JPH054530B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Field) The present invention relates to a V-belt type continuously variable transmission that changes the effective diameters of an input pulley and an output pulley by a servo mechanism using screws.

(Prior Art) Conventional V-belt type continuously variable transmissions use hydraulic pressure to change the gear ratio and increase/decrease the clamping pressure between the input pulley or the output pulley and the V-belt. This hydraulic control is limited by the volume of the hydraulic servo cylinder and the minimum hydraulic pressure required in other parts of the hydraulic circuit, so the clamping pressure can be adjusted accurately in response to changes in the transmitted torque. It was difficult to change.

For this reason, when used as an automobile transmission where transmission torque fluctuates rapidly, excessive clamping pressure tends to always occur on the friction surface between the pulley and V-belt. This causes a decrease in power transmission efficiency and a decrease in power transmission efficiency.

A first screw formed on each fixed flange or a member interlocking with the movable flange changes the effective diameter of the input pulley or the output pulley, and a first screw threadedly engaged with the first screw and axially locked on the transmission shaft. a driver element having two screws, the first screw and the second screw rotate relative to each other to change the movable flange in the axial direction;
This is done by a servo mechanism consisting of a driver drive mechanism that controls or drives the screw or the second screw, and a cam mechanism is used as a means to make the clamping pressure between the pulley and V-belt proportional to the transmitted torque. It is possible to improve the durability of However, in the V-belt type continuously variable transmission using this method, the rotation speed of the transmission shafts (input shaft and output shaft) is usually high, ranging from several hundred to several thousand revolutions per minute. In practical terms, the pitch of the second screw must be dimensioned so that the gear ratio changes from the maximum value to the minimum value (for example, 2:1 to 1:2) with a relative rotation of about 2 rotations, so the gear ratio must be input as input. It is difficult to precisely control the
A large torque is required to control or drive the screw or the second screw, resulting in a large drive mechanism.

(Objective of the Invention) An object of the present invention is to brake or drive the first screw or the second screw of the driver through a drive mechanism capable of extremely large speed reduction, so that the gear ratio can be adjusted precisely according to the input. The object of the present invention is to provide a V-belt type continuously variable transmission in which one pulley performs speed change control and the other pulley generates a clamping force in accordance with the transmission torque of the V-belt.

(Structure of the Invention) In order to solve the above-mentioned problems, the present invention provides a fixed flange provided on an input shaft and an output shaft disposed parallel to the input shaft, respectively, and a In the V-belt type continuously variable transmission, the V-belt type continuously variable transmission is composed of an input pulley and an output pulley, each of which is made up of a movable flange that rotates integrally with the fixed flange, and a V-belt that transmits power between the input pulley and the output pulley. A first screw formed on a movable flange disposed on either the input shaft or the output shaft or a member interlocking with the movable flange, and a second screw screwed onto the first screw. , a drive element connected to the second screw and displacing the movable flange of the one shaft in the axial direction by relative rotation between the first screw and the second screw, and a drive mechanism for the driver element. a servo mechanism provided between either the input shaft or the output shaft and a movable flange disposed on the other shaft, the servo mechanism displacing the movable flange of the other shaft in the axial direction; and a cam mechanism that applies a clamping force between the movable flange, the fixed flange, and the V-belt to the movable flange of the other shaft in proportion to the transmission torque of the V-belt, and the drive mechanism of the servo mechanism includes three It has a planetary gear set consisting of elements and two brakes, one element of the planetary gear set is connected to transmit the rotation of the one shaft, and the other two elements are each removably connected to the brake. It has a belt type continuously variable transmission structure.

