JP2009174698A - Ful toroidal stepless transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a toroidal stepless transmission equipped with a transmission ratio control mechanism which feedbacks an inclined angle of a power roller by a mechanical system. <P>SOLUTION: The transmission ratio control mechanism 201 is equipped with an arm member 21 including a first coupling section 21a for coupling an actuator 22, a second coupling section 21b for coupling the spool 23s of a ratio control valve 23, and a third coupling section 21c for coupling a piston 26p of a hydraulic servo 26 and the power roller 4. When starting to drive the actuator 22, the arm member 21 swings centering around the third coupling section 21c to move the spool 23s, controlling hydraulically the hydraulic servo 26. When the piston 26p and the power roller 4 start to move, the arm member 21 swings centering around the first coupling section 21a to move the spool 23s, thus allowing the feedback control to be carried out. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a full toroidal toroidal-type continuously variable transmission suitable for use in a transmission for use in automobiles, work vehicles, and the like. Specifically, the rotational center of a power roller is in the plane direction of both disks. The present invention relates to a full toroidal type toroidal continuously variable transmission provided with a speed ratio control mechanism for controlling the speed ratio by changing the inclination angle of a power roller by controlling movement.

  In recent years, development of a toroidal continuously variable transmission used for a continuously variable transmission mounted on an automobile, a working vehicle, or the like has been promoted. A toroidal-type continuously variable transmission is composed of an input disk, an output disk, and a power roller sandwiched between the two disks, and the gear ratio varies depending on the contact position (contact radius) with both disks based on the inclination of the power roller. can get. Such a toroidal-type continuously variable transmission changes the tilt angle of the power roller by controlling the movement of the rotation center of the power roller with respect to the surface direction of both disks by means of a link mechanism connected to a hydraulic servo, for example. Thus, a gear ratio control mechanism configured to change the gear ratio is provided.

  By the way, in the toroidal-type continuously variable transmission, feedback control is used when performing shift control in order to accurately obtain a target gear ratio, and the feedback control is not affected by an electrical failure. In addition, what can be mechanically performed rather than using a sensor or the like is desired. For this reason, the gear ratio control mechanism as described above has also been proposed that is configured to perform feedback control with a mechanical configuration (see Patent Document 1). This has a member that supports the power roller in a rotatable manner and tilts (rotates) integrally with the power roller, and controls the transmission ratio by feeding back the tilt angle of the power roller from the tilt (rotation) of this member. It is carried out.

Japanese Patent No. 3531362

  By the way, when the power roller of a full toroidal type toroidal-type continuously variable transmission is controlled to move with respect to the surface direction of both disks, the tilt angle is changed, the gear ratio is changed, and both disks are operated by the action of caster angles. The operation of changing the angle of the rotating surface in the tangential direction is autonomously performed. For this reason, when the gear ratio control mechanism that directly feeds back the inclination angle of the power roller as described above is used in a full toroidal toroidal continuously variable transmission, while allowing such autonomous operation, A mechanism for feeding back the tilt angle of the power roller has to be provided, and there is a problem that the structure becomes complicated and the apparatus becomes enlarged.

  Therefore, the present invention is provided with a gear ratio control mechanism capable of preventing the complication of the structure and the enlargement of the apparatus while allowing the gear ratio control to feed back the inclination angle of the power roller by a mechanical configuration. Another object of the present invention is to provide a full toroidal toroidal continuously variable transmission.

The present invention according to claim 1 (see, for example, FIGS. 1 to 8) includes an input disk (2), an output disk (3), and a power roller (4) sandwiched between the two disks (2, 3). A full toroidal toroidal continuously variable transmission (1) comprising a transmission ratio control mechanism (20) for controlling the transmission ratio by changing the inclination angle of the power roller (4),
The transmission ratio control mechanism (20)
An actuator (22) driven based on the set gear ratio;
A hydraulic servo (26) having a piston (26p, 27a) drivingly connected to a moving mechanism (27b) of the power roller (4);
The hydraulic pressure driven by the actuator (22) and supplied to the hydraulic servo (26) is controlled, and the ratio control valve (23, 223) driven mechanically in conjunction with the driving of the piston (26p, 27a). ) And
The hydraulic servo (26) is driven by the hydraulic pressure from the ratio control valve (23, 223) based on the drive of the actuator (22) to move the power roller (4), and the power roller (4) is moved. The ratio control valve (23, 223) is mechanically driven in conjunction with the driving of the piston (26p, 27a) by the movement of the power roller (4) based on the operation amount of the actuator (22). Feedback control so that becomes the set value,
The full toroidal type continuously variable transmission (1) is characterized in that.

The present invention according to claim 2 (see, for example, FIGS. 6 and 7) includes a drive shaft (22a) of the actuator (22), a spool (23s) of the ratio control valve (23), and the hydraulic servo (26 ) Piston (26p, 27a), and an interlocking mechanism (21, 121) for interlocking movement of each other,
A full toroidal toroidal continuously variable transmission (1 ₁ , 1 ₂ ) according to claim 1.

According to a third aspect of the present invention (see, for example, FIG. 6), the interlocking mechanism includes a first connecting portion (21a) swingably connected to a drive shaft (22a) of the actuator (22), and the The second control part (21b) is swingably connected to the spool (23s) of the ratio control valve (23) and the piston (26p, 27a) of the hydraulic servo (26) is swingably connected. An arm member (21) having a third connecting portion (21c),
By swinging the arm member (21) around the third connecting portion (21c) based on the driving of the actuator (22), the spool (23s) of the ratio control valve (23) is moved, The hydraulic servo (26) is driven by the hydraulic pressure from the ratio control valve (23) based on the movement of the spool (23s) to move the power roller (4). Based on the operating amount of the actuator (22), the spool (23s) of the ratio control valve (23) is moved by the swinging of the arm member (21) about the one connecting portion (21a). Feedback control so that the movement of the power roller (4) becomes a set value;
The full toroidal type toroidal continuously variable transmission (1 ₁ ) according to claim 2.

According to a fourth aspect of the present invention (see, for example, FIG. 7), the interlock mechanism includes a first rack gear (121a) fixed to a drive shaft (22a) of the actuator (22), and the ratio control valve (23). A center shaft (122) is coupled to the spool (23s) of the shaft and is rotatably supported by the center shaft (122) and meshed with the first rack gear (121a), and the hydraulic servo ( 26) a rack and pinion mechanism (121) having a second rack gear (121c) fixed to the piston (26p, 27a) and meshing with the pinion gear (121b),
By driving the first rack gear (121a) based on the driving of the actuator (22), the spool (23s) of the pinion gear (121b) and the ratio control valve (23) is moved, and the spool (23s) is moved. The hydraulic servo (26) is driven by the hydraulic pressure from the ratio control valve (23) to move the power roller (4), and the second rack gear (121c) is driven by the movement of the power roller (4). As a result, the spool (23s) of the pinion gear (121b) and the ratio control valve (23) moves, so that the movement of the power roller (4) based on the operation amount of the actuator (22) becomes a set value. To feedback control,
A full toroidal toroidal continuously variable transmission (1 ₂ ) according to claim 2.

