JP2007170496A - Control system and adjusting method for toroidal type continuously-variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To accurately detect an actual slant angle by a slant angle sensor connected with a trunnion which retains a power roller. <P>SOLUTION: In a control system for a toroidal type continuously-variable transmission in which a speed change ratio corresponding to a ratio between a radius from a rotation center axis of a disk at a contact point between a power roller clamped by a pair of disks and one disk and a radius from the rotation center axis of the disk at a contact point between the power roller and the other disk is set up and its change speed is executed by changing radii at respective contact points with the power roller slanted, the control system comprises a slant angle sensor which is connected with a retaining member retaining the power roller and detects a slant angle of the retaining member and a compensating means (steps S1 and S2) for compensating deviation between a detected value of the slant angle sensor and the actual slant angle. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a toroidal-type continuously variable transmission that transmits torque between disks via a power roller sandwiched between an input disk and an output disk, and changes the gear ratio by tilting the power roller. It is about.

  The toroidal type continuously variable transmission is configured so that a power roller is sandwiched between an input disk and an output disk, and torque is transmitted between the power roller and each disk via traction oil. . If the tangential speed of the power roller at the contact point (or contact area) between the power roller and each disk matches the tangential speed at the contact point radius of each disk, this is the neutral position. The force that tilts the power roller, that is, the tilting force does not occur. When the power roller is displaced (offset) from the neutral position, the tangential speed at the contact point between the power roller and each disk is different, so that a so-called side slip occurs, and the so-called tilt that tilts the power roller is caused. Power is generated.

  Therefore, in the toroidal-type continuously variable transmission, the power roller is offset from the neutral position based on the speed change request, and the power roller is tilted to the target angle accordingly. It is executed by returning. An apparatus configured to electrically perform such shift control is described in Patent Document 1. The device described in Patent Document 1 includes a sensor that detects a tilt angle of the power roller and a sensor that detects a displacement amount of the power roller, calculates a gear ratio from the detected tilt angle, The target displacement amount is calculated from the gear ratio and the target gear ratio. Furthermore, the duty ratio for driving the solenoid valve is calculated based on the so-called actual displacement amount and the target displacement amount detected by the displacement amount sensor, and the solenoid valve is driven based on the calculation result, and output from the solenoid valve. The spool valve is controlled by the signal pressure generated, and the displacement amount of the power roller is controlled by the hydraulic pressure output from the spool valve.

JP-A-8-233085

  Shift control of a continuously variable transmission mounted on a vehicle or the like is control that causes an actually set speed ratio to be equal to or close to a target speed ratio based on a required drive amount, etc. It is necessary to accurately determine the actual gear ratio. In the apparatus described in Patent Document 1, a tilt angle sensor is provided for this purpose. However, when assembling the above-described toroidal type continuously variable transmission, the relative position of the power roller with respect to each disk, the relative position of the power roller and the trunnion holding the trunnion, or the trunnion shaft supporting the trunnion or the trunnion shaft is supported. It is difficult to accurately set the relative position with respect to the turning angle sensor in the three-dimensional space. Therefore, conventionally, even if a tilt angle sensor is provided, there is a possibility that the actual tilt angle of the power roller cannot be accurately detected.

  The present invention has been made paying attention to the above technical problem, and an object thereof is to provide a control device for a toroidal continuously variable transmission capable of accurately detecting the tilt angle of the power roller. It is.

  In order to achieve the above object, the invention of claim 1 is directed to a radius of the contact point between the power roller sandwiched between a pair of disks and one of the disks from the rotation center axis of the disk and the power. A gear ratio is set according to the ratio of the radius of the contact point between the roller and the other disc from the rotation center axis of the disc, and the power roller is tilted to change the radius of each contact point. In a control device for a toroidal-type continuously variable transmission that performs a shift, a tilt angle sensor that is connected to a holding member that holds the power roller and detects a tilt angle of the holding member, and the tilt angle sensor And a correction unit that corrects a deviation between the detected value and the actual tilt angle.