(Effects of the Invention) With the above configuration, one element of a planetary gear set connected to transmit the rotation of one shaft can be stopped by one of the other two elements by a brake. The remaining one element can be rotated at increased speed or decelerated speed to generate relative rotation between the first screw and the second screw, and the movable flange of one shaft can be displaced in the axial direction. Accordingly, the gear ratio can be precisely controlled and the servo mechanism can be made more compact.
Furthermore, the other pulley uses a cam mechanism to displace the movable flange of the other shaft in the axial direction, and applies the clamping force between the movable flange, the fixed flange, and the V-belt to the movable flange of the other shaft in proportion to the transmitted torque of the V-belt. Since this is applied, speed change control can be easily performed and the durability of the V-belt can be improved.

(Example) Next, a V-belt type continuously variable transmission of the present invention will be explained based on an example shown in the drawings.

FIG. 1 shows a first embodiment, in which an input shaft 1 of a V-belt continuously variable transmission, an output shaft 2 of the V-belt continuously variable transmission arranged parallel to the input shaft, and a an input pulley 3, an output pulley 4 provided integrally with the output shaft 2, a V-belt 5 that transmits power between the input pulley 3 and the output pulley 4, a servo mechanism 6 that changes the effective diameter of the input pulley 3, and an output pulley. 4, and a cam mechanism 8 provided in the servo mechanism.

The input shaft 1 is rotatably supported by the V-belt type continuously variable transmission case 10 by bearings 11 and 12, and has a stage 1 at one end (left end in the figure).
3. On the other side, an outer peripheral spline 14 and a tip screw 15 are formed.

In this embodiment, the output shaft 2 is formed integrally with a fixed flange sleeve, which will be described later, and is connected to the V-belt continuously variable transmission case 10 by bearings 21 and 22.
is rotatably supported.

The input pulley 3 has one end (the right end in the figure) abutted against the step 13 of the input shaft via a thrust bearing 16, and the other end has a sleeve-shaped portion 33 provided with a keyway 32 on its outer periphery, and a sleeve-shaped portion 33. A fixed flange 3A consisting of a flange portion 35 integrally formed with a flange portion 35 having a slit 34 provided around the outer periphery for detecting the rotational speed of the input shaft; A sleeve-shaped hub part 38 is fitted, and has a key groove 36 corresponding to the key groove 32 of the fixed flange on the inner peripheral wall, and a ball screw groove 37 of a stroke cam, which will be described later, on the outer periphery; A movable flange 3B consisting of an integrally formed flange portion 39, and a movable flange 3B that is inserted into key grooves 32 and 36 to allow displacement in the axial direction of the fixed flange 3A and movable flange 3B, and integrally rotate around the axis. It consists of a ball key 30 for carrying out.

The output pulley 4 has a keyway 41, a spline 42, and a screw 43 formed on its outer periphery, and includes a sleeve-shaped portion 44 formed integrally with the output shaft, and a flange portion 45 formed integrally with the sleeve-shaped portion 44. a fixed flange 4A, and a key groove 49 fitted on the sleeve-shaped portion 44 of the fixed flange 4A so as to be freely displaceable in the axial direction, and corresponding to the key groove 41 on the inner periphery.
is provided, and a driven screw 4, which is a first screw, is provided on the outer periphery.
A movable flange 4B consisting of a sleeve-shaped hub portion 47 having a ring 6 formed thereon, a flange portion 48 formed integrally with the hub portion 47, and a fixed flange 4A and a movable flange 4B inserted into the keyways 41 and 49. Ball key 4 for allowing displacement in the axial direction and for integrally rotating around the axis.
Consists of 0.

The V-belt 5 has working surfaces 51 and 52 that contact the V-shaped working surfaces formed by the fixed flange 3A and the fixed flange 4A and the movable flange 3B and the movable flange 4B of the input pulley 3 and the output pulley 4, respectively, and form a friction surface. are provided at both ends.