According to the fifth aspect of the present invention (see, for example, FIG. 8), the ratio control valve (223) is fitted into the spool (223s) and slidably and relatively movable with respect to the spool (223s). And a sleeve (223t) in which ports (for example, 223a, 223b, 223c, 223d, and 223e) for supplying and discharging hydraulic pressure to the hydraulic servo (26) are formed by a relative positional relationship with the spool (223s). And
The drive shaft (22a) of the actuator (22) and the sleeve (223t) are coupled, and the spool (223s) and the piston (26p, 27a) of the hydraulic servo (26) are coupled,
The sleeve (223t) and the spool (223s) are moved relative to each other by the movement of the sleeve (223t) based on the drive of the actuator (22), and the hydraulic pressure from the ratio control valve (223) based on the relative movement is used. The hydraulic servo (26) is driven to move the power roller (4), and the piston (26p, 27a) is driven by the movement of the power roller (4), whereby the ratio control valve (223) spool ( 223s) moves to move the sleeve (223t) and the spool (223s) relative to each other so that the movement of the power roller (4) based on the operation amount of the actuator (22) becomes a set value. Feedback control,
The full toroidal continuously variable transmission (1 ₃ ) according to claim 1.

According to the sixth aspect of the present invention (see, for example, FIGS. 6 to 8), the hydraulic servo (26) is disposed on both sides of the piston (26p) and communicates with the ratio control valve (23, 223), respectively. Having an oil chamber (26a, 26b), and driving the piston (26p) to drive the rotational center of the power roller (4) against the surface direction of the disks (2, 3);
The ratio control valve (23, 223) is configured such that the original pressure (PL) supplied from the hydraulic pressure generation source is pressed against the direction in which the power roller (4) is driven to a position based on a set speed ratio. It is supplied to the oil chamber (26a, 26b) on the side that acts on the piston (26p),
A full toroidal toroidal continuously variable transmission (1) according to claim 1 characterized in that.

  In addition, although the code | symbol in the said parenthesis is for contrast with drawing, this is for convenience for making an understanding of invention easy, and has no influence on the structure of a claim. It is not a thing.

  According to the first aspect of the present invention, the hydraulic servo is driven by the hydraulic pressure from the ratio control valve based on the driving of the actuator to move the power roller, and the ratio control valve is interlocked with the driving of the piston by the movement of the power roller. Since the power roller movement based on the operation amount of the actuator is feedback controlled so that it becomes the set value, the full-toroidal continuously variable transmission is in the full toroidal type. The configuration of the mechanical feedback control based on the movement amount of the piston of the hydraulic servo, that is, the inclination angle of the power roller, while the inclination angle due to various operations can be fed back from the movement amount of the piston of the hydraulic servo, The ratio control valve and hydraulic servo are mechanically linked. Enough by the simplest of Rudake, compared to the speed change ratio control mechanism for directly feeding back the inclination angles of the power rollers, it is possible to prevent the enlargement of the complexity and device structures.

  According to the second aspect of the present invention, since the interlocking mechanism that interlocks the movements of the drive shaft of the actuator, the spool of the ratio control valve, and the piston of the hydraulic servo is provided, the drive of the ratio control valve by the actuator In addition, the feedback from the piston of the hydraulic servo to the ratio control valve can be realized with a simple configuration simply by providing an interlocking mechanism, thereby preventing the structure from becoming complicated and the apparatus from becoming enlarged.

  According to the third aspect of the present invention, the ratio by the actuator can be achieved with a simple configuration that includes arm members that are swingably connected to the drive shaft of the actuator, the spool of the ratio control valve, and the piston of the hydraulic servo. The drive of the control valve and the feedback from the piston of the hydraulic servo to the ratio control valve can be realized, and the complicated structure and the enlargement of the apparatus can be prevented.

  According to the fourth aspect of the present invention, the drive of the ratio control valve by the actuator can be achieved with a simple configuration that includes a rack and pinion mechanism that interlocks the drive shaft of the actuator, the spool of the ratio control valve, and the piston of the hydraulic servo. The feedback from the piston of the hydraulic servo to the ratio control valve can be realized, and the complexity of the structure and the enlargement of the apparatus can be prevented.

  According to the fifth aspect of the present invention, the ratio control valve is fitted to the spool so as to be slidable and relatively movable relative to the spool, and the hydraulic pressure is supplied to the hydraulic servo by the relative positional relationship with the spool. It is composed of a sleeve in which a port for discharging is formed, and the structure is such that the drive shaft of the actuator and the sleeve are connected, and the spool and the piston of the hydraulic servo are connected. Feedback from the servo piston to the ratio control valve can be realized, and the complexity of the structure and the enlargement of the apparatus can be prevented.

  According to the sixth aspect of the present invention, the hydraulic servo has oil chambers disposed on both sides of the piston and respectively communicating with the ratio control valve, and the rotational center of the power roller is pressed against the surface direction of both disks. Then, the ratio control valve supplies the original pressure to the oil chamber on the side that acts on the piston in the direction of pressing and driving the power roller to both the speed increasing side and the speed reducing side at a position based on the set gear ratio. Therefore, it is possible to set the tilt angle of the power roller simply by driving the ratio control valve with the actuator, and the tilt of the power roller set as described above can be set only by feedback from the hydraulic servo piston to the ratio control valve. The angle can be automatically and accurately controlled.

<First Embodiment>
A first embodiment according to the present invention will be described below with reference to FIGS. As embodiments according to the present invention, the first to third embodiments will be described below. However, when describing the portions common to these three embodiments, only the “toroidal continuously variable transmission” will be described. When it is referred to as “device 1”, it is referred to as “toroidal continuously variable transmissions 1 ₁ to 1 ₃ ”.

  As shown in FIG. 1, the continuously variable transmission 10 includes a torque converter 11, a toroidal continuously variable transmission (hereinafter simply referred to as a variator) 1, a planetary gear mechanism 6, and a forward / reverse switching mechanism 7. The variator 1 includes a full toroidal continuously variable transmission, and includes two input disks 2 and 2 connected to an input shaft 12 connected to a torque converter 11 and a connecting member 16 disposed on the outer peripheral side of the variator 1. And one output disk 3 connected to each other, and power rollers 4 and 4 sandwiched between the two disks. The input disks 2 and 2 and the output disk 3 have arc-shaped concave grooves 2a and 3a that form part of a circular shape so as to face each other, and double cavities 5 and 5 sandwiching two rows of power rollers. To cancel the thrust force between the input disks. The power rollers 4, 4 are inclined by shifting in a direction perpendicular to the shaft, and are changed continuously by changing the contact radius between the input disks 2, 2 and the output disk 3.

  The planetary gear mechanism 6 includes a carrier C having a sun gear S, a ring gear R, and a pinion P meshing with each of the sun gear S and the ring gear R. The sun gear S is connected to the output disk 3 of the variator 1 and serves as an input gear for inputting the speed change rotation by the variator 1. Further, the sun gear S is connected to the output shaft 13 via the reverse clutch RC of the forward / reverse switching mechanism 7 and also constitutes a reverse output gear.

