JPS62180159A - Stepless transmission for vehicle - Google Patents

Abstract

PURPOSE:To improve the durability of a drive power transmission mechanism by providing a drive block movable in a radial direction between fixed pulleys 1 and 1u and movable pulleys 2 and 2u, and a means for reducing a frictional force between the drive block and the surfaces of the fixed and movable pulleys. CONSTITUTION:A stepless transmission 305 has fixed pulleys 1 and 1u and movable pulleys 2 and 2u, and a drive block 4 movable on a V-groove in a radial direction is provided between said fixed and movable pulleys. The surface of the V-groove on the drive block 4 in frictional contact with a belt is so processed as to reduce a frictional force. Therefore, a frictional force between the drive block 4 and the surfaces of the fixed and movable pulleys can be reduced and a force working on the drive block 4 can be lessened, thereby enabling the improvement of the durability of a drive power transmission mechanism.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a continuously variable transmission for a vehicle, and more particularly to an improvement in a drive block that can move within the range of the effective diameter of a pulley.

[Conventional technology]

In a conventional continuously variable transmission for a vehicle, for example, as shown in U.S. Pat. By making it movable, the rotational position of the V-belt can be changed continuously, and the speed ratio can be changed continuously.

In this case, in this type of continuously variable transmission, both sides of the V-belt must be held by frictional force against the inner surfaces of a pair of pulleys, so the coefficient of friction on the inner surfaces of the V-belt pulleys should not be made too small. I can't.

On the other hand, as described above, when changing the speed ratio, the V-belt must slide radially on the inner surface of the pulley as one of the pulleys moves in the axial direction.

Therefore, especially when changing the gear ratio, very strong pressure is applied to the V-belt from both sides thereof.

For this reason, conventional continuously variable transmissions have had problems with the durability of the V-belt.

For example, in the continuously variable transmission shown in U.S. Patent No. 850,488, a plurality of drive elements are provided between a pair of guide disks each having a spiral slit, and a flat belt It has been proposed to wrap around the

In this case, the pins at both ends of the drive element are fitted into slits in the guide disks, and the pins are fixed in place by changing the relative positions of the pair of guide disks in the rotational direction. There is.

Therefore, when changing gears, torsional stress is applied to the pin,
The durability of the pin is an issue. Furthermore, when forming the spiral slit in the guide disk, extremely high processing accuracy is required.

[Problem that the invention seeks to solve]

In view of the above points, the present invention has been made in order to provide a continuously variable transmission which has excellent overall durability and is highly usable.

[Means for solving problems]

In the first invention, in order to solve the above-mentioned problems, an endless belt is wound around an input pulley and an output pulley, and the effective diameter of the pulley is changed to continuously change the gear ratio. In the continuously variable transmission for a vehicle, the input pulley and the output pulley include a fixed pulley that is fixed to a rotating shaft and has a tapered fixed pulley surface, and a tapered movable pulley that faces the fixed pulley surface of the fixed pulley. a movable pulley having a pulley surface and movable in the axial direction of the rotating shaft; slits formed radially in the fixed pulley and the movable pulley; and a movable pulley between the fixed pulley and the movable pulley; a plurality of rigid drive blocks arranged in contact with the movable pulley surface and the movable pulley surface and movable in the radial direction along the slit in accordance with the axial movement of the movable pulley; a guide member, a portion of which is provided within the slit; a friction force reducing means for reducing the friction force between the drive block and the fixed pulley surface and the movable pulley surface; A technical means is adopted in which the belt is arranged on the outer circumferential surface of the drive block so as to be able to transmit friction therebetween. Further, in a second invention, in addition to the first invention, an endless belt is wound around an input pulley and an output pulley, and the effective diameter of the pulley is changed to continuously change the gear ratio. In the continuously variable transmission, the input pulley and the output pulley include a fixed pulley that is fixed to the rotating shaft and has a tapered fixed pulley surface, and a tapered movable pulley surface that faces the fixed pulley surface of the fixed pulley. a movable pulley movable in the axial direction of the rotating shaft; slits formed radially in the fixed pulley and the movable pulley; and between the fixed pulley and the movable pulley, the fixed pulley surface and A plurality of movable pulley surfaces are arranged in contact with the movable pulley surface,
a rigid drive block that is movable in the radial direction along the slit in response to the axial movement of the movable pulley; a guide member that is integrated with the drive block and that is at least partially disposed within the slit; A belt disposed on the outer circumferential surface of the drive block to enable frictional transmission; a protrusion provided on the belt having a V-shaped cross section parallel to the rotational direction of the belt; and a groove provided on the drive block that meshes with the protrusion of the belt. a frictional force reducing means for reducing the frictional force between the drive block, the fixed pulley surface, and the movable pulley; and a biasing means for biasing the drive block toward the center of rotation of the pulley. Adopt technical means to ensure that