In this embodiment, the input pulley servo mechanism 6 includes a ball screw 6A and a torsion coil spring 64.
It consists of The ball screw 6A is threadedly engaged with the ball screw groove 37 of the movable flange 3B, and the ball screw groove 62A is formed on the outer periphery of the sleeve portion 62 of the stroke cam, which will be described later.
a sleeve portion 62 formed on the inner periphery, and a ball 81 inserted therebetween;
A torsion coil spring 64 is installed with both ends connected between a spring guide portion 63 formed on the outer periphery and the movable flange 3B, and a spline 86 that fits with the spline 14 of the input shaft 1 is formed. Stroke cam 82
and a cam mechanism 8 having a cam mechanism 8.

The ball screw 6A of the servo mechanism 6 also serves as the cam mechanism 8, and in FIG. The reduction ratio between the output pulleys is maximum (for example, 1:
2) Indicates a running state, and in this state, the cam mechanism 8 is connected to the tip 381 of the sleeve-shaped hub portion 38 of the movable flange 3B and the support portion 821 of the stroke cam 82.
Although the width between the movable flange 3 and
B is displaced to the right in the figure, and when traveling at the maximum reduction ratio, the space between the tip 381 of the cam mechanism 8 and the support portion 821 expands while rotating relatively. Since the torsion coil spring 64 always generates torque in the direction of the arrow in FIG. 2, it can generate axial force even when the transmitted torque is small, and the cam mechanism 8 is connected to the input shaft 1 as shown in FIG. The pressing force for pressing the movable flange 3B in the right direction in the figure is changed in accordance with the rotational displacement with respect to the fixed flange 3A.

The input pulley servo mechanism 7 includes a drive element 70 and its drive mechanism 71.

The drive element 70 is disposed on the outer periphery of the sleeve-shaped hub portion 47 of the movable flange 3B, has one end abutted against a carrier 721 of the drive mechanism 71 via a bearing 722, and is connected to a wet multi-layer motor via an annular connecting member 723. Plate electromagnetic downshift brake 7
6A, and has a second screw 72 formed on its inner periphery to be screwed into the first screw 46.
It consists of

The drive mechanism 71 includes a single planetary gear set 75 disposed around the outer periphery of the drive element 70, a wet multi-plate electromagnetic downshift brake 76A provided between the single planetary gear set 75 and the case 10, and a Downshift brake 76A
A wet multi-disc electromagnetic upshift brake 76B is provided on one side of the upshift brake 76B.

The single planetary gear set 75 includes a ring gear 751 connected to the downshift brake 76A via an annular connection member 723, a sun gear 752 connected to the upshift brake 76B via an annular connection drum 711, and a carrier 721. , and a planetary pinion 753 rotatably supported by a carrier 721 and meshed with the sun gear 752 and the link gear 751, and the ring gear 751 rotates integrally with the sleeve.

Next, the operation of this V-belt type continuously variable transmission will be explained.

(a) When driving at constant speed, downshift brake 76A,
and upshift brake 76B are both released.

Torque transmission is from input shaft 1 to stroke cam 8
2 → Ball 81 → Input pulley 3 → V belt 5 →
This is done in the order of output pulley 4 → output shaft 2. The magnitude of the message torque due to V-belt 5 is V-belt 5.
The clamping pressure is brought into contact with the stroke cam 82 via the movable flange 3B, and due to the principle of the cam mechanism, the input pulley moves slightly in the rotational direction within the elastic limit, and the ball 81 moves the input pulley in the axial direction. The clamping pressure that acts is relative to the transmitted torque,
The clamping pressure applied to the movable flange 3B that clamps the V-belt 5 is changed in proportion to the transmitted torque, and thereby the working surface of the V-belt 5 and the working surfaces of the movable flange 3B and the fixed flange 3A are The surface pressure changes to change the clamping pressure on the contact surface.

(b) Upshift is upshift brake 76B
This is done by engaging the

By engaging the upshift brake 76B, the sun gear 7 of the single planetary gear set 75 is
52 is fixed to the transmission case 10, a relative rotational force is generated between the ring gear 751 and the carrier 721, the planetary pinion 755 rotates, and the sun gear 752 and the ring gear 751 rotate relative to each other via the planetary pinion 753. However, the driver 70 has a movable flange 3 extending in the axial direction.
B is displaced in a direction that increases the effective diameter of the input pulley 3 (to the left in the figure). When the gear ratio reaches the control setting value, upshift brake 76B
will be released.