  The ring gear R is connected to the output shaft 13 and constitutes a forward output gear. The carrier C is connected to the forward brake FB of the forward / reverse switching mechanism 7 and can be locked to the case.

  Next, the operation of the continuously variable transmission 10 will be described with reference to FIGS.

  For example, when a vehicle equipped with a continuously variable transmission 10 is started, the forward / reverse switching mechanism 7 is controlled based on hydraulic control by a shift lever (not shown) or a hydraulic control device, the reverse clutch RC is released, and the forward brake The FB is locked and the continuously variable transmission 10 is brought into a drive (D range) state. Then, as shown in FIGS. 1 and 2, the rotation of the input shaft 12 connected to the engine output shaft is transmitted to the input disks 2 and 2 of the variator 1. The rotation of the input shaft 12 transmitted to the input disks 2 and 2 is shifted by the variator 1, and the variator output rotation Vout is output from the output disk 3 and input to the sun gear S. In the variator 1, since the output disk 3 is reversed with respect to the input disks 2 and 2, the output rotation with respect to the input rotation is the reverse rotation.

  When the variator output rotation Vout is input to the sun gear S, in the planetary gear mechanism 6, the variator output rotation Vout is based on the carrier C whose rotation is fixed by the locking of the forward brake FB and the gear ratio. Is output from the ring gear R as a reverse rotation slightly decelerated with respect to (ie, the same normal rotation as the rotation of the input shaft 12). The output rotation OutD of the ring gear R is output to the output shaft 13 as an output rotation in the drive state.

  Here, for example, when a shift lever (not shown) is set to the reverse (R) range, the forward / reverse switching mechanism 7 is controlled based on the hydraulic control by a hydraulic control device (not shown), the forward brake FB is released and the river is released. The scratch RC is engaged, and the continuously variable transmission 10 is set in the reverse (R range) state. Then, the rotation of the input shaft 12 is transmitted to the input disks 2 and 2 of the variator 1, and the variator output rotation Vout is output from the output disk 3 and is input to the sun gear S and is output as it is via the reverse clutch RC. It is output to the shaft 13. The variator output rotation Vout output to the output shaft 13 becomes a reverse rotation with respect to the rotation of the input shaft 12, and is output as an output rotation OutR in the reverse state.

  Next, autonomous shift control in the variator 1 will be described with reference to FIGS.

  For example, in a vehicle equipped with a continuously variable transmission 1, as shown in FIG. 3, the rotation from the engine 31 (see FIG. 6) is transmitted, and the input disk 2 rotates at the variator input rotation Vin. When the input disk 2 rotates at the variator input rotation Vin, the surface velocity vector at the contact portion Ei based on the contact radius of the power roller 4 becomes Vdi, and at the same time, the surface velocity vector of the power roller 4 at the contact portion Ei becomes Vri. Rotation is transmitted.

  Further, the surface speed of the power roller 4 at the contact portion Eo between the power roller 4 and the output disk 3 based on the contact radius is the surface speed vector Vro having the same magnitude as the reverse direction of the surface speed vector Vri. The surface velocity vector of the output disk 3 at the portion Eo is Vdo. That is, the output disk 3 rotates at the variator output rotation Vout according to the surface velocity vector Vdo at the contact portion Eo based on the contact radius.

  On the other hand, a force Tdi based on the engine torque TE transmitted from the engine (not shown) to the input disk 2 and the contact radius at the contact portion Ei acts on the input disk 2. At this time, when torque is transmitted from the input disk 2 to the power roller 4, a traction force Ftri is applied to the power roller 4 according to the force Tdi.

  Similarly, when torque is transmitted from the power roller 4 to the output disk 3, the force Tdo acts on the output disk 3 in accordance with the traction force Ftri at the contact portion Eo. Thus, the variator output torque Tout is transmitted to the output disk 3 as the rotational torque based on the contact radius according to the force Tdo acting on the contact portion Eo.

  When the force Tdo acts on the output disk 3 from the power roller 4, the traction force Ftro acts on the power roller 4 as a reaction force of the force Tdo. The combined force of the traction forces Ftri and Ftro acting on the power roller 4 particularly supports the power roller 4 as described above in a state where the power roller 4 is not moved. The reaction force Fp acting on the carriage (moving mechanism) 27b connected to the servo 26 is balanced.

  Here, for example, when the reaction force Fp is increased by the control of the hydraulic servo 26, the reaction force Fp and the combined force of the traction forces Ftri and Ftro are not balanced, and the power roller 4 moves in the Y1 direction, and the contact portion accordingly. Ei and Eo also move. That is, as shown in FIG. 4, the power roller 4 moves from the position x in the figure to the position y. Then, the surface velocity vector Vdi at the contact portion Ei was parallel in the same direction as the surface velocity vector Vri at the position x in the drawing, but at the position y in the drawing, the surface velocity vector Vdi is the input disk at the contact portion Ei. The tangential direction of 2 is not parallel to the surface velocity vector Vri, and the difference ΔV between the surface velocity vectors Vdi and Vri is also not parallel.

  Further, since the traction force acting on the power roller 4 is the same as the direction of the difference ΔV between the surface velocity vectors Vdi and Vri, the traction force acting on the power roller 4 in the state indicated by the y position in FIG. Become. As shown in FIG. 5, the traction force Fti has a force Ftti having a direction component perpendicular to the direction component of the traction force Ftri in addition to the direction component of the traction force Ftri.

  On the other hand, at the contact portion Eo between the power roller 4 and the output disk 3, the power roller 4 has a velocity vector in the direction opposite to the surface velocity vector Vdi and is transmitted (pressed) from the power roller 4 (in this case, the outer periphery). The traction force Fto acts as a reaction force of a force including a directional component that is pressed toward the side), that is, the traction force Fto is a force Ftto having a direction component perpendicular to the direction component of the traction force Ftro and the traction force Ftro. have. By the action of these forces Ftti and Ftto, the center axis d of the power roller 4 is tilted, that is, the gear ratio (contact radius) between the input disk 2 and the output disk 3 changes autonomously.

  Then, due to the effect of the caster angle β (see FIG. 3), the power roller 4 moves while returning autonomously in the direction along the rotation direction as indicated by the position z in FIG. 4, and the surface velocity vectors Vdi, Vri. Become parallel again, and the direction component of the traction force becomes the same direction as Ftri and Ftro, so that the power roller 4 is stabilized.

  Thus, in the variator 1, the traction force Ftri + Ftro generated at the contact portions Ei and Eo between the input disk 2 and the output disk 3 and the power roller 4 and the carriage 27 b that rotatably supports the power roller 4 act. By changing the reaction force Fp, a speed difference ΔV between the input disk 2 and the output disk 3 and the power roller 4 is generated, and the shift is made autonomous by the traction force components Ftti and Ftto generated by the speed difference ΔV. Done.