[Operation] First, in the first invention, in the continuously variable transmission configured as described above, when the movable pulley approaches the fixed pulley during gear shifting, the drive block moves radially outward. In this case, the frictional force reduction means reduces the frictional force between the drive block, the fixed pulley surface, and the movable pulley surface, so that the forces applied to the drive block from both side surfaces can be much smaller than in the past. Further, in this case, no axial compressive force is applied to the belt from the fixed pulley and the movable pulley.

In addition, the drive block tends to pop out radially outward due to centrifugal force, but the part where the drive block is in contact with the belt is pressed inward by the belt, and the part where it is not in contact with the belt is biased. Means attract the pulley to a radial position determined by the relative distance between the fixed and movable pulleys. Note that since the centrifugal force at the pulley portion of a continuously variable transmission for a vehicle is not very large, the force applied to the drive block from the urging means does not need to be large.

Further, since a belt is wound around the drive block so as to enable frictional transmission, a force acts on the drive block in the circumferential direction of the pulley due to the frictional force. However, the drive block can only be moved along the slit by means of a guide member which is integrated with the drive block and whose part is provided in the slit in each pulley face. Therefore, the circumferential force acting on the drive block is transmitted to the pulley via the guide member, and the rotation of the pulley is also transmitted to the drive block via the guide member. In this way, a large force acts on the guide member. Additionally, by machining the drive block and guide member separately, the machining accuracy of each is improved.

Further, by forming a portion of the guide member within the slit into a substantially cylindrical shape, the contact area between the inner wall of the slit and the guide member is reduced, and the coefficient of friction is reduced.

Furthermore, in the second invention, in order to enable frictional transmission between the drive block and the belt, a large number of V grooves are provided on the friction surface thereof, and V protrusions that mesh with the grooves are also formed on the belt.
Frictional force is increased by increasing the frictional area, wedge effect, etc. Furthermore, as a unique function of the present invention, the drive block moves in the radial direction as the movable pulley moves in the axial direction, and at the same time, because the pulley surface is tapered, it also moves slightly in the axial direction. This axial movement exerts an axial force on the belt. Since the belt and the drive block are engaged with each other through the grooves and the protrusions, this axial force increases the frictional force between the slopes of the grooves and the slopes of the protrusions of the belt.

〔Example〕

The present invention will be explained in detail below based on embodiments shown in the drawings. FIG. 1 shows a continuously variable transmission 305 for a vehicle to which the present invention is applied and an overall configuration diagram for controlling the same. It is connected to an automobile engine 301.

The continuously variable transmission 305 has a pair of groove pulleys 1.2 on the input side A.
, a pair of V-groove pulleys fun2u on the output side B, a plurality of drive blocks 4 movable in the radial direction on the grooves, and an endless belt 6 wound around the drive blocks 4. A fixed pulley 1 on the input side A is fixed integrally with an input shaft 3, and the other movable input pulley 2 is mounted so as to be slidable in the axial direction on the rotating shaft of the fixed input pulley 1.

