right, brings the movable pulley half 59 closer to the fixed pulley half 57, and moves the movable pulley half 59 closer to the fixed pulley half 57, The effective radius of the V-pulley 41 can be expanded. In addition, with hydraulic pressure applied to the first hydraulic chamber 621, the second hydraulic chamber 62. If you release the hydraulic pressure of
The piston 61 moves to the left by the hydraulic pressure in the first hydraulic chamber 62m to move the movable pulley half 59 away from the fixed pulley half 57,
The effective radius of the driven V-pulley 41 can be reduced.

(Thus, the piston 61 and the hydraulic cylinder 62 act as a hydraulic actuator Hy for moving the movable pulley half 59 in the axial direction.
Configure z.

A second control valve r is provided in the driven pulley shaft 56 for hydraulically operating the piston 61 as described above, and its details will be described later.

The driven pulley shaft 56 is supported by the casing C through bearings 64, 65, and 66 at three locations, at both left and right ends and at the center. The hydraulic cylinder 62 is connected to the stop ring 6 between the center bearing 65 and the right end bearing 66.
3 and a driven pulley shaft 56, the fixed pulley half 51 is integrally connected to the fixed pulley half 51. In this way, the driven pulley shaft 5 is a thrust load that acts between the fixed pulley half 57 and the hydraulic cylinder 62 due to the hydraulic operation of the piston 61.
As a result, the load on the bearings 65 and 66 is reduced.

Well, number one. The explanation will now turn to the second control valves V, , V and the oil passages around them.

The first control valve r includes a cylindrical driven spool valve T1 that is slid into a hollow drive pulley shaft 45, and this driven spool valve T.
The main drive spool valve 70 consists of a cylindrical main drive spool valve TO slidably fitted into the main drive spool valve 70, and an inner communication pipe T2 and an outer communication pipe 73 that are fitted in a double manner inside and out are inserted into the main drive spool valve 70. The inner communication pipe 72 passes through the main drive valve TO from side to side, and provides communication between the control oil passage Lc provided in the cover C'3 of the casing C and the oil passage 14 connected to the hydraulic chamber 13 of the starting clutch Sc. .

In addition, the inner communication pipe 72 defines a cylindrical oil passage 74 inside the main drive spool valve TO, and this oil passage 7- is connected to the first oil supply passage L1 provided in the cover 〇 through the outer communication pipe 73. Communicate.

Both communication pipes 72 and 73 are connected by squeezing the right end of the outer communication pipe 73 and welding it to the outer circumferential surface of the inner communication pipe 72, and a mounting flange 75 is welded to the outer circumference of the outer communication pipe 73. ing. This mounting flange T5 is fitted into the large diameter part of a stepped mounting recess 76 formed on the inner wall of the cover 03 via an elastic seal ring 77, and is prevented from coming off by a retaining ring 78. The right protrusion of the inner communication pipe T2 is fitted into the small diameter portion of the stepped mounting recess T6 via an elastic seal ring T9. (Yes, double connecting pipes 72 and 73 have cover 0.
3, and can follow the runout of the crankshaft 1 and drive shaft 45. In addition, 8
0 is a through hole bored in the peripheral wall of the connecting pipe 730 in order to communicate the first oil supply path L1 of the cover 〇 with the inside of the outer spill pipe 73.

The main spool valve TO has a pair of annular oil supply grooves 81 on the left and right sides on the outer periphery.
．． 82 and one annular oil drain groove 83, the oil supply groove 81,
82 communicates with the cylindrical oil passage 74 in the main drive spool valve 70 via through holes 84 and 85.

Further, the driven spool valve T1 has a pair of left and right annular oil grooves 86, 87 on the outer periphery, and the left oil groove 86 is.