  Further, the power roller 4 is linearly moved under the control of the hydraulic servo 26, and the contact portion Ei also moves accordingly. At this time, the surface velocity vector Vdi at the contact portion Ei is an angle formed with the surface velocity vector Vri as the movement distance of the contact portion Ei, that is, the movement amount of the piston 26p (see FIG. 6) of the hydraulic servo 26 increases. Also grows. As a result, the direction of the traction force Fti that is the same direction as the speed difference ΔV has a larger angle with respect to the direction of the traction force Ftri, the force Ftti of the direction component perpendicular to the direction component of the traction force Ftri also increases, and the power roller The inclination angle of 4 also increases. That is, as the movement amount of the piston 26p of the hydraulic servo 26 increases, the inclination angle of the power roller 4 also increases. That is, the movement amount of the piston 26p and the inclination angle of the power roller 4 have a one-to-one correspondence relationship. It has become.

Then, along with FIG. 6, the description of the gear ratio control mechanism 20 ₁ of the variator 1 _1. Figure 6 is a schematic view for explaining the gear ratio control mechanism 20 ₁ of the first embodiment.

Vehicles equipped with a continuously variable transmission 10 according to the present invention, the variator 1 _1, roughly, the input disk 2 connected to the engine 31, the output disc 3 connected to the drive wheels 32, has a power roller 4 which is held in these input disk 2 and output disk 3, also has a gear ratio control mechanism 20 ₁ for controlling the gear ratio by changing the inclination angle of the power roller 4 Configured.

The gear ratio control mechanism 20 ₁ of the present invention, the arm member 21, the actuator 22 is configured to have a ratio control valve 23 and the roller drive device 25,. The arm member 21 is a rod-shaped member having three connecting portions at both end portions and a central portion, and is connected to one end portion so that a telescopic member (drive shaft) 22a of an actuator 22 described later can swing freely. The first connecting portion 21a is connected to the central portion so that a connecting member 23f of the ratio control valve 23 described later is swingable, and the other end is described later. The piston rod (piston) 27a and the carriage 27b of the link mechanism 27 are each provided with a third connecting portion 21c that is connected so as to be swingable.

  The actuator 22 includes a stepping motor that is swingably connected to the first connecting portion 21a of the arm member 21 and has a telescopic member 22a that expands and contracts, and is based on a command from a control unit (ECU) (not shown). The telescopic member 22a is driven in accordance with the set gear ratio.

  The ratio control valve 23 has a spool 23 s, a port 23 a to which a line pressure (original pressure) PL is input via an oil passage a, and an oil chamber 26 b of a hydraulic servo 26 described later via an oil passage b. The port 23b is connected (communication), the port 23c is connected (communication) to the oil chamber 26a of the hydraulic servo 26 via the oil passage c, and the drain port 23d is configured. A connecting member 23f is connected to the spool 23s, and the connecting member 23f is swingably connected to the second connecting portion 21b of the arm member 21. Accordingly, the spool 23s is configured to move based on the operation of the arm member 21.

  The roller drive device 25 includes a hydraulic servo 26 and a link mechanism 27. The hydraulic servo 26 includes a piston 26p that is slidably disposed inside a cylinder 26c, and an oil chamber 26a and an oil chamber 26b that are disposed on both sides of the piston 26p. The oil chamber 26a is connected (communication) to the port 23c of the ratio control valve 23 via the oil passage c, and the oil chamber 26b is connected (communication) to the port 23b of the ratio control valve 23 via the oil passage b. Has been.

  The link mechanism 27 includes a piston rod 27a having one end connected to the piston 26p and a carriage 27b having one end rotatably supporting the power roller 4. The other end of the piston rod 27a and the carriage 27b The other end of the carriage 27b is connected to each other. The third connecting portion 21c of the arm member 21 is swingably connected to a portion where the piston rod 27a and the carriage 27b are connected.

Next, it will be described with reference to FIGS. 1 and 6 the operation of the gear ratio control mechanism 20 _1. For example, when a vehicle equipped with a continuously variable transmission 10 is started, a drive state is set by operating a shift lever (not shown) to the drive (D) range. That is, based on an electrical signal from a control unit (ECU) (not shown), hydraulic pressure is supplied from a hydraulic control device (not shown) to the hydraulic servo of the forward brake FB to engage the forward brake FB, and No hydraulic pressure is supplied to the hydraulic servo of the reverse clutch RC, and the reverse clutch RC is released.

  On the other hand, in the continuously variable transmission 10, when a shift lever (not shown) is operated to set the drive (D) range, the drive state is set, and the actuator 22 is driven based on an electrical signal from the control unit (ECU). The line pressure PL input to the ratio control valve 23 is supplied to the oil chamber 26a of the hydraulic servo 26 via the oil passage c, and is supplied to the oil chamber 26b of the hydraulic servo 26 via the oil passage b. . Thereby, the power roller 4 is hydraulically controlled by the hydraulic servo 26.

  Further, when the output disk 3 rotates in the ω5 direction in the driving state of the variator 1 (the input disk 2 rotates in the ω1 direction and the power roller 4 rotates in the ω3 direction), the power roller 4 has a reaction as described above. The hydraulic servo 26 is controlled so that the hydraulic pressure in the oil chamber 26b is larger than the hydraulic pressure in the oil chamber 26a.

  At this time, as shown in FIG. 6, when shifting the variator 1 to the speed increasing side, the actuator 22 is driven based on an electric signal from a control unit (ECU) (not shown), and the telescopic member 22a is shown in the drawing. Drive upward. When the telescopic member 22a is driven upward, the arm member 21 has the first connecting portion 21a swinging upward with the third connecting portion 21c as a fulcrum, so that the second connecting portion 21b is on the upper side. Move to. When the second connecting portion 21b moves upward, the spool 23s of the ratio control valve 23 also moves upward via the connecting member 23f, and the port 23a and the port 23c of the ratio control valve 23 communicate with each other to provide hydraulic pressure. The line pressure PL is supplied to the oil chamber 26a of the servo 26, and the port 23b and the port 23d communicate with each other so that the oil pressure in the oil chamber 26b of the hydraulic servo 26 is drained.

  As a result, the force of the hydraulic servo 26 that opposes the reaction force is weakened, the piston 26p is moved downward, and the power roller 4 is moved downward, that is, the ω1 direction side of the input disk 2 via the link mechanism 27. Thus, as described above, the power roller 4 performs an autonomous shift on the speed increasing side. At this time, the third connecting portion 21 c is moved downward together with the link mechanism 27. Then, the arm member 21 has the first connecting portion 21a as a fulcrum and the third connecting portion 21c swings downward, so that the spool 23s of the ratio control valve 23 moves downward, and the port 23a and the port 23a 23c, port 23b and port 23d are blocked. As a result, when the supply or discharge of the hydraulic pressure from the ratio control valve 23 to the hydraulic servo 26 is not performed, the movement of the piston 26p is also not performed, and the speed change operation ends.

  When shifting the variator 1 to the deceleration side, the actuator 22 is driven based on an electric signal from a control unit (ECU) (not shown), and the telescopic member 22a is driven downward. When the telescopic member 22a is driven downward, the arm member 21 causes the first connecting portion 21a to swing downward with the third connecting portion 21c as a fulcrum, so that the second connecting portion 21b moves downward. Move to. When the second connecting portion 21b moves downward, the spool 23s of the ratio control valve 23 also moves downward via the connecting member 23f, and the port 23a and the port 23b of the ratio control valve 23 communicate with each other to provide hydraulic pressure. The line pressure PL is supplied to the oil chamber 26b of the servo 26, and the port 23c and the port 23d communicate with each other to drain the oil pressure in the oil chamber 26a of the hydraulic servo 26.

  Thereby, the force opposite to the reaction force of the hydraulic servo 26 is increased, the piston 26p is moved upward, and the power roller 4 is moved upward via the link mechanism 27, that is, the direction opposite to the ω1 direction of the input disk 2. As described above, the power roller 4 performs an autonomous shift on the deceleration side. At this time, the third connecting portion 21 c is moved upward together with the link mechanism 27. Then, since the third connecting portion 21c swings upward with the first connecting portion 21a as a fulcrum, the arm member 21 moves the spool 23s of the ratio control valve 23 upward, and the port 23a and the port 23b, port 23c and port 23d are blocked. As a result, when the supply or discharge of the hydraulic pressure from the ratio control valve 23 to the hydraulic servo 26 is not performed, the movement of the piston 26p is also not performed, and the speed change operation ends.

  In the continuously variable transmission 10, when the relative rotation (acceleration) of the input disk 2 and the output disk 3 of the variator 1 changes, the balance between the traction force acting on the power roller 4 and the reaction force is lost. . The hydraulic control in this case will be described.

  For example, when a force for decelerating the output disk 3 is applied, such as when moving from a flat road to an uphill road, the traction force acting on the power roller 4 increases, and the traction force exceeds the reaction force. That is, the traction force acting on the power roller 4 exceeds the reaction force, and the power roller 4 starts to move from a predetermined position to the direction opposite to the ω5 direction (downward side) of the output disk 3. Then, the power roller 4 moves the piston 26p of the hydraulic servo 26 downward via the link mechanism 27.

  At this time, the third connecting portion 21c of the arm member 21 is also moved downward together with the piston 26p and the link mechanism 27, and the arm member 21 swings with the first connecting portion 21a as a fulcrum. The 23 spools 23s move downward. When the spool 23s of the ratio control valve 23 moves downward, the port 23a and the port 23b communicate with each other, the line pressure PL is supplied to the oil chamber 26b of the hydraulic servo 26, and the port 23c and the port 23d communicate with each other. Thus, the hydraulic pressure in the oil chamber 26a of the hydraulic servo 26 is drained.

  As a result, the piston 26p of the hydraulic servo 26 is pushed back and moved upward, and the power roller 4 is moved upward via the link mechanism 27, that is, the ω5 direction side of the output disk 3 to a predetermined position. Returned to

  On the other hand, when a force that accelerates the output disk 3 is applied, such as when moving from a flat road to a downhill road, the traction force acting on the power roller 4 is weakened and the reaction force exceeds the traction force. That is, the reaction force acting on the power roller 4 exceeds the traction force, and the power roller 4 starts to move from the predetermined position to the ω5 direction side (upper side) of the output disk 3. Then, the power roller 4 moves the piston 26p of the hydraulic servo 26 upward via the link mechanism 27.

  At this time, the third connecting portion 21c of the arm member 21 is also moved upward together with the piston 26p and the link mechanism 27, and the arm member 21 swings with the first connecting portion 21a as a fulcrum. 23 spools 23s move upward. When the spool 23s of the ratio control valve 23 moves upward, the port 23a and the port 23c communicate with each other, the line pressure PL is supplied to the oil chamber 26a of the hydraulic servo 26, and the port 23b and the port 23d communicate with each other. Thus, the hydraulic pressure in the oil chamber 26b of the hydraulic servo 26 is drained.

As a result, the piston 26p of the hydraulic servo 26 is moved downward in the form of being pulled back, and the power roller 4 is moved downward via the link mechanism 27, that is, in the direction opposite to the ω5 direction of the output disk 3, Returned to a predetermined position. Variator 1 ₁ according to the present invention as described above, the movement of the power roller 4 based on the operation amount of the actuator 22 is it possible to feedback control so that the set value.

As described above, the variator 1 ₁ according to the present invention, the third swing arm member 21 around the connecting portion 21c of which is based on the actuator 22 to move the spool 23s of the ratio control valve 23, the spool 23s The hydraulic servo 26 is controlled by the ratio control valve 23 based on the movement of the power roller 4 to move the power roller 4, and the ratio by the swing of the arm member 21 around the first connecting portion 21 a due to the movement of the power roller 4. Feedback control is performed such that the spool 23s of the control valve 23 moves and the movement of the power roller 4 based on the operation amount of the actuator 22 becomes a set value. Therefore, in the full toroidal toroidal continuously variable transmission, The inclination angle by the autonomous operation of the roller 4 is determined by the piston 26 of the hydraulic servo 26. The configuration of the mechanical feedback control based on the movement amount of the piston 26p of the hydraulic servo 26, that is, the inclination angle of the power roller 4, while being able to feed back from the movement amount of p, the actuator 22 and the ratio control valve It is sufficient to simply provide the arm member 21 swingably connected to each of the spool 23s of the 23 and the hydraulic servo 26, and the transmission ratio control for directly feeding back the inclination angle of the power roller 4 is sufficient. Compared to the mechanism, it is possible to prevent complication of the structure and enlargement of the device.

  The hydraulic servo 26 has oil chambers 26a and 26b that are disposed on both sides of the piston 26p and communicate with the ratio control valve 23, respectively, and the rotation center of the power roller 4 is set to the surface direction of both disks 2 and 3. Since it is a hydraulic servo 26 that can be pressed, the ratio control valve 23 piston 26p with respect to the direction in which the power roller 4 is pressed and driven to both the speed increasing side and the speed reducing side at a position based on the set gear ratio. Therefore, the line pressure PL can be supplied to the oil chamber on the side that acts on the oil pressure, thereby improving the controllability of the speed ratio control of the power roller 4 by the hydraulic servo 26.

<Second Embodiment>
Next, a second embodiment in which the first embodiment is partially changed will be described with reference to FIG. Figure 7 is a schematic diagram showing a variator 1 ₂ of the speed change ratio control mechanism 20 ₂ according to the second embodiment. In the second embodiment, parts that are the same as those in the first embodiment described above are denoted by the same reference numerals, except for a part that is changed, and description thereof is omitted.

Variator 1 ₂ according to the second embodiment is different from the variator 1 ₁ according to the first embodiment, the elastic member 22a of the actuator 22 in the gear ratio control mechanism 20 _1, ratio control valve 23 This is a modification of the interlocking mechanism that interlocks the movements of the spool 23s and the piston 26p of the hydraulic servo 26 with each other.