A hydraulic chamber 203A for sliding the input movable boo U 2 in the axial direction is formed on the side of the movable input pulley 2 opposite to the part around which the endless belt 6 is wound, and the hydraulic pressure flows into the hydraulic chamber 203A. The pressure oil controls the size of the input pulley diameter defined by the input pulley 1.2.

One output side fixed pulley 1u is fixed to the output shaft 3u,
It is connected to the drive wheel W, and the other output side movable pulley 2
u is mounted on the rotating shaft of the output side fixed pulley lu so as to be slidable in the axial direction. A hydraulic chamber 203B for sliding the output side movable pulley 2u in the axial direction is provided on the opposite side of the output side movable boolean IJ 2u from the part around which the endless belt 6 is wound.
is formed, and the size of the diameter of the output pulley defined by the output pulleys lu and 2u is controlled by the pressure oil flowing into the hydraulic chamber. In other words, the hydraulic chambers 203A, 2
By controlling the pressure oil flowing into 03B, the pulley diameters of the input pulley and output pulley are adjusted, and as a result, the gear ratio e (e = input coupler rotation speed NIN/output pulley rotation speed N.ur') can be adjusted freely. selected. Each hydraulic chamber 20
The pressure oil flowing into 3A and 203B is controlled by a flow rate control means 304 consisting of a flow rate control valve, a pressure control valve, and the like.

The engine 301 is provided with a throttle opening sensor sI and an engine rotation speed sensor s2, and the input side A of the continuously variable transmission 305 is equipped with an input pulley rotation speed sensor S3 that senses the rotation speed of the input pulley l, and an output side An output pulley rotation speed sensor s4 for sensing the rotation speed of the output pulley 2u is provided at each of the output pulleys B. Each of the above-mentioned sensors and a vehicle speed sensor S for detecting vehicle speed are connected to a transmission control device 303 consisting of a microcomputer.

This transmission control device? 1303 calculates the target gear ratio of the continuously variable transmission based on the output signals from the throttle opening sensor Sl, engine speed sensor S2, and vehicle speed sensor S, and then calculates the target gear ratio of the continuously variable transmission.
The gear ratio e is calculated from the output signal from s4 and is compared with the target gear ratio described above, and a control signal is output to the hydraulic control means so that the measured gear ratio e approaches the target gear ratio.

The hydraulic control means 304 sets the hydraulic pressure and flow rate in the hydraulic chambers 203A and 203B to appropriate values based on this control signal.

Next, a specific configuration of the continuously variable transmission 305 will be described in detail. In the above configuration, the input pulley A and the output pulley B have the same configuration, so the explanation will focus on the specific configuration of the input pulley A, and the output side will not be described in detail. Omitted.

FIG. 2 shows a detailed sectional view of the input pulley in the first embodiment of the continuously variable transmission of the present invention, and FIG.
−■ Shows a cross-sectional view.

The fixed pulley 1 is made of an iron-based alloy formed into a polygonal pyramid (a 20-sided pyramid in this embodiment), and linear slits 7) la are formed radially on each pulley surface 100. The pulley surface 100 and the inner side surface of the linear slit are carburized as surface hardening treatment, and the surface is further polished to minimize surface roughness. The fixed pulley 1 is attached to the shaft 3 using the key 14 and the circlip 15.
It is fixed in one direction, the direction of rotation.

On the other hand, on the movable pulley 203 side, there is a fixed flange 8.
is fixed to the shaft 3 with a key 19 and a circlip 21, 24, and sealed to the shaft 3 with an O-ring 2o. Further, a movable pulley 2 (made of an iron-based alloy) having a pulley surface 200 in the form of a polygonal pyramid (a 20-sided pyramid in this embodiment) is provided so as to be able to slide in the axial direction with respect to the shaft 3 . The movable pulley 2, like the fixed pulley l, has bottomed linear slits 7) 2a radially provided on the pulley surface 200 as shown in FIG. Further, the pulley surface 200 and the inner side surface of the linear slit are also carburized and polished in the same way as the fixed pulley l. Further, a cam 9 is fixed to the movable pulley 2 by a bolt 10, and a cam 11 is also fixed to the fixed flange 8 by a bolt 12, so that the projections and depressions of the two cams 9 and 11 are alternated.