(c) For downshifting, use downshift brake 76A.
This is done by engaging the

When the downshift brake 76A is engaged,
Ring gear 7 via annular connecting drum 711
51 is fixed to the automatic transmission case 10, relative rotation occurs between the ring gear 751 and the carrier 721, and the planetary pinion 755 is rotated in the opposite direction to the upshift. 751 occurs, and the axial dimension of the driver element 70 is shortened. As a result, the V-belt 5 uses tension to displace the movable flange 4B in the direction in which the effective diameter of the output pulley 4 decreases (to the left in the figure), and the movable flange 4B
Direction of increase in the effective diameter of the output pulley (left side in the diagram)
Displace it to. The displacement of the movable flange 3B of the input pulley 3 is determined by the cam mechanism.
It is done against the pressing force of B. Downshift brake 76 when the gear ratio reaches the control set value
Release A.

In this V-belt type continuously variable transmission, if the electromagnetic brakes of the brakes 76A and 76B fail and the brakes become inapplicable, the vehicle can run with the gear ratio before the failure. This prevents the gear ratio from being changed inadvertently due to hydraulic leaks in V-belt continuously variable transmissions that use hydraulic servos to change the gear ratio, resulting in excellent safety and allowing the gear ratio to be adjusted precisely according to the input. In addition to being controllable, the driving force of the servo mechanism can be reduced, and the other servo mechanism can be made more compact.One pulley performs speed change control, and the other pulley follows the movement of one to change the speed ratio. Shift control becomes easier.

FIG. 3 shows a second embodiment.

In this embodiment, the fixed flange 3A is formed integrally with the input shaft 1, and serves as the drive mechanism 61 of the drive element 60 of the servo mechanism 6 of the input shaft 1. Drive mechanism 7
A Lavigneaux-type planetary gear set is used instead of the planetary gear set of 1. The first sun gear 9 consists of a Lavigneaux planetary gear set 90 and a downshift brake 66A and an upshift brake 66B that control its components.
01 is connected to the wet multi-disc electromagnetic downshift brake 66A which is the first brake, the second sun gear 902 is connected to the wet multi-disc electromagnetic upshift brake 66B which is the second brake, and the carrier 904 is connected to the first screw. The ring gear 903 is connected to the sleeve-shaped hub portion 38 of the movable flange 3B formed with a 37 via the carrier support portion 905 and the input shaft 1, and the ring gear 903 is connected to the sleeve portion 62 formed with a second screw 62A.

FIG. 4 shows a third embodiment of the invention.

In this embodiment, the servo mechanism 6 of the input pulley 3
is a fixed flange 3A formed integrally with the input shaft.
An annular member 84 that is supported by a screw 311 formed on the outer periphery and rotates together with the fixed flange 3A, which also serves as a cam mechanism to be described later, and a spring 816 inserted between the annular member 84 and the movable flange 3B. and the annular member 84
, a support portion 811 fixed near the center of the flange portion 39 of the movable flange 3B, and the support portion 811
A cam mechanism consisting of a centrifugal weight type cam 85 is provided, which includes a connector 813 rotatably supported by a pin 812 and a roller 815 rotatably supported by the connector 813 by a pin 814. The cam mechanism 8 generates clamping pressure for the V-belt.

Further, the servo mechanism 7 of the output pulley 4 has a drive element 7.
Planetary gear set 7 as the drive mechanism 71 of 0
5 and the case 10, and a wet multi-plate electromagnetic upshift brake 76 provided on one side of the downshift brake 76A.
It consists of B.

The planetary gear set 75 connects to the downshift brake 76A via a cylindrical connecting member 761.
The sun gear 751 is connected to the annular connecting drum 7, which is rotatably supported via a metal bearing 102 provided on the side wall of the case 10.
11, a ring gear 752 connected to the upshift brake 76B, and a carrier 7.
a first gear 756 having a number of teeth N1, which is rotatably supported by the ring gear 752 and the sun gear 751, and which is integrally formed with the first gear and meshed with the first driven gear 741; N
The planetary pinion 755 includes two second gears 757 and a third gear 758 having N3 teeth, which is integrally formed with the second gears 757 and meshed with the second driven gear 742. The number of teeth N1 to N3 of the first to third gears of the planetary pinion 755 is N1>N2>
It is set to be N3.

The driver 70 is disposed on the outer periphery of the sleeve-shaped hub portion 47 of the movable flange 4B, has one end in contact with the carrier support member 72 via a bearing 722, and has a first driven gear 741 formed thereon. The first screw 723 is formed with the second screw 723.
A sleeve 772 and a first sleeve 77 on the inner periphery.
A first screw 724 is formed on the outer periphery of the second screw 723 and is screwed into the second screw 723, and a second driven gear 742 is integrally formed therein.
A second sleeve 773 that is in contact with the sleeve-shaped hub portion 47 of B, and a spring 77 that is provided between the first driven gear 741 and the second driven gear 742 to maintain a set interval between these driven gears.
Consists of 5.

FIG. 5 shows a fourth embodiment.

In this embodiment, the drive mechanism 61 of the driver 60 of the servo mechanism 6 of the input pulley 3 includes a planetary gear set 65, a harmonic reduction gear 90, a downshift brake 76A, and an upshift brake 76B. The harmonic reducer 90 includes a wave generator 91 consisting of a plug having an oval cross section and a ball bearing fitted around the outer periphery of the plug.
A flexible flex spline 92 arranged around the outer periphery of the wave generator 91 and having a predetermined number of splines on the outer periphery, a flexible flex spline 92 provided on the outer periphery of the flex spline 92 and having one or two fewer teeth than the flex spline. The wave generator 91 is composed of a circular spline 93 formed with an inner spline, and the wave generator 91 is connected to the upshift brake 7 together with the ring gear 651 of the planetary gear set 65.
6B, the flex spline 92 is connected to the sleeve 66, and the circular spline 93 is connected to the fixed flange 3A together with the carrier 621 of the planetary gear set 65. Furthermore, sun gear 652 is connected to downshift brake 76A. Servo mechanism 7 of output pulley 4
has the same configuration as the cam mechanism of the servo mechanism 6 of the input pulley 3 of the third embodiment.

FIG. 6 shows a fifth embodiment of the invention.

The servo mechanism 6 of the input pulley 3 is a compression mechanism inserted between the movable flange 3B and an annular spring guide ring 611 that is supported by a screw 311 formed on the outer periphery of the fixed flange 3A and rotates integrally with the fixed flange 3A. The compression spring 64A generates clamping pressure for the V-belt 5.

The drive mechanism 71 of the driver 70 of the servo mechanism 7 of the output pulley 4 has a drive screw 72 formed on its inner periphery to be screwed into the driven screw 46 of the movable flange 4B of the output pulley 4, and one end is connected to a thrust bearing 722.
A sleeve 73, which is a driver of a movable flange, is brought into contact with a carrier to be described later through the sleeve 7.
3, a harmonic reducer 100 disposed on the outer periphery of the sleeve 73, and the harmonic reducer 100.
and the case 10, and a wet multi-plate electromagnetic upshift brake 76B provided on one side of the downshift brake 76A.
and a planetary gear set 75 provided between the upshift brake 76B and the harmonic reduction gear 100.

The harmonic reduction gear 100 includes a wave generator 101 consisting of a plug having an elliptical cross section, two pairs of bearings circumferentially arranged around the outer periphery of the plug, and a retainer holder arranged between the rows of each bearing.
A flexible flexspline 103 arranged on the outer periphery of the wave generator 101 and having a predetermined number of splines on the outer periphery, the flexspline 1
An inner spline having the same number of teeth as the flex spline 103 is formed on the outer periphery of the sleeve 73 and beside the movable flange, and a circular spline 105 is connected to the end of the sleeve 73 on the side of the movable flange 4B; 103 and on the other side of the circular spline 105, an inner spline having one or two more teeth than the flex spline 103 is formed, and is connected to the fixed flange 4A via the cylindrical portion 106. It consists of a circular spline 107 slidably connected in the axial direction.

The planetary gear set 75 includes a ring gear 75.
1 is connected to the brake hub 763 of the brake 76A, the sun gear 752 is connected to the upshift brake 76B, and the planetary gear 753 is rotatably supported by the carrier 721 and meshed with the ring gear 751 and the sun gear 752. There is.

FIG. 7 shows a sixth embodiment of the invention.

This embodiment has almost the same structure as the fifth embodiment, and uses a Simpson type planetary gear set as the planetary gear set. Simpson planetary gear set 68, two brakes 66A and 66B that fix its components, a downshift brake 66A that controls the ring gear 682 of the small planetary pinion 681, and the small planetary pinion 681 and the large planetary pinion 6.
Upshift brake 66B that brakes sun gear 683 of 84 and carrier 6 of small pinion 681
A carrier support member 686, etc. is attached to the sleeve portion 62 formed with the second screw 62A connected to the ring gear 688 of the large pinion, and the sleeve portion 33 of the fixed flange 3A, which is the first screw 37. It consists of a large pinion carrier 687 connected via a connecting member.

FIG. 8 shows a seventh embodiment.

In this embodiment, the servo mechanism 6 uses a hydraulic servo mechanism 6B. The hydraulic servo mechanism 6B is
A cylinder 391 is formed by projecting in the axial direction on the outer periphery of the flange portion 39 of the movable flange 3B by applying hydraulic pressure (for example, hydraulic pressure proportional to the transmitted torque) guided through the oil passage 111 formed in the axis of the input shaft 1.
and a piston 39 fixed to the fixed flange 3A.
2 to apply clamping pressure to the V-belt 5. Further, a balance shield 393 and a piston 392 connected to the cylinder 391
This forms an oil chamber 396 for centrifugal oil pressure correction. Furthermore, a spring 394 for applying clamping pressure to the V-belt 5 is provided in advance between the piston 392 and the movable flange 3B.

In addition, in the servo mechanism 7 of the output pulley, the drive element 70 is connected to the sleeve-shaped hub portion 47 of the movable flange 4B.
A first screw 46 formed on the outer periphery and a second screw 72 that engages with the screw 46 are formed with a sleeve 73 formed on the inner periphery, and connect the carrier 721 of the planetary gear set 75 and the sleeve 73. , the planetary pinion 755 has a large-diameter first gear 726 that meshes with the sun gear 752 and the ring gear 751.
and a small-diameter second gear 727 that meshes with a gear 288 provided on a support ring 287 and is formed integrally with the first gear 726 . In this servo mechanism, there is no sliding at the meshing portions that occurred in the first to sixth embodiments, and gear changes can be made smoothly.

FIG. 9 shows an eighth embodiment.

In this embodiment, a first drive gear 92 and a second drive gear 93 are attached to the tip of the rotating shaft 91 of the servo motor 9, and a second sleeve 773 and a second
The first sleeve 772 and the first driven gear 772A are integrally formed with the driven gear 773A, and the first sleeve 772 and the first driven gear 772A are integrally formed with the drive gears 92 and 93.
match each other.

FIG. 10 shows a ninth embodiment.

In this embodiment, in the servo mechanism 6 of the input pulley 3, the driver 60 is attached to the first screw 331 formed on the outer periphery of the sleeve-shaped hub portion 38 of the movable flange 3B and on the outer periphery of a support ring 331 that rotates integrally with the fixed flange.
A and a second screw 66 that screws into the threaded portion 331A.
2 is formed with a sleeve 66 formed on the inner periphery,
The carrier 621 of the planetary gear set 65 and the sleeve 66 are connected, and the planetary pinion 65
5 meshes with a ring gear 652 and a sun gear 651, and the sun gear 651 has a sleeve 66 at its inner circumference.
It meshes with a spline 663 provided on the outer periphery.

[Brief explanation of the drawing]

FIG. 1 is a sectional view of a V-belt type continuously variable transmission according to a first embodiment of the present invention, FIG. 2 is a front view of a ball screw, and FIG. 3 is a cross-sectional view of a V-belt type continuously variable transmission according to a second embodiment of the present invention. The skeleton diagram of the gear transmission, FIG. 4, is the third embodiment of the present invention.
FIG. 5 is a skeleton diagram of a V-belt type continuously variable transmission according to the fourth embodiment of the present invention, and FIG. 6 is a skeleton diagram of a V-belt type continuously variable transmission according to the fourth embodiment of the present invention. Skeletal diagram of the V-belt continuously variable transmission, No. 7
The figure is a skeletal diagram of a V-belt type continuously variable transmission according to a sixth embodiment of the present invention, FIG. 8 is a skeletal diagram of a V-belt type continuously variable transmission according to a seventh embodiment of the present invention, and FIG. FIG. 10 is a skeletal diagram of a V-belt type continuously variable transmission according to an eighth embodiment of the present invention, and FIG. 10 is a skeletal diagram of a V-belt type continuously variable transmission according to a ninth embodiment of the present invention. In the figure, 1...Input shaft, 2...Output shaft, 3...Input pulley, 4...Output pulley, 5...V belt,
6, 7... Servo mechanism, 8... Cam mechanism, 60,
70... Drive element, 61, 71... Drive mechanism, 66
A, 76A...first brake, 66B, 76B
...Second brake, 68...Simpson planetary gear set, 65, 75...Planetary gear set, 90...Ravigneau planetary gear set, 100...Harmonic reduction gear.

Claims (1)

[Scope of Claims] 1. Provided on an input shaft and an output shaft disposed parallel to the input shaft, respectively, and displaceable in the axial direction with respect to a fixed flange, and integrated with the fixed flange. An input pulley and an output pulley consisting of a rotating movable flange, and a V that transmits power between the input pulley and output pulley.
a V-belt type continuously variable transmission comprising a belt; a first screw formed on a movable flange disposed on either the input shaft or the output shaft or a member interlocking with the movable flange; A second screw screwed into the first screw, and a movable flange of the one shaft in the axial direction by relative rotation between the first screw and the second screw connected to the second screw. a servo mechanism provided with a drive element to be displaced, a drive mechanism for the drive element, and a movable flange provided between either the input shaft or the output shaft and a movable flange disposed on the other shaft. , a cam mechanism that displaces the movable flange of the other shaft in the axial direction and applies a squeezing force between the movable flange, the fixed flange, and the V-belt to the movable flange of the other shaft in proportion to the transmitted torque of the V-belt; The drive mechanism of the servo mechanism has a planetary gear set consisting of three elements and two brakes, one element of the planetary gear set is connected to transmit the rotation of the one shaft, and the other two A V-belt type continuously variable transmission, wherein each of the elements is releasably connected to the brake. 2. The cam mechanism includes an annular member that rotates integrally with the fixed flange, a support portion that is fixed to the movable flange, a connector that is rotatably supported by the support portion, and a rotatable member that is rotatably supported by the connector. The V-belt type roller according to claim 1, comprising a centrifugal weight type cam including a freely supported roller and a spring inserted between the annular member and the movable flange. gearbox. 3. The cam mechanism according to claim 1, wherein the cam mechanism comprises a stroke cam including a sleeve portion in which a ball screw is formed on the inner periphery.
Belt type continuously variable transmission.