Specifically, the gear ratio control mechanism 20 _2, a rack-and-pinion mechanism 121 as interlocking mechanism, actuator 22 is configured to have a roller driving device 25 including a ratio control valve 23 and the hydraulic servo 26,. The rack and pinion mechanism 121 includes a first rack gear 121a, a pinion gear 121b, and a second rack gear 121c.

  The first rack gear 121 a is a so-called rack in which a flat plate member is cut, and is fixed to the telescopic member 22 a of the actuator 22. The pinion gear 121b is a so-called pinion gear made of a circular gear, and is rotatably supported by a central shaft 122 connected to a connection member 23f of the ratio control valve 23. The second rack gear 121c is a so-called rack in which a tabular member is cut, and is fixed to a piston rod 27a connected to the piston 26p of the hydraulic servo 26. The pinion gear 121b meshes with the first rack gear 121a and also meshes with the second rack gear 121c.

With the above configuration, the gear ratio control mechanism 20 _2, in the case of shifting the variator 1 ₂ speed increasing side, based on the electric signal from the control unit (not shown) (ECU), drives the actuator 22, The telescopic member 22a, that is, the first rack gear 121a is driven upward in the drawing. When the first rack gear 121a is driven upward, the pinion gear 121b rotates while meshing with the first rack gear 121a and moves upward with the second rack gear 121c as a fulcrum. When the pinion gear 121b moves upward, the spool 23s of the ratio control valve 23 also moves upward via the center shaft 122 and the connecting member 23f, and the port 23a and port 23c of the ratio control valve 23 communicate with each other to make hydraulic pressure. The line pressure PL is supplied to the oil chamber 26a of the servo 26, and the port 23b and the port 23d communicate with each other so that the oil pressure in the oil chamber 26b of the hydraulic servo 26 is drained.

  As a result, the force of the hydraulic servo 26 that opposes the reaction force is weakened, the piston 26p is moved downward, and the power roller 4 is moved downward, that is, the ω1 direction side of the input disk 2 via the link mechanism 27. Thus, as described above, the power roller 4 performs an autonomous shift on the speed increasing side. At this time, the second rack gear 121 c is moved downward together with the link mechanism 27. Then, the pinion gear 121b moves downward while rotating while meshing with the first rack gear 121a and the second rack gear 121c, so that the spool 23s of the ratio control valve 23 moves downward together with the central shaft 122, and the ports 23a and Port 23c, port 23b, and port 23d are blocked. As a result, when the supply or discharge of the hydraulic pressure from the ratio control valve 23 to the hydraulic servo 26 is not performed, the movement of the piston 26p is also not performed, and the speed change operation ends.

Further, in case of shifting the variator 1 ₂ the deceleration side, based on the electric signal from the control unit (not shown) (ECU), the actuator 22 is driven to drive the elastic member 22a to the lower side. When the telescopic member 22a, that is, the first rack gear 121a is driven downward, the pinion gear 121b rotates while meshing with the first rack gear 121a and moves downward with the second rack gear 121c as a fulcrum. When the pinion gear 121b moves downward, the spool 23s of the ratio control valve 23 also moves downward via the central shaft 122 and the connecting member 23f, and the port 23a and port 23b of the ratio control valve 23 communicate with each other to hydraulically move. The line pressure PL is supplied to the oil chamber 26b of the servo 26, and the port 23c and the port 23d communicate with each other to drain the oil pressure in the oil chamber 26a of the hydraulic servo 26.

  Thereby, the force opposite to the reaction force of the hydraulic servo 26 is increased, the piston 26p is moved upward, and the power roller 4 is moved upward via the link mechanism 27, that is, the direction opposite to the ω1 direction of the input disk 2. As described above, the power roller 4 performs an autonomous shift on the deceleration side. At this time, the second rack gear 121 c is moved upward together with the link mechanism 27. Then, the pinion gear 121b moves upward while rotating while meshing with the first rack gear 121a and the second rack gear 121c, so that the spool 23s of the ratio control valve 23 moves upward together with the central shaft 122, and the ports 23a and Port 23b, port 23c and port 23d are blocked. As a result, when the supply or discharge of the hydraulic pressure from the ratio control valve 23 to the hydraulic servo 26 is not performed, the movement of the piston 26p is also not performed, and the speed change operation ends.

In the continuously variable transmission 10, the change in the relative rotation of the input disk 2 and output disk 3 of the variator 1 ₂ (acceleration) occurs, the balance of balance between traction forces and reaction forces acting on the power roller 4 Collapse. The hydraulic control in this case will be described.

  For example, when a force for decelerating the output disk 3 is applied, such as when moving from a flat road to an uphill road, the traction force acting on the power roller 4 increases, and the traction force exceeds the reaction force. That is, the traction force acting on the power roller 4 exceeds the reaction force, and the power roller 4 starts to move from a predetermined position to the direction opposite to the ω5 direction (downward side) of the output disk 3. Then, the power roller 4 moves the piston 26p of the hydraulic servo 26 downward via the link mechanism 27.

  At this time, the second rack gear 121c of the rack and pinion mechanism 121 is moved downward together with the piston 26p and the link mechanism 27, and the pinion gear 121b is moved with the first rack gear 121a as a fulcrum, so that the spool 23s of the ratio control valve 23 is moved. Moves downward. When the spool 23s of the ratio control valve 23 moves downward, the port 23a and the port 23b communicate with each other, the line pressure PL is supplied to the oil chamber 26b of the hydraulic servo 26, and the port 23c and the port 23d communicate with each other. Thus, the hydraulic pressure in the oil chamber 26a of the hydraulic servo 26 is drained.

  As a result, the piston 26p of the hydraulic servo 26 is pushed back and moved upward, and the power roller 4 is moved upward via the link mechanism 27, that is, the ω5 direction side of the output disk 3 to a predetermined position. Returned to

  On the other hand, when a force that accelerates the output disk 3 is applied, such as when moving from a flat road to a downhill road, the traction force acting on the power roller 4 is weakened and the reaction force exceeds the traction force. That is, the reaction force acting on the power roller 4 exceeds the traction force, and the power roller 4 starts to move from the predetermined position to the ω5 direction side (upper side) of the output disk 3. Then, the power roller 4 moves the piston 26p of the hydraulic servo 26 upward via the link mechanism 27.

  At this time, the second rack gear 121c of the rack and pinion mechanism 121 moves together with the piston 26p and the link mechanism 27, and the pinion gear 121b moves using the first rack gear 121a as a fulcrum, so the spool 23s of the ratio control valve 23 Moves upward. When the spool 23s of the ratio control valve 23 moves upward, the port 23a and the port 23c communicate with each other, the line pressure PL is supplied to the oil chamber 26a of the hydraulic servo 26, and the port 23b and the port 23d communicate with each other. Thus, the hydraulic pressure in the oil chamber 26b of the hydraulic servo 26 is drained.

As a result, the piston 26p of the hydraulic servo 26 is moved downward in the form of being pulled back, and the power roller 4 is moved downward via the link mechanism 27, that is, in the direction opposite to the ω5 direction of the output disk 3, Returned to a predetermined position. Variator 1 ₂ according to the present invention as described above, the movement of the power roller 4 based on the operation amount of the actuator 22 is it possible to feedback control so that the set value.

As described above, the variator 1 ₂ according to the present invention, simple as including a rack and pinion mechanism 121 for interlocking the piston 22p of the spool 23s and the hydraulic servo 26 of the elastic member 22a and the ratio control valve 23 of the actuator 22 With the configuration, it is possible to realize the drive of the ratio control valve 23 by the actuator 22 and the feedback from the piston 26p of the hydraulic servo 26 to the ratio control valve 23, thereby preventing the complicated structure and the enlargement of the apparatus. it can.

  In the second embodiment, other configurations, operations, and effects are the same as those in the first embodiment, and thus description thereof is omitted.

<Third Embodiment>
Next, a third embodiment obtained by partially changing the first embodiment will be described with reference to FIG. Figure 8 is a schematic diagram showing a variator 1 ₃ of the gear ratio control mechanism 20 ₃ according to the third embodiment. In the third embodiment, parts that are the same as those in the first embodiment described above are denoted by the same reference numerals, except for a part that is changed, and description thereof is omitted.

Variator 1 ₃ according to the third embodiment is different from the variator 1 ₁ according to the first embodiment, the elastic member 22a of the actuator 22 in the gear ratio control mechanism 20 _1, ratio control valve 23 This is a modification of the interlocking mechanism that interlocks the movements of the spool 23s and the piston 26p of the hydraulic servo 26 with each other.

Specifically, the gear ratio control mechanism 20 _3, actuator 22 is configured to have a ratio control valve 223 and the hydraulic servo 26,. The ratio control valve 223 includes a spool 223s and a sleeve 223t that is slidably and relatively movably fitted to the spool 223s and has a plurality of ports.

  The spool 23s is connected to the piston rod 27a via a connecting member 223f fixed so as to be integrated with the spool 23s and a connecting member 221 connected to the connecting member 223f. It is configured to move based on the movement. The sleeve 223 t is connected to the expansion / contraction member 22 a of the actuator 22, and is configured to move based on the driving of the actuator 22. The sleeve 223t includes a port 223a to which the line pressure PL is supplied through the oil passage a1, a port 223e to which the line pressure PL is supplied through the oil passage a2, and a hydraulic servo 26 through the oil passage c. A port 223c for supplying the line pressure PL to the oil chamber 26a, a port 223b for supplying the line pressure PL to the oil chamber 26b of the hydraulic servo 26 via the oil passage b, and a drain port 223d are provided.

With the above configuration, the gear ratio control mechanism 20 _3, in case of shifting the variator 1 ₃ to the acceleration side, based on the electric signal from the control unit (not shown) (ECU), drives the actuator 22, The elastic member 22a, that is, the sleeve 223t is driven downward in the drawing. When the sleeve 223t is driven downward, the sleeve 223t and the spool 223s move relative to each other, the port 223a and the port 223c of the ratio control valve 223 communicate with each other, and the line pressure PL is supplied to the oil chamber 26a of the hydraulic servo 26. At the same time, the port 223b and the drain port 223d communicate with each other and the hydraulic pressure in the oil chamber 26b of the hydraulic servo 26 is drained.

  As a result, the force of the hydraulic servo 26 that opposes the reaction force is weakened, the piston 26p is moved downward, and the power roller 4 is moved downward, that is, the ω1 direction side of the input disk 2 via the link mechanism 27. Thus, as described above, the power roller 4 performs an autonomous shift on the speed increasing side. At this time, the spool 223s is moved downward together with the link mechanism 27, the connecting member 221, and the connecting member 223f. Then, the port 223a and the port 223c, the port 223b and the drain port 223d are blocked. As a result, when the supply or discharge of the hydraulic pressure from the ratio control valve 223 to the hydraulic servo 26 is not performed, the movement of the piston 26p is also not performed, and the shift operation is completed.

Further, in case of shifting the variator 1 ₃ the deceleration side, based on the electric signal from the control unit (not shown) (ECU), the actuator 22 is driven to drive the elastic member 22a to the upper side. When the expansion member 22a, that is, the sleeve 223t is driven upward, the sleeve 223t and the spool 223s move relative to each other, and the port 223e and the port 223b of the ratio control valve 223 communicate with each other to the oil chamber 26b of the hydraulic servo 26. While the line pressure PL is supplied, the port 223c and the drain port 223d communicate with each other, and the hydraulic pressure in the oil chamber 26a of the hydraulic servo 26 is drained.

  Thereby, the force opposite to the reaction force of the hydraulic servo 26 is increased, the piston 26p is moved upward, and the power roller 4 is moved upward via the link mechanism 27, that is, the direction opposite to the ω1 direction of the input disk 2. As described above, the power roller 4 performs an autonomous shift on the deceleration side. At this time, the spool 223s is moved upward together with the link mechanism 27, the connecting member 221, and the connecting member 223f. Then, the port 223e and the port 223b, the port 223c and the drain port 223d are blocked. As a result, when the supply or discharge of the hydraulic pressure from the ratio control valve 223 to the hydraulic servo 26 is not performed, the movement of the piston 26p is also not performed, and the shift operation is completed.

In the continuously variable transmission 10, the change in the relative rotation of the input disk 2 and output disk 3 of the variator 1 ₃ (acceleration) occurs, the balance of balance between traction forces and reaction forces acting on the power roller 4 Collapse. The hydraulic control in this case will be described.

  For example, when a force for decelerating the output disk 3 is applied, such as when moving from a flat road to an uphill road, the traction force acting on the power roller 4 increases, and the traction force exceeds the reaction force. That is, the traction force acting on the power roller 4 exceeds the reaction force, and the power roller 4 starts to move from a predetermined position to the direction opposite to the ω5 direction (downward side) of the output disk 3. Then, the power roller 4 moves the piston 26p of the hydraulic servo 26 downward via the link mechanism 27.

  At this time, the spool 223s also moves downward together with the piston 26p, the link mechanism 27, the connecting member 221, and the connecting member 223f. When the spool 223s moves downward, the port 223e and the port 223b communicate with each other to supply the line pressure PL to the oil chamber 26b of the hydraulic servo 26, and the port 223c and the drain port 223d communicate with each other. The oil pressure in the 26 oil chambers 26a is drained.

  As a result, the piston 26p of the hydraulic servo 26 is pushed back and moved upward, and the power roller 4 is moved upward via the link mechanism 27, that is, the ω5 direction side of the output disk 3 to a predetermined position. Returned to

  On the other hand, when a force that accelerates the output disk 3 is applied, such as when moving from a flat road to a downhill road, the traction force acting on the power roller 4 is weakened and the reaction force exceeds the traction force. That is, the reaction force acting on the power roller 4 exceeds the traction force, and the power roller 4 starts to move from the predetermined position to the ω5 direction side (upper side) of the output disk 3. Then, the power roller 4 moves the piston 26p of the hydraulic servo 26 upward via the link mechanism 27.