The movable pulley 2 and the fixed flange 8 are movable relative to each other in the axial direction and fixed in the circumferential direction. In other words,
There is an O ring 23 on the sliding surface between the movable pulley 2 and the shaft 3.
and a dry bearing 18 are installed, and on the other hand, an O-ring 22 is installed on the fixed flange side on the sliding surface between the fixed flange 8 and the movable boob I72, so that sliding is easy at any location. It is also installed on the spring 2 side to always urge the movable pulley 2 toward the fixed pulley l.

Next, the drive block 4 of the first embodiment shown in FIG.
I will explain in detail. FIG. 5 is a sectional view of the drive block, and FIG. 6 is a sectional view taken along line V-V. These plurality of drive blocks 4 are made movable only in the radial direction along the slits 1a and 2a by means of a four-piece pin 4b serving as a guide member. The drive block 4 has a V-groove 4 on the friction surface with the belt.
A cylindrical pin 4b is press-fitted and fixed into the drive block main body 4a, which has undergone the processing of d, the processing of a hole to fit the pin 4b on the surface 4c, and the surface processing that is a friction force reducing means on the surface 4C. .

The portion of the pin 4b provided within the slits la and 2a is
The frictional force on the contact surfaces with the slits 1a and 2a is reduced by the polishing process.

In addition, four pins 4 protruding from the drive block main body 4a
b are fixed so that they are aligned on the same plane with high precision. That is, the central axes of the four-wood pins are aligned with the radial plane of the pulley with high precision.

The drive block main body 4a is preferably rigid and lightweight, and may be made of metal, composite materials such as FRM or FRP, ceramics, or the like. The pin 4b, which is a guide member, acts on the drive block 4 and the slits la, 2a (because it receives force in the circumferential direction, it is preferably a rigid body with high shear resistance and lightweight; Similarly, a wide variety of materials can be used.

In this embodiment, the pin 4b is made of steel.

Furthermore, a large number of grooves 4d parallel to the belt 6, which serve as friction force increasing means, are formed on the friction surface of the drive block 4 that contacts the belt 6, and the belt 6 is also formed with V projections that mesh with the grooves 4d. has been done.

Each drive block 4 is connected to, for example, a piano wire (wire diameter 0.
One end of the tension wire 5 (5 to 11 m) is fixed by caulking or the like, and the other end of the tension wire 5 has the same number of wire slits la as the linear slits la provided in the flange portion 101 of the fixed pulley 1, as shown in FIG. It is also fixed to the tension rotor through 102 by caulking or the like.

Tension wire 7 connects bearing 1 to shaft 3
3 and circlips 16 and 17, it is fixed in the axial direction and rotatably attached, and is also installed with a gap between it and the fixed pulley l. The tension rotor has a lead groove 71, which is a spiral square groove, on its inner surface as shown in FIG. A cylindrical protrusion 202 having the same width as the lead groove 71 is fitted into the lead groove 71. A hydraulic pressure supply path 300 for moving the movable pulley 2 is formed in the shaft 3, and the hydraulic pressure supply path 300 is connected to a hydraulic chamber 203A formed between the movable pulley 2 and the fixed flange 3 of the movable pulley unit 203. is familiar with