The left oil supply groove 81 of the main drive spool valve 70 is inserted through the through hole 88.
It is always in communication with the first hydraulic chamber 501 of the hydraulic cylinder 50 via the through hole 89, the annular oil passage 90, and the oil passage 91. The right oil groove 87 constantly communicates with the drain oil groove 83 of the main drive spool valve 70 via the through hole 92,
The second hydraulic chamber 50 of the hydraulic cylinder 50 through the through hole 93 .
We are in constant communication. The driven spool valve 71 also has a through hole 94 that controls communication and isolation between the right side oil groove 87 and the right side oil supply groove 82 of the main drive spool valve 70, and an oil drain groove 83 of the main drive spool valve 70 and a casing. A cutout-shaped oil drain port 95 is provided to control communication and cutoff with the inside of C. Further, the driven spool valve 711 is connected to the drive pulley shaft 45
It is connected to the movable pulley half 47 via an interlocking pin 96 that passes through it in the radial direction, so that it can move left and right together with the movable pulley half.

The portion of the drive pulley shaft 45 that is penetrated by the interlocking pin 96 is
A long hole 97 is formed so as not to impede the horizontal movement of the interlocking pin 96.

The second control valve r consists of a cylindrical driven spool valve 101 slidably fitted within the hollow driven pulley shaft 56, and a main driven spool valve 100 slidably fitted within the driven spool valve 101. An oil supply passage 103 and an oil discharge passage 104 are formed in the center of the active spool valve 100 and are separated from each other by a partition wall 102.

The oil supply passage 103 is the second oil supply passage formed in the cover 〇 through the communication pipe 105 inserted therein.

The oil drain passage 104 opens into a hollow portion of the driven pulley shaft 56 that communicates with the inside of the casing C.

The attachment 7 flange 106 welded to the outer periphery of the communication pipe 105 is fitted into the attachment recess 107 formed on the inner wall of the cover 03 via the elastic seal ring 1 (Nl), and is prevented from coming off by a stop ring 109. The communication pipe 105 is floatingly supported by the cover C8 and can follow the runout of the driven pulley shaft 56.

Further, the main drive spool valve 100 has a pair of left and right annular oil supply grooves 110, 111 and a single annular oil drain groove 112 on the outer periphery, and the oil supply grooves 110 and 111 are connected to each other through through holes 113 and 114. The oil drain groove 112 communicates with the oil supply path 103 , and the oil drain groove 112 communicates with the oil drain path 104 via a through hole 115 .

Further, the driven spool valve 101 has a pair of left and right annular oil grooves 116 and 117 on the outer periphery, and the right oil groove 117 has a through hole 1.
18 to the right oil supply groove 111 of the main drive spool valve 100
The first hydraulic chamber 62 of the hydraulic cylinder 62 is always in communication with the
．． The left oil groove 116 is in constant communication with the second hydraulic chamber 62 of the hydraulic cylinder 62 through the through hole 122. I am in constant communication with. The driven spool valve 101 also has a through hole 1 that controls communication and isolation between the left oil groove 116 and the left oil supply groove 110 and the left oil drain groove 112 of the driven spool valve 100.
23°124 is provided. Further, the driven spool valve 101 is connected to the movable pulley half 59 via an interlocking pin 125 passing through the driven pulley shaft 56 in the radial direction, so that the driven spool valve 101 can move laterally together with the movable pulley half body 59. The portion of the driven pulley shaft 56 that is penetrated by the interlocking pin 125 is formed into a long hole 126 so as not to hinder the left and right movement of the interlocking pin 56.

1st. Both second control valves V, , V, are on the driving side. The movable pulley half 4T and the driven movable pulley half 59 are connected by an interlocking mechanism 130 in order to operate synchronously. The interlocking mechanism 130 includes a support shaft 131 provided in the casing C in parallel with both control valves '1#'1 between both control valves V11r,
A shifter 132 is slidably supported on this support shaft 131, an intermediate portion is fixed to this shifter 132, and both control valves r1°V! The shifter 132 is actuated by the rotation of a shift lever 134 pivotally supported on the casing C, and the shift lever 134 is operated by the operation shown in FIG. Left grip H of facing handle H! It is operated by rotating the.