  According to a second aspect of the present invention, there is provided a toroidal-type stepless device according to the first aspect of the present invention, further comprising a tilt angle calculating means for determining the actual tilt angle based on the rotational speed of each disk. This is a transmission control device.

  According to a third aspect of the present invention, there is provided the transmission ratio control means for controlling the transmission ratio based on a detection value of the tilt angle sensor after the deviation is corrected by the correction means. A control device for a toroidal-type continuously variable transmission, further comprising:

  According to a fourth aspect of the present invention, the radius of the contact point between the power roller and one disk sandwiched between a pair of disks from the rotation center axis of the disk and the contact point between the power roller and the other disk are determined. A toroidal-type continuously variable transmission that sets a gear ratio in accordance with a ratio of a radius from the rotation center axis of the disk, and changes the radius of each contact point by tilting the power roller to perform a gear shift. In this adjustment method, each disk is rotated at a rotational speed equal to or higher than a predetermined rotational speed, and the tilt angle of the power roller is calculated based on the rotational speed of each disk in this state, and the calculated tilt is determined. The deviation between the angle and the detected value of the tilt angle sensor that detects the tilt angle of the holding member holding the power roller is obtained, and the detected value of the tilt angle is corrected so as to eliminate the deviation. Characteristic Is an adjustment how to.

  According to the first aspect of the present invention, when there is a deviation between the detected value of the tilt angle sensor and the actual tilt angle of the power roller at the time when the detected value is obtained, correction based on the deviation is executed. Is done. As a result, the deviation between the detected value and the actual tilt angle is corrected in the tilt angle sensor, and the actual tilt angle of the power roller can be accurately detected by the tilt angle sensor. Therefore, the gear ratio can be accurately obtained even in a low rotational speed state where the rotational speed of each disk cannot be accurately detected.

  According to the second aspect of the invention, since the rotational speed of each disk corresponds to the tilt angle of the power roller, the actual tilt angle of the power roller can be accurately obtained.

  Furthermore, according to the invention of claim 3, the deviation between the detected value of the tilt angle by the tilt angle sensor and the actual tilt angle of the power roller is corrected, based on the detected value of the tilt angle sensor. Since the shift control is executed, the accuracy of the shift control can be improved.

  According to the fourth aspect of the present invention, each disk is rotated at a rotational speed equal to or higher than a predetermined rotational speed, and the tilt angle of the power roller is calculated based on the rotational speed. Therefore, the rotational speed of each disk is accurately determined. Therefore, the tilt angle of the power roller can be accurately calculated, and the detected value is corrected so as to eliminate the deviation between the tilt angle and the detected value of the tilt angle sensor. It is possible to accurately perform the shift control based on.

  Next, the present invention will be described more specifically. The toroidal type continuously variable transmission targeted by the present invention has an input side disk and an output side disk facing each other, and a rotation center axis between these disks is a rotation center axis of each disk. Is a continuously variable transmission that is configured such that a power roller is disposed and sandwiched so as to be substantially orthogonal to the disk, and torque is transmitted between the disks via the power roller. In particular, it is a continuously variable transmission in which the opposing surface of each disk forms a toroidal surface, and the so-called half toroidal type in which the center of curvature of the opposing toroidal surface is near or outside the outer peripheral edge of each disk, Any of the types in which the center of curvature is inside the outer peripheral edge of each disk may be used. Further, the present invention is not limited to a so-called single cavity type continuously variable transmission including a pair of disks, and may be a double cavity type continuously variable transmission including two pairs of disks. The power rollers sandwiched between the input-side disk and the output-side disk need only be provided at equal intervals in the circumferential direction of the disk, and are not limited to a configuration including a pair of power rollers.