Next, the operation when the first embodiment having the above configuration is used as the continuously variable transmission 305 for a vehicle will be explained. In FIG. 1, the input shaft 3 rotates together with the engine 301. The output pulley B rotates together with an output shaft 3u that is integrated with a differential gear (not shown). The rotational force is transmitted from the input pulley A to the output pulley B via a flat belt 6 wrapped around both pulleys, and the rotational speed of both pulleys is determined by the radius vector of the flat belt 6. This effective diameter is determined by the position of the drive block 4 sandwiched between the V-groove portion formed by the fixed pulleys 1, 1u and the movable pulley 2.2u. The movable boo 'J2.2u restricts the movement of the drive block 4 in the radial direction. In other words, in order to increase the effective diameter of the belt on the input pulley, oil (hydraulic pressure is at most 20 to 30 kg/cnl) pumped by a hydraulic pump driven by the hydraulic control means 304 is connected to the hydraulic supply path in the input shaft 3. Fixed flange 8 through 300
As a result, the movable pulley 2 moves toward the fixed pulley 1 side, and the gap between the fixed pulley 1 and the movable pulley 2 becomes smaller. Therefore, the drive block 4 moves radially outward, and the effective diameter of the belt 6 can be increased.

At this time, the belt 6 tries to reduce its effective diameter on the output pulley B side, so if the hydraulic pressure in the hydraulic chamber 203B is reduced, the drive block 4 is pressed to the small diameter side, and the movable pulley 2
u moves in the direction away from the fixed pulley 1u, and the oil in the oil chamber on the output side drains.

Therefore, as the diameter of the output side increases, the diameter of the belt 6 becomes smaller. In this way, the gear ratio of the continuously variable transmission 305 can be easily changed by supplying and discharging the oil (maximum flow rate: 20 to 301/1 IIin) that is force-fed into the pulley.

Moreover, since the pulley is a polygonal pyramid, the contact portion between the drive block 4 and the pulley surfaces 100, 200 is a surface contact, and no excessive force is applied to a part of the drive block 4. Furthermore, since the contact surface is sufficiently smooth by polishing and has a small coefficient of friction, the sliding resistance between the drive block 4 and the pulley surface to0.200 is small, and therefore the force pushing the movable pulley 2 to move the drive block 4 (pulley Thrust) can also be small. In other words, the supplied hydraulic pressure can be reduced.

This will be explained later, but since the transmission force between the pulleys is the frictional force between the belt 6 and the drive block 4, in order to transmit the necessary torque, the drive block 4 and the pulley surface 100.
The smaller the friction coefficient at 0, the smaller the pulley thrust, that is, the supplied hydraulic pressure, and the smaller the size and the higher the reliability. The oil inside the pulley is sealed by O-rings 20, 22, and 23 installed on the fixed flange 8 and the movable pulley 2, as shown in FIG.

Next, power transmission will be explained with reference to FIGS. 1 and 2. Power from the engine 301 is transmitted from the input shaft 3 to the fixed pulley l via the key 15, and from the key 19 to the fixed flange 8. The rotational force is further transmitted from the fixed flange 8 to the movable pulley 2 via the cam 11.9. Furthermore, tension is generated in the belt 6 due to the frictional force between the drive block 4 and the belt 6, which is transmitted to the drive block 4 via the linear link between the fixed pulley 1 and the movable pulley 2 (la, 2a) and the pin 4b, which is a guide member. Rotate side pulley B.

Here, a shearing force is generated between the portion of the pin 4b that is integrated with the drive block and the portion provided within the slit as power is transmitted. However, the material of the pin 4b is steel, which can sufficiently withstand this stress.

Since the output pulley B has the same transmission path as the input pulley A, a description thereof will be omitted, but the feature of the present invention is that the power is transmitted by the frictional force between the belt 6 and the drive block 4, so it is different from the conventional steel belt. Compared to this, the transmission efficiency and durability of the belt can be significantly improved.

Next, the operation of the drive block 4 will be described in detail with reference to FIGS. 2 to 10. As the movable pulley 2 moves, the drive block 4 moves radially on the pulley surface 200 along the linear slit 2m as shown in FIG. At this time, the part of the drive block 4 around which the belt is wound is movable, and the outward force due to the thrust from the fixed pulley and the centrifugal force due to rotation act to generate frictional force with the belt, contributing to the transmission force. However, the drive block 4 that is not in contact with the belt 6 tends to fly outward in the radial direction due to the above-mentioned force. Therefore, a mechanism is required to constantly pull the drive block toward the center.