  At this time, the spool 223s also moves upward together with the piston 26p, the link mechanism 27, the connecting member 221, and the connecting member 223f. When the spool 223s moves upward, the port 223a and the port 223c communicate with each other, the line pressure PL is supplied to the oil chamber 26a of the hydraulic servo 26, and the port 223b and the drain port 223d communicate with each other. The oil pressure in the 26 oil chambers 26b is drained.

As a result, the piston 26p of the hydraulic servo 26 is moved downward in the form of being pulled back, and the power roller 4 is moved downward via the link mechanism 27, that is, in the direction opposite to the ω5 direction of the output disk 3, Returned to a predetermined position. Variator 1 ₃ according to the present invention as described above, the movement of the power roller 4 based on the operation amount of the actuator 22 is it possible to feedback control so that the set value.

As described above, the variator 1 ₃ according to the present invention, the ratio control valve 223, a spool 223S, relative position between the spool 223S with slidably and relatively movably to be fitted to said spool 223S According to the relationship, the sleeve 223t is formed with ports 223a, 223b, 223c, 223d, and 223e for supplying and discharging hydraulic pressure to the hydraulic servo 26, and the expansion / contraction member 22a of the actuator 22 and the sleeve 223t are connected to each other and the spool 223s. By simply connecting the piston 26p of the hydraulic servo 26, the drive of the ratio control valve 223 by the actuator 22 and the feedback from the piston 26p of the hydraulic servo 26 to the ratio control valve 223 can be realized. Double It can prevent complications and enlargement of equipment.

  In the third embodiment, other configurations, operations, and effects are the same as those in the first embodiment, and a description thereof will be omitted.

  The continuously variable transmission 10 according to the above-described embodiment has been described as a combination of the variator 1 with the torque converter 11, the planetary gear mechanism 6, and the forward / reverse switching mechanism 7. However, the present invention is not limited to this. Even if the planetary gear mechanism configured to combine the rotation and the variator output rotation by torque circulation and to have a gear neutral position in the neutral state in the transmission ratio is combined with a configuration that eliminates the need for a torque converter, Can be applied.

The skeleton figure which shows the continuously variable transmission which concerns on this invention. The speed diagram of the continuously variable transmission which concerns on this invention. The schematic diagram which shows a part of variator part. The schematic diagram which shows a part of variator part. The schematic diagram which shows a part of variator part. The schematic diagram which shows the gear ratio control mechanism which concerns on 1st Embodiment. The schematic diagram which shows the gear ratio control mechanism which concerns on 2nd Embodiment. The schematic diagram which shows the gear ratio control mechanism which concerns on 3rd Embodiment.

Explanation of symbols

1 Toroidal continuously variable transmission (variator)
2 Input disk 3 Output disk 4 Power roller 20 Gear ratio control mechanism 21 Interlocking mechanism, arm member 21a First connection part 21b Second connection part 21c Third connection part 22 Actuator 22a Drive shaft (expandable member)
23 Ratio control valve 23s Spool 25 Roller drive device 26 Hydraulic servo 26a Oil chamber 26b Oil chamber 26p Piston 27a Piston (piston rod)
27b Movement mechanism (carriage)
121 interlocking mechanism, rack and pinion mechanism 121a first rack gear 121b pinion gear 121c second rack gear 122 central shaft 223 ratio control valve 223s spool 223t sleeve PL original pressure (line pressure)

Claims (6)

A full toroidal toroidal type equipped with an input disk, an output disk, a power roller sandwiched between these disks, and a gear ratio control mechanism for controlling the gear ratio by changing the tilt angle of the power roller In the continuously variable transmission,
The transmission ratio control mechanism is
An actuator driven based on the set gear ratio;
A hydraulic servo having a piston drivingly connected to the moving mechanism of the power roller;
And a ratio control valve driven by the actuator to control the hydraulic pressure supplied to the hydraulic servo and driven mechanically in conjunction with the driving of the piston,
The hydraulic servo is driven by the hydraulic pressure from the ratio control valve based on the drive of the actuator to move the power roller, and the ratio control valve is mechanically interlocked with the driving of the piston by the movement of the power roller. By driving, feedback control is performed so that the movement of the power roller based on the operation amount of the actuator becomes a set value.
A toroidal-type continuously variable transmission of the full toroidal type. Provided with an interlocking mechanism for interlocking movements of the drive shaft of the actuator, the spool of the ratio control valve, and the piston of the hydraulic servo,
The full toroidal toroidal continuously variable transmission according to claim 1. The interlock mechanism includes a first connecting portion that is swingably connected to a drive shaft of the actuator, a second connecting portion that is swingably connected to a spool of the ratio control valve, and a hydraulic servo that An arm member having a third connecting portion swingably connected to the piston,
The spool of the ratio control valve is moved by the swinging of the arm member around the third connecting portion based on the driving of the actuator, and the hydraulic pressure from the ratio control valve is moved based on the movement of the spool. The servo is driven to move the power roller, and the spool of the ratio control valve is moved by the swing of the arm member around the first connecting portion due to the movement of the power roller, whereby the actuator Feedback control so that the movement of the power roller based on the operation amount becomes a set value,
The full toroidal toroidal continuously variable transmission according to claim 2. The interlock mechanism includes a first rack gear fixed to the drive shaft of the actuator, a central shaft connected to the spool of the ratio control valve, and rotatably supported by the central shaft, and meshed with the first rack gear. And a second rack gear fixed to the piston of the hydraulic servo and meshing with the pinion gear.
The drive of the first rack gear based on the drive of the actuator moves the spool of the pinion gear and the ratio control valve, and the hydraulic servo is driven by the hydraulic pressure from the ratio control valve based on the movement of the spool to drive the power. When the second rack gear is driven by the movement of the power roller, the pinion gear and the spool of the ratio control valve are moved, so that the movement of the power roller based on the operation amount of the actuator becomes a set value. Feedback control so that
The full toroidal toroidal continuously variable transmission according to claim 2. The ratio control valve is fitted with a spool and a slidably and relatively movable fit with respect to the spool, and a port for supplying and discharging hydraulic pressure with respect to the hydraulic servo is formed by a relative positional relationship with the spool. A sleeve, and
The drive shaft of the actuator and the sleeve are connected, and the spool and the piston of the hydraulic servo are connected,
The sleeve and the spool are relatively moved by the movement of the sleeve based on the drive of the actuator, the hydraulic servo is driven by the hydraulic pressure from the ratio control valve based on the relative movement to move the power roller, and By driving the piston by the movement of the power roller, the spool of the ratio control valve moves and moves the sleeve and the spool relative to each other, so that the movement of the power roller based on the operation amount of the actuator becomes a set value. Feedback control so that
The full toroidal toroidal continuously variable transmission according to claim 1. The hydraulic servo has oil chambers that are disposed on both sides of the piston and communicate with the ratio control valve, respectively, and drives the rotation center of the power roller against the surface direction of the two disks by driving the piston. And
The ratio control valve supplies an original pressure supplied from a hydraulic pressure generation source to an oil chamber on a side that causes the piston to act on a direction in which the power roller is pressed and driven at a position based on a set speed ratio. Become
The full toroidal toroidal continuously variable transmission according to claim 1.

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