Here, to explain the operation of both control valves V1 and V, when the shifter 132 is located at the right movement limit in contact with the cover C1, as shown in FIG. Hole 9
4 is closed by the main drive spool valve TO, and the right side oil supply groove 8
2 and the right oil groove 87, and the oil drain groove 8
3 and the oil drain port 95 are in communication, and on the other hand, the left oil supply groove 81 and the left oil groove 86 are always in communication, so that the first hydraulic chamber 5
01, the hydraulic pressure waiting in the cylindrical oil passage 74 is introduced through the oil grooves 81, 86, etc., and the second hydraulic pressure chamber 50. is oil groove 82
, 87, etc., to the oil drain port 95.

Therefore, the piston 11 moves to the right in response to the hydraulic pressure in the first hydraulic chamber 501 and holds the movable pulley half 47 at the backward limit.

Moreover, in this case, the second control valve V! Now, the left oil supply groove 11
0 communicates with the left oil groove 116 via the through hole 123, and the through hole 124 is closed by the active spool valve 100, thereby blocking the oil drain groove 112 and the left oil groove 116. On the other hand, since the right oil groove 111 and the right oil groove 117 are always in communication, the hydraulic pressure waiting in the oil supply path 103 is applied to the first hydraulic cylinder 62. The piston 61 is introduced into the second two hydraulic chambers 62r-62*, and accordingly, as described above, the piston 61 receives the differential hydraulic pressure and moves to the right to hold the movable pulley half 59 at the forward limit.

In this way, the effective radius of the driving r pulley 40 is controlled to the minimum and the effective radius of the driven V pulley 41 is controlled to the maximum, so that the driving r pulley 40 drives the driven r pulley 41 with the maximum reduction ratio. I can do it.

Next, when the shifter 132 is moved to the left, both active spool valves 70 and 100 are simultaneously moved to the left by the interlocking rod 133. When the main drive spool valve 70 moves to the left, the through hole 94 opens and the right oil supply groove 82 and the right oil groove 87 communicate with each other, and when the oil drain port 95 is closed by the drive spool valve 70, the cylindrical oil passage 74 opens. The working oil pressure is in the second oil pressure chamber 50. Since the piston 49 receives the differential oil pressure as described above, it starts to move to the left and moves the movable bobbin half 4T forward.

Then, the movement of the movable pulley half-rest 47 is caused by the interlocking pin 96.
Since the oil is transmitted to the driven spool valve T1 via the spool valve T1, the spool valve T1 also moves at the same time and tracks the driven spool valve 70, and as a result of the tracking, the through hole 94 and the oil drain port 95 are closed by the driven spool valve 70. , second hydraulic chamber 50. When the piston 49 and the movable pulley half 4T are blocked from both the cylindrical oil passage T4 and the oil drain port 95, the movement of the piston 49 and therefore the movable pulley half 4T stops.

That is, the movable pulley half 4T can move forward in response to leftward movement of the main drive spool valve 70.

Furthermore, when the second active spool valve 100 moves to the left, the through hole 123 is closed to the active spool valve 1'00, and
Since the through hole 124 is opened and the oil drain groove 112 and the left oil groove 116 communicate with each other, the oil pressure in the second hydraulic chamber 62 is transferred to the oil drain path 10.
Released on 4th. For this reason, the piston 61 is in the first hydraulic chamber 62. The leftward movement starts due to the hydraulic pressure of the movable pulley half 59.
to retreat. Then, the retreat of the movable pulley half 59 is transmitted to the driven spool valve 101 via the interlocking pin 125, so the spool valve tot also moves at the same time and tracks the driving spool valve 100. Hole 11
3,114 is closed to the main drive spool valve 100, and the second
Hydraulic chamber 62. When the piston 61 and the movable pulley half 59 are cut off from both the oil supply passage 103 and the oil discharge passage 104, the movement of the piston 61 and therefore the movable pulley half 59 is stopped. That is, the movable pulley half 5
9 can be moved backward in response to leftward movement of the main drive spool valves '1j, , o.

In this way, the movable pulley half 4 of the drive r pulley 40
7 and the retreat of the movable pulley half 59 of the driven r pulley 41 are performed in synchronization.

The reduction in the effective radius of the driving r pulley 40 and the expansion of the effective radius of the driven r pulley 41 are achieved at the same time without applying excessive tension to the r pulley 42 (r bell) 42, and the reduction ratio between the r pulleys 40 and 41 of both cars is accurately adjusted. can be reduced.

In the above, the hydraulic cylinder 50 of the driving r pulley 40 is formed to have a larger diameter than the hydraulic cylinder 62 of the driven r pulley 41. According to this, even under the same hydraulic pressure, the hydraulic operating force received by the piston 49 on the driving side is transferred to the piston 6 on the driven side.
This is effective in improving the responsiveness of shifting.

Also, in the piston 49 of the drive r pulley 40, its second hydraulic chamber 50. The pressure receiving area on the side is A8, and the second hydraulic chamber 50. If the pressure receiving area of @ is A, '* 't
>', the above equation holds true, and in the piston 61 of the driven r pulley 41, 1. The first hydraulic chamber 62 of it, the side pressure receiving area is 1, the second hydraulic chamber 62! Let the pressure receiving area on the side be B2.

B, -Bl>B.

The above formula holds true. Therefore, each movable pulley half 4
The forward force generated by the 7.59 hydraulic pressure can always be made larger than the respective reverse force, and this also improves the shift response.

Furthermore, the hydraulic cylinder 50.62 has a movable pulley half 47.
．． Springs 53 and 67 are compressed as elastic members that bias the springs 59 in the forward direction, that is, in the direction of enlarging the effective radius. These springs 53°6T are connected to each hydraulic cylinder 5G.
, 62, it functions to pretension the r belt 42Vc and remove its slack.

In the auxiliary case C7, the hydraulic cylinder 50 of the driving r pulley 40 is arranged on the front outer side, and the hydraulic cylinder 62 of the driven r pulley 41 is arranged on the rear inner side, so that the fixed pulley half 5T of the driven r pulley 41 is arranged on the rear outer side. be done. Since this fixed pulley half 57 does not have an attached part such as a hydraulic cylinder 62, a recess 135 can be formed in the rear right outer surface of the casing C on the back side of the fixed pulley half 57, and the first As shown, this recess 135
The brake pedal Bp is installed using this. In this way, the outward protrusion of the brake pedal Ep can be eliminated (or the amount of the protrusion can be reduced). In the figure, St is a step.

In addition, the meat pond pressure cylinders 50, 62 are connected to both r pulleys 40.4.
1, both r pulleys 40 and 41 are arranged diagonally.
Even in the case of a close arrangement, the outer diameter of each hydraulic cylinder 50, 62 can be freely set without being interfered with by the other hydraulic cylinder 62, 50, which is advantageous.

Next, the auxiliary transmission Tα will be explained.

As shown in Figures 1 and 2, the bearing 64°650
An input shaft 138 is supported on the driven pulley shaft 56 via a needle bearing 137 between the input shaft 138 and an output shaft 141 supported at both ends on a case C1 via a needle bearing 139 and a ball bearing 140 behind the input shaft 138. The input shaft 138 is connected to the driven pulley shaft 56 via a reduction gear train 142, while the input shaft 138 is connected to the driven pulley shaft 56 via a reduction gear train 142, while a low speed and high speed gear train 143
, 144, it is also connected to the output shaft 141.

The reduction gear train 142 includes a first small gear 145 spline-coupled to the driven pulley shaft 56, a first large gear 147 driven by the small gear 145 via an intermediate gear 146, and a first small gear 147 that rotates integrally with the large gear 147. It is composed of a second small gear 148 and a second large gear 149 driven by this small gear 148, and the first large gear 147 and second small gear 148, which are integrated, are supported on the output shaft 141 via a needle bearing 150. The second large gear 149 is integrally formed with one end of the input shaft 138. Therefore, the rotation of the driven pulley shaft 56 is decelerated by one step by the first gears 145, 147, and
The input shaft 1 is decelerated by 51 steps by gears 148 and 149.
38.

The low-speed gear train 143 includes a driving gear 151 integrally formed with the input shaft 138 and a driven gear 152 rotatably supported on the output shaft 141 and driven by the gear 151. The high-speed gear train 144 also includes a driven gear 152. Same (composed of a drive gear 153 integrally formed with the input shaft 138 and a driven gear 154 rotatably supported by the output shaft 141 and driven by the gear 153, and the reduction ratio is the same as that of the low-speed gear train 143. is naturally thicker than the high-speed gear train 144 (
Set. In addition, the output shaft 141Vc is connected to both driven gears 15
2,154 is slidably splined 156 such that the shifter 155 has a low speed position "LO" that couples with the driven gear 152 and a shifter 155 that couples with the driven gear 154. High speed position rHs
It has a switching position of "J", but in addition to that, both driven gears 1
The shifter 155 can be switched to a neutral position rNJ in which it is not connected to any of the angles 52 and 154, and the shift fork 157 performs the switching operation of the shifter 155. In this way, when the shifter 155 is switched to the "LoJ" or "rHsJ" position, the low speed gear train 143 or the high speed gear train 144 becomes operational, providing a two-speed gear ratio between high and low gears for five people and between the output shafts 138 and 141. be able to.

This auxiliary transmission Ta compensates for the insufficient gear ratio width of the continuously variable transmission Tna, in other words, the auxiliary transmission T
By installing α, it becomes possible to narrow the distance between the driving and driven V pulleys 40, 41 of the continuously variable transmission Tm as much as possible and to compactly store them in the casing C of the power unit PtL. Some sacrifice in the gear ratio width of the continuously variable transmission Tm is allowed.

As described above, according to the present invention, a V-belt is suspended between the driving r pulley and the driven r pulley, each of which has a movable pulley half whose effective radius can be adjusted by movement in the axis ti direction o*, and In a V-belt continuously variable transmission in which a V-pulley is provided with a hydraulic actuation device for moving each movable pulley half, at least one of the hydraulic actuation devices urges the movable pulley half in a direction to expand the effective radius. Since it accommodates an elastic member, when the five-wheel hydraulic actuator is not in operation, it applies pretension to the R belt and removes its slack, and this allows the R belt to be removed when starting.
It is possible to prevent the application of excessive impact loads and extend the life of the V-belt. Furthermore, since the elastic member is housed within the hydraulically actuated device, there is no need to provide an occupied space for installing the elastic member (this is effective in reducing the size of the continuously variable transmission).

Incidentally, if elastic members are housed in the pad pressure actuating devices of the driving and driven r pulleys, the effect of removing slack in the V-belt is further improved.

[Brief explanation of drawings]

The drawings show one embodiment of the present invention; FIG. 1 is a schematic plan view of a power transmission system of a motorcycle, FIG. It is an enlarged longitudinal sectional plan view of the V-belt type continuously variable transmission in the power unit. "/" e HI3...Hydraulic actuation device, T1...Continuously variable transmission, 40...Driver pulley, 41...Driver r
Pulley, 42...V bell), 47.59...Movable pulley half, 53.67...Spring as elastic member Patent applicant Honda Motor Co., Ltd.

Claims (1)

[Claims] (1) A driving r pulley and a driven r pulley each having a movable pulley half whose effective radius can be adjusted by moving in the axial direction.
A V-belt is suspended between the pulleys, and the drive and driven r pulleys are provided with hydraulic actuators for moving the respective movable pulley halves. A V-belt type continuously variable transmission that houses an elastic member that urges the pulley half in the direction of expanding the effective radius.
A V-belt type % type % in which the elastic members are respectively accommodated in the flesh pressure actuation devices of the driving and driven r pulleys.