In the first embodiment, the drive block 4 is connected to the tension wire 5.
This always prevents the tension drive block from popping out. Here, FIG. 7 and FIG. 8 show diagrams when the drive block 4 is on the minimum diameter side, and the tension wire 5 fixed to the drive block 4 is tensioned through the wire slit 102 of the flange portion 101 of the fixed pulley 1. It is wrapped in a low tough. In order to move the drive block to the larger diameter side from this state, when the movable pulley 2 moves toward the fixed pulley l side, the tension rotor 7 is moved between the spiral lead groove 71 and the cylindrical protrusion 202 at the tip of the flange portion 201 of the movable pulley. Therefore, as the drive block 4 rotates in the direction of the arrow in FIG. 8 and moves in the outer diameter direction, the tension wire 5 is uncoiled from the tension rotor 7, and as the movable pulley 2 moves, the position of the cylindrical protrusion 202 is determined and the tension rotor is moved. Since the rotation angle of the tension wire 5 is determined, the length of the tension wire 5 is adjusted.

The state when the drive block 4 reaches its maximum diameter is shown in FIGS. 9 and 10. The rotation angle of the tension rotor 7 from FIG. 8 is approximately 90 degrees, and this value is determined by the stroke of the drive block and the wire winding diameter of the tension rotor.

Here, the slit 102 provided in the flange portion 101 of the fixed boo I71 has the effect of guiding the wire 5 so that the drive block 4 can be moved while being constantly pulled toward the center.

As mentioned above, the centrifugal force acting on the drive block 4 of the first embodiment is transmitted by the tension wire 5, and the rotational force is transmitted by the frictional force with the belt 6 via the pin 4b.

Furthermore, the force that presses the drive block in the radial direction of the pulley due to the tension of the bell 1- and the force that presses the drive block in the axial direction of the pulley due to the movement of the movable pulley act on the surface 4C of the drive block 4. Transmission of rotational force between the drive block and the pulley is performed by the pin 4b.

In this way, the actuating force is distributed, and all the actuating force is not applied to the pin, such as the pin of the drive element shown in U.S. Pat. Just consider whether it will slide. Therefore, the machining accuracy of the drive block 4, the pulley surfaces 100, 200 of the fixed and movable pulleys 1 and 2, and their slits la and 2a can be reduced, and durability can also be improved.

Next, a second embodiment of the present invention will be described based on FIG. 11. As shown in FIG.
b is passing through. Other than this configuration, the second embodiment is completely the same as the first embodiment.

In the second embodiment, the same effects as in the first embodiment described above can be obtained. Furthermore, in the first embodiment described above, the pins 4b protruding from the two surfaces 4c of the drive block 4 must be aligned on one plane parallel to the slots la and 2a along which the drive block 4 moves. If these are not aligned, the forces acting on each pin 4b will be uneven, resulting in a large force acting on a specific pin or causing distortion stress such as torsion in the drive block 4. Therefore, positioning of the pin 4b, that is, machining of the hole into which the pin 4b fits, requires highly accurate machining. However, in this second embodiment, 2
Since the pin 4b protruding from one surface 4C penetrates,
The accuracy of arranging all the protruding pins 4b on one plane can be improved. Furthermore, the rigidity of the drive block 4 can be supplemented.

Further, as in the third embodiment shown in FIG. 12, the first embodiment and the second embodiment can be
Effects similar to those of the embodiment can be obtained. Furthermore, the weight of the drive block 4 can also be reduced.