  3 and 4 schematically show an example of a double-cavity half-toroidal continuously variable transmission, in which the input disk 1 and the output disk 2 with the toroidal surfaces facing each other are two pairs, the same axis. It is arranged on the line. In the examples shown in these drawings, the input disks 1 are arranged at both the left and right ends in the axial direction, the output disks 2 are arranged in a so-called back-to-back manner, and an output member between these output disks 2 is used as an output member. An output gear 3 is arranged.

  The input shaft 4 passes through the center of each of the disks 1 and 2 and the output gear 3, and each input disk 1 is attached to the input shaft 4 so as to rotate integrally and move in the axial direction. Yes. On the other hand, the output disk 2 and the output gear 3 are rotatably fitted to the input shaft 4, and each output disk 2 and the output gear 3 are connected so as to rotate together. Yes. A lock nut 5 as a lock member for preventing the input disk 1 from coming off is attached to one end portion (left end portion in FIG. 3) of the input shaft 4. A hydraulic cylinder 6 is attached to the opposite end (the right end in FIG. 3). The hydraulic cylinder 6 is a clamping pressure generating mechanism for generating a clamping pressure that presses each pair of the input disk 1 and the output disk 2 toward each other, and the cylinder 7 is fixed to the input shaft 4. In addition, a piston 8 accommodated in the cylinder 7 so as to be movable in the axial direction is in contact with the back surface of the input disk 1. Accordingly, by supplying hydraulic pressure between the cylinder 7 and the piston 8, the piston 8 presses one input disk 1 toward the input disk 1 disposed on the opposite side. Has been. Note that this clamping pressure generating mechanism may be constituted by another mechanism such as a cam mechanism or a screw mechanism that changes the torque to an axial thrust instead of the hydraulic cylinder 6.

  A plurality of power rollers 9 are sandwiched between each pair of input disk 1 and output disk 2. These power rollers 9 are so-called transmission members that mediate the transmission of torque between the input disk 1 and the output disk 2, have a substantially disk shape, and between the input disk 1 and the output disk 2, The disks 1 and 2 are arranged at equal intervals in the circumferential direction. Each power roller 9 is held by a trunnion 10 so as to rotate as the disks 1 and 2 rotate, and to tilt (tilt) between the disks 1 and 2.

  Each trunnion 10 is for holding the power roller 9 so as to rotate and tilt freely, and trunnion shafts 12 extend on both upper and lower sides of a holding portion 11 having a flat surface facing the center. Yes. The upper trunnion shaft 12 in FIG. 4 is fitted to the upper yoke 13 via a bearing, and the lower trunnion shaft 12 in FIG. 4 is fitted to the lower yoke 14 via a bearing. Accordingly, the trunnions 10 are connected to each other by the yokes 11 and 12 so as to be rotatable about the trunnion shaft 12. Therefore, the central axis of the trunnion shaft 12 is the tilt axis.

  Each power roller 9 is rotatably held by a pivot shaft 15 attached to the holding portion 11 in each trunnion 10, and a thrust bearing 16 is interposed between each power roller 9 and each trunnion 10. . The trunnion 10, the pivot shaft 15, the thrust bearing 16 and the like correspond to the holding member of the present invention.

  The lower trunnion shaft 12 in FIG. 4 in each trunnion 10 is connected to an actuator that performs a linear longitudinal movement. The actuator is composed of a fluid pressure cylinder, an electric cylinder that outputs torque by changing it into thrust, and a hydraulic cylinder 17 is employed in the example shown in the figure. Specifically, the trunnion shaft 12 is connected to a piston 18 of a hydraulic cylinder 17 provided corresponding to each power roller 9. These hydraulic cylinders 17 are configured to move one power roller 9 upward in FIG. 4 and simultaneously move the other power roller 9 downward in FIG. 4. For example, the hydraulic chamber above the piston 18 in the left hydraulic cylinder 17 in FIG. 4 is a high oil chamber 17H for shifting to a high speed side with a small gear ratio, and the lower hydraulic chamber opposite thereto is shifted. The low oil chamber 17L is used for shifting to a low speed side having a large ratio. In addition, the hydraulic chamber above the piston 18 in the right hydraulic cylinder 17 in FIG. 4 is a low oil chamber 17L for shifting to a low speed side with a large gear ratio, and the lower hydraulic chamber opposite to this is shifted. The high oil chamber 17H is used for shifting to a high speed side with a small ratio. The high oil chambers 17H and the low oil chambers 17L communicate with each other.

  The mechanism for shifting the power roller 9 from the neutral position to the upshift side or the downshift side will be described. The mechanism is configured to operate an actuator such as the hydraulic cylinder 17. In the example shown in the figure, the mechanism is constituted by a duty-controlled electromagnetic valve 19. Note that this type of control valve may be provided with two valves: a valve for controlling supply / discharge of hydraulic pressure to the high oil chamber 17H and a valve for controlling supply / discharge of hydraulic pressure to the low oil chamber 17L. You may comprise so that the supply / discharge of the hydraulic_pressure | hydraulic with respect to each oil chamber 17H and 17L may be controlled simultaneously with this control valve.

  The electromagnetic valve 19 shown in the figure includes a high side port 20 communicating with the high oil chamber 17H, a low side port 21 communicating with the low oil chamber 17L, an input port 22 to which line pressure is input, and two drains. Ports 23 and 24, and a spool 27 that is moved in the axial direction by a solenoid 25 and a spring 26 disposed on the opposite side thereof to switch the communication state of these ports. The spool 27 closes the input port 22 and the drain ports 23 and 24 with respect to both the high-side port 20 and the low-side port 21, and simultaneously connects the input port 22 to the high-side port 20. An upshift state in which the low-side port 21 communicates with the drain port 24, and a downshift state in which the low-side port 21 communicates with the input port 22 and the high-side port 20 communicates with the drain port 23. It is configured to switch to.

  The shift control using the electromagnetic valve 19 is electrically executed. That is, a stroke sensor 28 is provided to detect the position of each power roller 9 as the position or displacement of the trunnion 10. As an example, the stroke sensor 28 is attached to the trunnion shaft 12 of one trunnion 10, and is configured to electrically detect the amount of displacement in the axial direction and output it as a detection signal. Here, the amount of displacement is the amount of movement in the direction of the tilting axis from the neutral position where no side slip force or tilting force acts on the power roller 9.

  In addition, a tilt angle sensor 29 is provided on any trunnion shaft 12. In the example shown in the figure, a tilt angle sensor 29 is attached to another trunnion shaft 12 on the same axis as the trunnion shaft 12 to which the stroke sensor 28 is attached. The tilt angle sensor 29 electrically detects the rotation angle of the trunnion shaft 12 and outputs a signal. For example, the rotation speed of the input disk 1 and the output disk 2 is equal, that is, the gear ratio is “ The angle of the trunnion shaft 12 in the “1” state is set to “0”, the rotation angle of the trunnion shaft 12 from this state is detected as the tilt angle, and an electrical signal corresponding to the tilt angle is output. It has become.

  Further, an input rotational speed sensor 30 that detects the rotational speed of any one of the input disks 1 and outputs an electrical signal, and an output that detects the rotational speed of any one of the output disks 2 and outputs an electrical signal. A rotation speed sensor 31 is provided. Therefore, the actual gear ratio can be obtained based on the respective rotational speeds detected by these rotational speed sensors 30 and 31.

  Each of these sensors 28, 29, 30, 31 is electrically connected to an electronic control unit (ECU) 32 for controlling the transmission ratio and the aforementioned clamping pressure. The electronic control device 32 is mainly composed of a microcomputer, and performs various calculations according to an input signal, data stored in advance and a program, and outputs a control command signal based on the calculation result. It is configured to output. The toroidal-type continuously variable transmission can be mounted on a vehicle, and in this case, the electronic control unit 32 includes an accelerator opening in addition to the signals from the sensors 28, 29, 30, 31. Various detection signals such as vehicle speed, engine speed, etc. are input.

  The torque transmission and shift by the toroidal-type continuously variable transmission will be described. When torque is input to the input disk 1 from a power source such as an engine, the power that is in contact with the input disk 1 via traction oil Torque is transmitted to the roller 9, and torque is further transmitted from the power roller 9 to the output disk 2 via traction oil. In that case, the traction oil undergoes glass transition by being pressurized, and torque is transmitted by the accompanying large shearing force, so that each disk 1, 2 seems to generate a pressure corresponding to the input torque with the power roller 9. Pressed.

  Further, since the peripheral speed of the power roller 9 and the peripheral speed at the torque transmission point of each of the disks 1 and 2 (the point where the power roller 9 is in contact via the traction oil) are substantially the same, the power roller 9 And the discs 1 and 2 according to the radius from the rotation center axis of the torque transmission point to the input disc 1 and the radius from the rotation center axis of the torque transmission point to the output disc 2. The rotation speed (rotation speed) is different, and the ratio of the rotation speed (rotation speed) becomes the gear ratio.

  The tilting of the power roller 9 that sets the gear ratio in this way is caused by moving the power roller 9 in the vertical direction in FIG. For example, when the solenoid valve 19 is controlled to supply line pressure to the high oil chamber 17H of the hydraulic cylinder 17, the left power roller 9 in FIG. 4 moves downward and the right power roller 9 in FIG. Move up. As a result, a force (side slip force) that tilts each power roller 9 is generated between the disks 1 and 2, and each power roller 9 tilts. The amount of displacement of the power roller 9 is controlled based on the deviation between the actual tilt angle and the target tilt angle. Therefore, when the power roller 9 tilts gradually and matches the target tilt angle, the power roller 9 Is returned to its neutral position and its tilting stops. As a result, a target gear ratio is set.

  The electronic control device 32 obtains a tilt angle corresponding to a target gear ratio based on a required drive amount represented by a throttle opening or the like, a vehicle speed, and the like, and a solenoid valve so as to achieve the tilt angle. A command signal is output to 19. The target tilt angle can be achieved by causing the power roller 9 to stroke with the trunnion 10, so that the offset amount of the power roller 9 is detected by the stroke sensor 28, and the deviation between the detected offset amount and the stroke command amount is detected. A command signal (for example, duty ratio) for the electromagnetic valve 19 is feedback controlled as a control deviation.

  The above basic shift control is conceptually shown in a block diagram in FIG. In FIG. 5, first, a deviation between the target tilt angle φo corresponding to the target gear ratio and the actual tilt angle φ is obtained. The calculation of the target gear ratio and the tilt angle corresponding to the target gear ratio can be performed in the same way as conventionally performed in the shift control in the toroidal type continuously variable transmission. For example, the required driving force is calculated based on the required driving amount represented by the accelerator opening and the vehicle speed, and the target output is obtained from the required driving force and the vehicle speed, and the target output is achieved with the minimum fuel consumption. The rotational speed of the internal combustion engine is obtained, and the target gear ratio and the target tilt angle φo are obtained so that the input rotational speed of the continuously variable transmission becomes a rotational speed corresponding to the rotational speed of the internal combustion engine.

  The deviation is processed with a predetermined gain K1 to obtain an offset amount X0 of the power roller 9 (for example, an offset amount from a neutral point). The deviation between the offset amount X0 and the actual offset amount X is processed by a predetermined gain K2, and a command signal (for example, duty ratio) is obtained for the solenoid valve 19, and the hydraulic pressure output by the solenoid valve 19 is obtained. When the power roller 9 is displaced and the power roller 9 is tilted accordingly, the continuously variable transmission (CVT) performs a speed change operation.

  In order to detect the actual tilt angle φ described above, the control device according to the present invention or the adjustment method according to the present invention corrects the deviation between the tilt angle sensor 29, that is, the detected value and the actual tilt angle. Do. An example of the control or adjustment method is shown in a flow chart in FIG. 1. The control or adjustment method shown here is a state in which the vehicle is not running on a vehicle equipped with the above-described toroidal continuously variable transmission, for example, the vehicle It is executed at the time of inspection before completion after delivery, at the time of inspection when the toroidal-type continuously variable transmission is mounted on the vehicle, at the time of periodic inspection of the vehicle, or in the running state.

  In FIG. 1, first, the gear ratio γ is calculated from the input rotational speed and the output rotational speed (step S1). The input rotational speed is the rotational speed detected by the input rotational speed sensor 30 described above, and the output rotational speed is the rotational speed detected by the output rotational speed sensor 31 described above. If each of these sensors 30, 31 is a sensor with low detection accuracy when the number of revolutions is low, such as a sensor composed of a pulse gear and an electromagnetic pickup, for example, detection of the number of revolutions is greater than a predetermined number of revolutions. The number of rotations is detected in a state where the disks 1 and 2 are rotated at a medium and high number of rotations so that the accuracy is sufficiently high. The medium / high rotation speed can be determined in advance according to the characteristics of the sensors 30 and 31. Further, the gear ratio γ can be obtained as a ratio between the input rotation speed and the output rotation speed.

  The control in step S <b> 1 is control for obtaining the actual tilt angle of the power roller 9. That is, since the gear ratio γ and the tilt angle φ of the power roller 9 are geometrically determined, the tilt angle φ can be obtained from the calculated gear ratio γ. Briefly explaining this, FIG. 2 schematically shows a state in which the power roller 9 is in contact with the respective disks 1 and 2 at a predetermined angle, and the gear ratio γ in the state shown in FIG. Is the ratio (= r1 / r2) of the contact point radius r1 between the input disk 1 and the power roller 9 and the contact point radius r2 between the output disk 2 and the power roller 9.

Since these contact point radii r1 and r2 are radii from the rotation center axis of the disks 1 and 2, they are expressed by the following equations.
r1 = r0 (1 + k0-cosφ)
r2 = r0 {1 + k0-cos (2θ0-φ)}
Where r0 is the radius of curvature of the toroidal surface of each of the disks 1 and 2, and k0 is the radius of curvature r0 of the distance (r0 + e0) between the axis of rotation center of each of the disks 1 and 2 and the center of curvature of the toroidal surface. The coefficient represented by the ratio (e0 / r0) to the dimension e0, θ0, is a half angle (half apex angle) of the apex angle formed by the line connecting the center of curvature of the toroidal surface and each contact point. Accordingly, the radius of curvature r0, the coefficient k0, and the half apex angle θ0 are values determined in advance as the structure of the toroidal type continuously variable transmission, so that the speed ratio γ is obtained by detecting the input speed Nin and the output speed Nout. Thus, the tilt angle φ of the power roller 9 can be calculated.

  The tilt angle sensor 29 is corrected so as to eliminate the deviation between the actual tilt angle thus obtained and the detected value of the tilt angle sensor 29 (step S2). One example is correction using the detected value of the tilt angle sensor 29 when the speed ratio γ is “1” as a zero point. In another example, the speed ratio γ is set to the maximum value γmax, the actual tilt angle in that state is calculated by the above relational expression, and the deviation between the value and the detected value of the tilt angle sensor 29 is calculated. Then, the tilt angle sensor 29 is calibrated or the detection value of the tilt angle sensor 29 is corrected.

  Shift control is executed using the detected value of the tilt angle sensor 29 corrected in this way (step S3). In other words, the shift control is performed based on the detected value of the tilt angle sensor 29 based on the sensor zero point calibrated as described above. Specifically, the target offset amount X0 of the power roller 9 is obtained by multiplying the deviation between the target tilt angle φ0 and the tilt angle φ detected by the tilt angle sensor 29 by a control gain, and the target offset amount X0 is obtained. The hydraulic control command value for controlling the hydraulic cylinder 17 by multiplying the deviation between the actual offset amount X and another control gain, that is, the duty command value for the electromagnetic valve 19, is obtained. Be controlled.

  Therefore, once the tilt angle sensor 29 is calibrated or the detected value is corrected as described above, there is no deviation between the detected value and the actual tilt angle, and the actual tilt angle of the power roller 9 is reduced. It can be detected accurately. Therefore, for example, even if the detection accuracy of at least one of the input rotation speed sensor 30 and the output rotation speed sensor 31 is low due to the low vehicle speed, the actual inclination angle or Since the speed ratio can be obtained, the speed ratio can be accurately controlled without causing a shift in the speed ratio. For example, it is possible to avoid a situation in which the gear ratio gradually changes when traveling at a low speed.

  Here, the relationship between the above-described specific example and the present invention will be briefly described. The functional means of step S1 and step S2 shown in FIG. 1 correspond to the correction means of the present invention. Since the rotation angle is calculated, this corresponds to the tilt angle calculation means of the present invention, and the functional means of step S3 corresponds to the transmission ratio control means of the present invention.

It is a flowchart for demonstrating an example of the calibration control of the tilt angle sensor performed with the control apparatus which concerns on this invention. It is a figure which shows typically the relationship between each dimension and angle in the state which the power roller inclines. It is a figure which shows typically an example of the toroidal type continuously variable transmission made into object by this invention. It is typical sectional drawing which shows the state which cut | disconnected one cavity of the toroidal type continuously variable transmission by the plane which passes through the center part. It is a control block diagram for demonstrating an example of basic shift control by the transmission which concerns on this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Input disc, 2 ... Output disc, 3 ... Output gear, 4 ... Input shaft, 9 ... Power roller, 10 ... Trunnion, 12 ... Trunnion shaft, 17 ... Hydraulic cylinder, 19 ... Solenoid valve, 29 ... Tilt angle sensor 30... Input rotational speed sensor 31... Output rotational speed sensor 32.

Claims (4)

The radius of the contact point between the power roller sandwiched between the pair of disks and one of the disks from the rotation center axis of the disk and the rotation center axis of the disk at the contact point between the power roller and the other disk In a control device for a toroidal continuously variable transmission that sets a transmission ratio according to a ratio of a radius from and changes the radius of each contact point by tilting the power roller, and executes a shift.
A tilt angle sensor connected to a holding member holding the power roller and detecting a tilt angle of the holding member;
A control device for a toroidal-type continuously variable transmission, comprising correction means for correcting a deviation between a detected value of the tilt angle sensor and an actual tilt angle.   2. The control device for a toroidal continuously variable transmission according to claim 1, further comprising a tilt angle calculating means for determining the actual tilt angle based on the number of rotations of each disk.   The gear ratio control means for controlling the gear ratio based on a detection value of the tilt angle sensor after the deviation is corrected by the correction means. Toroidal continuously variable transmission control device. The radius of the contact point between the power roller sandwiched between the pair of disks and one of the disks from the rotation center axis of the disk and the rotation center axis of the disk at the contact point between the power roller and the other disk In the adjustment method of the toroidal continuously variable transmission, the gear ratio is set according to the ratio of the radii from and the power roller is tilted to change the radius of each of the contact points to execute the shift.
Each disk is rotated at a rotational speed equal to or higher than a predetermined rotational speed, and the tilt angle of the power roller is calculated based on the rotational speed of each disk in this state, and the calculated tilt angle and the power roller are calculated. A toroidal type characterized in that a deviation from a detected value of a tilt angle sensor that detects a tilt angle of a holding member that holds the tilt angle is obtained, and the detected value of the tilt angle is corrected so as to eliminate the deviation Adjustment method for continuously variable transmission.

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