Further, as in the fourth embodiment shown in FIG. 13, the tension wire 5 is configured to protrude from the center of the through hole 4e of the drive block 4, and to be held between both sides by pins 4b serving as guide members. Even if the above-mentioned first embodiment and second embodiment
The same effects as in the embodiment can be obtained, and furthermore, the constricting portion of the tension wire 5 due to the powder 5a can be omitted.

Next, FIG. 14 shows a fifth embodiment of the present invention.

This will be described based on FIG. In the fifth embodiment, grooves 4 parallel to the belt 6 are formed on the friction surface of the drive block 4 with the belt 6.
d, the belt 6, and a substantially perpendicular groove 4f. Also,
The belt 6 has these grooves 4d.

It has a protrusion that engages with 4f. The configuration other than these is the same as that of the first embodiment described above.

With the above configuration, the frictional force between the drive block 4 and the belt 6 can be improved, and the efficiency of torque transmission between the input pulley and the output pulley can be improved.

In the first to fifth embodiments described above, the pins 4b serving as guide members are arranged as shown in FIG.
It is also possible to arrange four wires as shown in Fig. 6. Alternatively, the pin 4b may have an oval cross section as shown in FIGS. 17 and 18, which is a sixth embodiment of the present invention.

In this way, the pin 4b serving as a guide member also has the function of preventing the drive block from moving away from the slits la, lb or rotating due to the frictional force with the belt 6. The shape is not limited to a cylindrical pin.

In the embodiments described above, the fixed pulley 1 and the movable pulley 2 are made of iron-based alloy, but may be made of FRM or high-strength aluminum alloy. Furthermore, there is no problem with surface hardening treatment such as hard chrome plating or electroless nickel.

Further, as the material of the drive block 4, in addition to the first embodiment, an iron alloy or a high tensile strength aluminum alloy may be used. However, the sliding portion requires surface hardening treatment, surface polishing, and other treatments and processing.

In addition, the tension wire 5 was made of piano wire, but carbon fiber,
High tensile strength fibers such as Kepler fibers or composite fibers using the same fibers may also be used. In short, the effects of the present invention can be fully achieved as long as the material has a high tension and is flexible. Furthermore, since rubber belts require tensile force, they may be made of rubber containing carbon fibers or high-tensile fibers, and the shape is advantageous for frictional transmission as it can ensure a large friction surface and a small winding radius. It does not particularly specify the belt shape, if any.

〔Effect of the invention〕

As described above, according to the first invention, it is possible to reduce the force applied to the drive block that transmits the rotational force of the belt and pulley to the belt. This has the effect of improving the durability of the mechanical parts.

Furthermore, there is no need to supply unnecessary force to move the movable pulley, so it can be used in an energy-saving manner.

Furthermore, since the drive block main body and the guide member are formed separately, the machining accuracy of each can be improved, and the stress applied to the drive block and the slit of the pulley can be made uniform. Furthermore, materials suitable for the stresses exerted by the respective operating conditions can be used.

Further, since the frictional force between a part of the guide member provided in the slit and the inner wall of the slit can be reduced, the movement of the drive block in the radial direction accompanying the movement of the movable pulley can be performed more smoothly.

Furthermore, in the second invention, in addition to the effects of the first invention, the belt and drive block are improved by increasing the friction area, the wedge effect, and the movement of the drive block in the axial direction, which is a unique effect of the second invention. The friction angle between the belt and the drive block can be dramatically improved by the force acting on the groove slope.

[Brief explanation of drawings]

Fig. 1 is a system configuration diagram of a continuously variable transmission for a vehicle including a sectional view of the continuously variable transmission of the present invention, Fig. 2 is a sectional view of the input pulley section in the first embodiment of the invention, and Fig. 3 is ■- in Figure 2
■Partial sectional view, Figure 4 is a perspective view of the drive block of the first embodiment, Figure 5 is a sectional view of the drive block of the first embodiment, and Figure 6 is a perspective view of the drive block of the first embodiment.
The figure is a sectional view taken along line V-V in figure 5, figure 7 is a partially broken enlarged sectional view of figure 2 when the drive block is at the minimum diameter position, figure 8 is a sectional view taken along 9 is a partially enlarged sectional view of FIG. 2 when the drive block is at the maximum diameter position, FIG. 10 is a sectional view taken along line IX-IX in FIG. 9, and FIG. 11 is a sectional view of the drive block of the second embodiment. FIG. 12 is a sectional view of the drive block of the third embodiment, FIG. 13 is a sectional view of the drive block of the fourth embodiment, FIG. 14 is a sectional view of the drive block of the fifth embodiment, and FIG.
FIG. 5 is a plan view of the drive block of the fifth embodiment viewed from the direction of arrow XIV in FIG. 14, FIG. 16 is a sectional view of the drive block showing the arrangement of the bin 4b, and FIG. FIG. 18 is a sectional view of the drive block and pin 4b of the sixth embodiment. A...Input pulley, B...Output pulley, 1. lu・
...Fixed pulley, 2,2u...Movable pulley, 3...
input shaft. 3u...Output shaft, 100,200...Pulley, 1
a. 2a...Slit, 4...Drive block, 4a...
・Drive block main body, 4b...Guiding member, 6...Belt 300...Hydraulic pressure supply path, 203A, 203B・
...Hydraulic chamber. 5... Tension wire, 7... Tension rotor. 40 Figure 5 Figure 6 Figure 8 ΣV [ Figure 14 Figure 15 Figure 16 Figure 17 and 18

Claims (3)

[Claims] (1) In a continuously variable transmission for a vehicle configured to wrap an endless belt around an input pulley and an output pulley, change the effective diameter of the pulley, and continuously change the gear ratio, the input pulley and the output pulley The pulley has a fixed pulley that is fixed to the rotating shaft and has a tapered fixed pulley surface, and a tapered movable pulley surface that faces the fixed pulley surface of the fixed pulley. a movable pulley; a plurality of slits formed radially in the fixed pulley and the movable pulley; a plurality of slits arranged between the fixed pulley and the movable pulley in contact with the fixed pulley surface and the movable pulley surface; a rigid drive block that is movable in the radial direction along the slit in response to the axial movement of the movable pulley; a guide member that is integrated with the drive block and that is at least partially disposed within the slit; a frictional force reducing means for reducing the frictional force between the drive block and the fixed pulley surface and the movable pulley surface; and a biasing means for biasing the drive block in the direction of the rotation center of the pulley. The continuously variable transmission for a vehicle is characterized in that the belt is disposed on an outer circumferential surface of the drive block to enable frictional transmission. (2) The continuously variable transmission for a vehicle according to claim 1, wherein a portion of the guide member provided within the slit has a substantially cylindrical shape. (3) In a continuously variable transmission for a vehicle configured to wrap an endless belt around an input pulley and an output pulley, change the effective diameter of the pulley, and continuously change the gear ratio, the input pulley and the output pulley. The pulley has a fixed pulley that is fixed to the rotating shaft and has a tapered fixed pulley surface, and a tapered movable pulley surface that faces the fixed pulley surface of the fixed pulley. a movable movable pulley; a plurality of slits formed radially in the fixed pulley and the movable pulley; a plurality of slits arranged between the fixed pulley and the movable pulley in contact with the fixed pulley surface and the movable pulley surface;
a rigid drive block that is movable in the radial direction along the slit in response to the axial movement of the movable pulley; a guide member that is integrated with the drive block and that is at least partially disposed within the slit; A belt disposed on the outer peripheral surface of the drive block to enable frictional transmission; a protrusion on the belt having a V-shaped cross section parallel to the rotational direction of the belt; and a groove on the drive block that meshes with the protrusion of the belt. a frictional force reducing means for reducing the frictional force between the drive block and the fixed pulley surface and the movable pulley surface; and urging means for urging the driving block toward the center of rotation of the pulley. A continuously variable transmission for a vehicle, characterized by comprising: