JP2012211612A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To perform the pressing control of the adequate magnitude by improving inconveniences of a conventional example.SOLUTION: This continuously variable transmission includes first and second rotating members 10, 20, a planetary ball 30 held by the first and second rotating members 10, 20, a speed change device for changing the speed by the tilting operation of the planetary ball 30, a pressing device 70 for outputting the pressure for generating the pressing load from the first rotating member 10 to the planetary ball 30 and the pressing load from the second rotating member 20 to the planetary ball 30, and a temperature sensor 81 arranged so as to detect at least any one of the temperature on the reference rolling track between the first rotating member 10 and the planetary ball 30, and the temperature on the reference rolling track between the second rotating member 20 and the planetary ball 30. The elastic deformation amounts of the first rotating member 10, the second rotating member 20, and the planetary ball 30 caused by the pressure of the pressing device 70 are calculated. The temperature on the actual rolling track is estimated by correcting the detected temperature based on the elastic deformation amounts. The pressure of the pressing device 70 is controlled based on the estimated temperature of the actual rolling track.

Description

  The present invention includes first and second rotation elements having a common first rotation center axis, and third rotation elements having a plurality of second rotation center axes arranged radially with respect to the first rotation center axis, The rotation ratio between the first rotation element and the second rotation element is steplessly changed by tilting each third rotation element sandwiched between the first rotation element and the second rotation element. The present invention relates to a continuously variable transmission.

  Conventionally, this type of traction drive type continuously variable transmission is known. Specifically, a toroidal continuously variable transmission including an input disk as a first rotating element, an output disk as a second rotating element, and a power roller as a third rotating element is known. . Further, for this type of continuously variable transmission, a transmission shaft concentric with the first rotation center shaft, a first rotation member (first disk or first ring) as a first rotation element, and a second rotation element A second rotating member (second disk or second ring), a rolling member (planetary ball) as a third rotating element, and a fourth rotating element (sun roller) in which each planetary ball is disposed on the outer peripheral surface. There is known one provided with a so-called traction planetary gear mechanism having a fixing element (carrier) fixed to a transmission shaft and holding each planetary ball.

  Here, the former toroidal continuously variable transmission is disclosed in the following Patent Documents 1-4.

  Japanese Patent Application Laid-Open No. 2004-133260 describes a technique for detecting a temperature in the vicinity of a contact portion between an input / output disk and a power roller (rolling surface temperature of the power roller) using a temperature sensor provided on the rolling surface of the power roller. In the continuously variable transmission described in Patent Document 1, the temperature near the contact portion between the first input disk and the first output disk and the first power roller, the first input disk, the first output disk, and the second power roller, Of the contact area between the second input disk, the second output disk, and the third power roller, and the contact area temperature between the second input disk, the second output disk, and the fourth power roller. When the difference between the two temperatures is equal to or greater than a predetermined value, it is determined that the traction coefficient is in the vicinity of the maximum value, and the determination result is used for pinching control.

  Patent Document 2 describes a technique in which a tilt angle sensor for detecting the tilt angle of a power roller is provided for each power roller. In the continuously variable transmission described in Patent Document 2, the tilt angle sensor is disposed between the trunnion and the swing frame, and if any of the tilt angle sensors is abnormal, Gear ratio control is performed using the detected value of the normal tilt angle sensor. Further, Patent Document 3 obtains the displacement amount and displacement direction of the component based on the magnitude and direction of the torque passing through the transmission, and switches between the high speed clutch and the low speed clutch based on the displacement amount and displacement direction. A technique for correcting the time is described. Patent Document 4 describes a temperature sensor that detects an oil temperature in the vicinity of a contact portion between an input disk and a power roller.

  Further, the continuously variable transmission including the latter traction planetary gear mechanism is disclosed in Patent Document 5 below.

JP 2005-344867 A JP 2005-233377 A JP 2004-116576 A JP 2007-107626 A US Patent Application Publication No. 2010/0267510

  By the way, in this type of continuously variable transmission, an axial pressing force (clamping pressure) for pressing the first rotating element and the second rotating element against the third rotating element is generated. For this reason, in the contact portion between the first and second rotating elements and the third rotating element, the respective rotating elements are elastically deformed by the pressing load due to the pressing force. Therefore, in the conventional continuously variable transmission, the measurement position of the temperature sensor shifts due to the elastic deformation, and the detected value of the temperature of the contact portion also shifts with the shift. May not be output, and spin loss and gloss slip may occur.

  Therefore, an object of the present invention is to provide a continuously variable transmission that improves the disadvantages of the conventional example and enables a pressure control of an appropriate size.

  In order to achieve the above object, the present invention provides a first and a second rotating element having a common first rotation center axis arranged opposite to each other and capable of relative rotation, and the same plane as the first rotation center axis. A third rotation element having a second rotation center axis disposed and sandwiched between the first and second rotation elements, and a rotation ratio between the first rotation element and the second rotation element; A transmission device that is changed by a tilting operation of the third rotating element, and a pressing load from the first rotating element to the third rotating element and a pressing load from the second rotating element to the third rotating element. A pressing device that outputs a pressing force of the first rotation element, a temperature on a reference rolling path between the first rotation element and the third rotation element, or a reference rotation between the second rotation element and the third rotation element. Temperature detector arranged to detect at least one of the temperatures on the running track , Comprising a. And the amount of elastic deformation of the first rotating element, the second rotating element and the third rotating element generated according to the pressing force of the pressing device is calculated, and the temperature detecting device is based on the calculated amount of elastic deformation By correcting the temperature detected by the above, the temperature on the actual rolling track is estimated, and the pressing force of the pressing device is controlled based on the estimated temperature on the actual rolling track.

  Here, when the temperature on the actual rolling track is estimated, a shift amount between the position of the detection unit of the temperature detection device and the actual rolling track is calculated based on the elastic deformation amount, and the shift amount Accordingly, it is desirable to correct the temperature detected by the temperature detection device.

  In the continuously variable transmission according to the present invention, the amount of elastic deformation of the first rotating element, the second rotating element, and the third rotating element is taken into account, and the difference between the position of the detection unit of the temperature detecting device and the actual rolling track is reduced. The detected temperature deviation is corrected. For this reason, in this continuously variable transmission, the target pressing force of the pressing device can be set to an optimal size without excess or deficiency, and between the first and second rotating elements and the third rotating element. Optimal pressing load without excess or deficiency can be applied. Therefore, this continuously variable transmission can generate a tangential force with an optimal magnitude that suppresses spin loss and gloss slip at the contact portion between them, so that torque transmission efficiency and durability can be improved. It becomes possible.

FIG. 1 is a partial cross-sectional view showing a configuration of a first embodiment of a continuously variable transmission according to the present invention. FIG. 2 is a cross-sectional view taken along line XX or YY in FIG. 1 and is a view showing an example of the arrangement and attachment of the temperature sensor. FIG. 3 is a cross-sectional view taken along line XX or YY in FIG. 1 and is a view showing another example of the arrangement and attachment of the temperature sensor. FIG. 4 is a cross-sectional view taken along line XX or YY in FIG. 1 and is a view showing another example of the arrangement and attachment of the temperature sensor. FIG. 5 is a diagram illustrating elastic deformation of the continuously variable transmission according to the first embodiment. FIG. 6 is a diagram for explaining the relationship between the positional deviation amount of the temperature sensor and the rolling contact surface temperature. FIG. 7 is a flowchart for explaining the pressing control operation of the continuously variable transmission according to the present invention. FIG. 8 is a diagram showing a configuration of a continuously variable transmission according to a second embodiment of the present invention. FIG. 9 is a diagram illustrating the trunnion. 10 is a cross-sectional view taken along line ZZ in FIG. FIG. 11 is a diagram illustrating an example of the arrangement of the temperature sensor according to the second embodiment. FIG. 12 is a diagram illustrating another example of the arrangement of the temperature sensor according to the second embodiment. FIG. 13 is a diagram illustrating elastic deformation of the continuously variable transmission according to the second embodiment.

  Embodiments of a continuously variable transmission according to the present invention will be described below in detail with reference to the drawings. The present invention is not limited to the embodiments.

[Example 1]
A first embodiment of a continuously variable transmission according to the present invention will be described with reference to FIGS.

  First, an example of a continuously variable transmission according to the present embodiment will be described with reference to FIG. Reference numeral 1 in FIG. 1 indicates a continuously variable transmission according to this embodiment.

  The continuously variable transmission mechanism constituting the main part of the continuously variable transmission 1 includes first to fourth rotating elements 10, 20, 30, 40, a shaft 50 as a transmission shaft, and a fixed element 60. This is a so-called traction planetary gear mechanism. The first, second, and fourth rotating elements 10, 20, and 40 have a common first rotation center axis R1, and are mutually centered around a shaft 50 that is concentric with the first rotation center axis R1. Relative rotation is possible. The third rotation element 30 has a second rotation center axis R2 disposed on the same plane as the first rotation center axis R1, and rotates about the second rotation center axis R2. The second rotation center axis R2 is parallel to the first rotation center axis R1 at a reference position described later. A plurality of third rotating elements 30 are arranged radially around the shaft 50 and are sandwiched between the first rotating element 10 and the second rotating element 20. The 4th rotation element 40 has arrange | positioned each 3rd rotation element 30 on the outer peripheral surface. The shaft 50 is fixed to a fixed portion of the continuously variable transmission 1 in a housing or a vehicle body (not shown), and is a columnar fixed shaft configured not to rotate relative to the fixed portion. The fixing element 60 is fixed to the shaft 50 and holds each third rotating element 30 in a tiltable manner.

  The continuously variable transmission 1 changes the gear ratio between input and output by inclining the second rotation center axis R2 with respect to the first rotation center axis R1 and tilting the third rotation element 30. . In the following, unless otherwise specified, the direction along the first rotation center axis R1 is referred to as an axial direction, and the direction around the first rotation center axis R1 is referred to as a circumferential direction. Further, the direction orthogonal to the first rotation center axis R1 is referred to as a radial direction, and among these, the inward side is referred to as a radial inner side, and the outward side is referred to as a radial outer side.

  In the continuously variable transmission 1, torque is transmitted between the first rotating element 10, the second rotating element 20, and the fourth rotating element 40 via the third rotating elements 30. For example, in the continuously variable transmission 1, one of the first, second, and fourth rotating elements 10, 20, and 40 serves as a torque (power) input unit, and at least one of the remaining rotating elements. This is the torque output section. For this reason, in this continuously variable transmission 1, the ratio of the rotation speed (the number of rotations) between any rotation element serving as the input unit and any rotation element serving as the output unit is the gear ratio. For example, the continuously variable transmission 1 is disposed on the power transmission path of the vehicle. In that case, the input part is connected with the power source side, such as an engine and a motor, and the output part is connected with the drive wheel side.

  The continuously variable transmission 1 presses at least one of the first and second rotating elements 10, 20 against the third rotating element 30, whereby the first, second, and fourth rotating elements 10, 20, Appropriate tangential force (traction force) is generated between 40 and the third rotating element 30, and torque can be transmitted between them. Further, the continuously variable transmission 1 tilts each third rotation element 30 on a tilt plane including its second rotation center axis R2 and its first rotation center axis R1, and thereby the first rotation element 10 The ratio of the rotational speed (rotational speed) between the input and output is changed by changing the ratio of the rotational speed (rotational speed) between the first rotating element 20 and the second rotational element 20.

  Here, in the continuously variable transmission 1, the first and second rotating elements 10 and 20 function as a ring gear as a planetary gear mechanism. The third rotating element 30 functions as a ball type pinion of the traction planetary gear mechanism. The fourth rotating element 40 functions as a sun roller of the traction planetary gear mechanism. The fixing element 60 functions as a carrier for the traction planetary gear mechanism. Hereinafter, the first and second rotating elements 10 and 20 are referred to as “first and second rotating members 10 and 20”, respectively. The third rotating element 30 is referred to as “planetary ball 30”, and the fourth rotating element 40 is referred to as “sun roller 40”. The fixing element 60 is referred to as a “carrier 60”.

  The first and second rotating members 10 and 20 are disk members (disks) or ring members (rings) whose center axes coincide with the first rotation center axis R1, and each planetary ball is opposed in the axial direction. 30 is interposed. In this example, both are circular members.

  Each of the first and second rotating members 10 and 20 has a contact surface that comes into contact with an outer peripheral curved surface on the radially outer side of each planetary ball 30 described in detail later. Each of the contact surfaces has, for example, a concave arc surface having a curvature equivalent to the curvature of the outer peripheral curved surface of the planetary ball 30, a concave arc surface having a curvature different from the curvature of the outer peripheral curved surface, a convex arc surface, or a flat surface. is doing. Here, the first and second contact surfaces are formed such that the distance from the first rotation center axis R1 to the contact portion with each planetary ball 30 is the same length in the state of a reference position described later. The contact angles θ of the rotating members 10 and 20 with respect to the planetary balls 30 are set to the same angle. The contact angle θ is an angle from the reference to the contact portion with each planetary ball 30. Here, the radial direction is used as a reference. The respective contact surfaces are in point contact or surface contact with the outer peripheral curved surface of the planetary ball 30. Each contact surface is radially inward with respect to the planetary ball 30 when an axial force (pressing force) is applied from the first and second rotating members 10, 20 toward the planetary ball 30. And an oblique pressing load (normal force) is applied.

  In this illustration, the input shaft 11 is connected to the first rotating member 10, and the output shaft 21 is connected to the second rotating member 20.

  The continuously variable transmission 1 is provided with a pressing device 70 that generates the pressing force described above. The pressing device 70 generates a pressing force from the first rotating member 10 toward the planetary ball 30, generates a pressing force from the second rotating member 20 toward the planetary ball 30, and each pressing force thereof. Any of those generated may be used. For example, the illustrated pressing device 70 is configured to increase or decrease the hydraulic pressure of the hydraulic chamber provided on the back side (the side opposite to the planetary ball 30) of the first rotating member 10 or the input shaft 11 with the pressing control device. A target pressing force from the rotating member 10 toward the planetary ball 30 is generated. The pressing control device is prepared as one of arithmetic processing functions of the electronic control unit ECU.

  The planetary ball 30 is a rolling member that rolls on the outer peripheral surface of the sun roller 40. The planetary ball 30 is preferably a perfect sphere, but it may have a spherical shape at least in the rolling direction, for example, a rugby ball having an elliptical cross section. The planetary ball 30 is rotatably supported by a support shaft 31 that passes through the center of the planetary ball 30. For example, the planetary ball 30 can be rotated relative to the support shaft 31 with the second rotation center axis R2 as a rotation axis (that is, rotation) by a bearing (not shown) disposed between the outer periphery of the support shaft 31. . Accordingly, the planetary ball 30 can roll on the outer peripheral surface of the sun roller 40 around the support shaft 31. Both ends of the support shaft 31 are projected from the planetary ball 30.

  The reference position of the support shaft 31 is a position where the second rotation center axis R2 is parallel to the first rotation center axis R1, as shown in FIG. The support shaft 31 is the same plane (hereinafter referred to as “tilt plane”) including its own rotation center axis (second rotation center axis R2) and the first rotation center axis R1 formed at the reference position. In the inside, it can rock | fluctuate (tilt) with the planetary ball 30 between the reference position and the position inclined from there. The tilt is performed with the center of the planetary ball 30 as a fulcrum in the tilt plane.

  The sun roller 40 has a cylindrical shape with a central axis coinciding with the first rotation central axis R1, and a plurality of planetary balls 30 are radially arranged on the outer peripheral surface at substantially equal intervals. In the sun roller 40, the outer peripheral surface becomes a rolling surface when the planetary ball 30 rotates.

  The carrier 60 holds each protrusion of the support shaft 31 so as not to prevent the tilting movement of each planetary ball 30. In this carrier 60, for example, first and second disk members 61 and 62 having a center axis coinciding with the first rotation center axis R1 are arranged to face each other, and the first and second disk members 61 and 62 are opposed to each other. Are connected by a plurality of connecting shafts 63 (FIG. 2) to form a bowl shape as a whole. As a result, the carrier 60 has an open portion on the outer peripheral surface. Each planetary ball 30 is disposed between the first and second disk members 61 and 62 and is in contact with the first rotating member 10 and the second rotating member 20 through the open portion.

  The carrier 60 fixes the inner peripheral surface side of the first and second disk members 61 and 62 to the outer peripheral surface side of the shaft 50, and relative rotation in the circumferential direction and relative movement in the axial direction with respect to the shaft 50 are performed. I can't do it. For example, the carrier 60 can inhibit such relative rotation in the circumferential direction by spline fitting the inner peripheral surfaces of the first and second disk members 61 and 62 with the outer peripheral surface of the shaft 50. .

  The continuously variable transmission 1 is provided with a guide portion for guiding the support shaft 31 in the tilting direction when each planetary ball 30 tilts. In this example, the guide portion is provided on the carrier 60. The guide portions are radial guide grooves 64 and 65 for guiding the support shaft 31 protruding from the planetary ball 30 in the tilt direction, and the first and second disk members 61 and 62 are opposed to each other. A portion is formed for each planetary ball 30 (FIG. 2). That is, all the guide grooves 64 and all the guide grooves 65 are radial when viewed from the axial direction.

  In this continuously variable transmission 1, when the tilt angle of each planetary ball 30 is the reference position, that is, 0 degrees, the first rotating member 10 and the second rotating member 20 have the same rotational speed (the same rotational speed). Rotate with. That is, at this time, the rotation ratio (ratio of rotation speed or rotation speed) between the first rotation member 10 and the second rotation member 20 is 1, and the speed ratio γ is 1. On the other hand, when each planetary ball 30 is tilted from the reference position, the distance from the central axis of the support shaft 31 to the contact portion with the first rotating member 10 changes and from the central axis of the support shaft 31. The distance to the contact portion with the second rotating member 20 changes. Therefore, one of the first rotating member 10 and the second rotating member 20 rotates at a higher speed than when it is at the reference position, and the other rotates at a lower speed. For example, the second rotating member 20 has a lower rotation (deceleration) than the first rotating member 10 when the planetary ball 30 is tilted in one direction, and the first rotating member 10 is tilted in the other direction. (High speed). Therefore, in the continuously variable transmission 1, the rotation ratio (speed ratio γ) between the first rotating member 10 and the second rotating member 20 can be changed steplessly by changing the tilt angle. it can. When the speed is increased (γ <1), the upper planetary ball 30 in FIG. 1 is tilted in the clockwise direction on the paper and the lower planetary ball 30 is tilted in the counterclockwise direction on the paper. . Further, at the time of deceleration (γ> 1), the upper planetary ball 30 in FIG. 1 is tilted counterclockwise on the paper surface and the lower planetary ball 30 is tilted clockwise on the paper surface.

  The continuously variable transmission 1 is provided with a transmission (not shown) that changes the speed ratio γ. Since the gear ratio γ changes as the tilt angle of the planetary ball 30 changes, a tilting device that tilts each planetary ball 30 is used as the speed change device. As this transmission, one known in this technical field is used. For example, the transmission is configured by a support member having a radial direction in the longitudinal direction attached to one end of the extended support shaft 31 and an actuator that applies a radial force to the support member. Things can be considered. This transmission device tilts the planetary ball 30 via the support shaft 31 by moving the support member in the radial direction.

  By the way, the target pressing force of the pressing device 70 described above is a target value of the magnitude of the pressing load Fn in the normal direction from the first and second rotating members 10 and 20 to the planetary ball 30 (hereinafter referred to as “target pressing load”). It is determined according to Fn0 and the geometric conditions of the continuously variable transmission 1. The geometric condition is a contact angle θ or the like, and is one piece of specification information of the continuously variable transmission 1. The target pressing load Fn0 is calculated from the target traction force Ft0 and the traction coefficient μ (Fn = Ft / μ). The target traction force Ft0 is determined by the output torque of the power source (input torque to the continuously variable transmission 1) or the like. Further, the traction coefficient μ is determined by a contact portion (input-side contact portion) between the first rotating member 10 and the planetary ball 30 or a contact portion (output-side contact) between the second rotating member 20 and the planetary ball 30. Part) is determined by the surface pressure, slip rate, temperature, and the like. That is, when the pressing control device sets the target pressing force of the pressing device 70, the traction coefficient μ is obtained based on the temperature of the contact portion, and the target pressing load Fn0 is obtained from the traction coefficient μ and the target traction force Ft0. Ask. The electronic control unit ECU calculates the target pressing force based on the target pressing load Fn0 and the geometric condition of the continuously variable transmission 1.

  These calculations are well known in the technical field of this type of traction drive device. However, in the calculation, the temperature of the contact portion uses the oil temperature of the lubricating oil in the vicinity of the contact portion, and there is a deviation from the actual temperature. For this reason, in this embodiment, as the temperature of the contact portion, the temperature on the rolling orbit between the first rotating member 10 and the planetary ball 30 or the rotation between the second rotating member 20 and the planetary ball 30 is used. Use the temperature on the running track. That is, when the electronic control unit ECU sets the target pressing force of the pressing device 70, the temperature on the rolling path between the first rotating member 10 and the planetary ball 30 or the second rotating member 20 and the planetary ball 30. At least one of the temperatures on the rolling trajectory between and is used.

  The temperature of the contact portion on the input side is the temperature on the rolling path between the first rotating member 10 and the planetary ball 30, and the rolling surface between the first rotating member 10 and the planetary ball 30. Or the temperature of the rolling surface between the planetary ball 30 and the first rotating member 10 is measured. Further, the temperature of the contact portion on the output side is the temperature on the rolling orbit between the second rotating member 20 and the planetary ball 30, and the rolling between the planetary ball 30 in the second rotating member 20 is the same. The temperature of the running surface or the temperature of the rolling surface between the planetary balls 30 and the second rotating member 20 is measured. In order to measure the temperature of the rolling surface (hereinafter also referred to as “rolling surface temperature”), the continuously variable transmission 1 is provided with a temperature detection device having a temperature sensor 81. The temperature sensor 81 may be provided for at least one planetary ball 30.

  2 and 3, temperature sensors 81 are respectively provided on the rolling surface between the planetary ball 30 and the first rotating member 10 and the rolling surface between the planetary ball 30 and the second rotating member 20. The case where it provided is illustrated. 2 and 3 are sectional views taken along lines XX and YY in FIG. 2 has a holding member 82 fixed to the connecting shaft 63 of the carrier 60, and the holding member 82 holds the temperature sensor 81. 3 includes a holding member 82 fixed to the inner wall surface of the casing Ca of the continuously variable transmission 1, and the holding member 82 holds the temperature sensor 81. The temperature sensor 81 is preferably attached to a member that does not rotate or move relative to the shaft 50.

  The temperature sensor 81 takes into account, for example, the rotation direction when torque is input from the power source, and the temperature immediately after passing through the contact portion of the rolling surface of the planetary ball 30 with the first rotating member 10 or the second rotating member 20 is It is desirable to place it where it is detected. This is because the value closest to the temperature of the contact portion can be detected, so that the estimation accuracy of the traction coefficient μ is improved. Here, in the case where only one planetary ball 30 is provided, the temperature sensor 81 is provided at a place where the temperature immediately after passing through the contact portion with the first rotation member 10 and the contact portion with the second rotation member 20 is detected. Each is preferably arranged. However, in this case, since the detected temperature of one contact portion may change due to the temperature of the other contact portion, when detecting the temperatures of the input side and the output side, two or more planetary balls 30 are detected. On the other hand, it is preferable to arrange the temperature sensors 81 separately on the input side and the output side one by one.

  Further, when the temperature sensors 81 are provided for the plurality of planetary balls 30, for example, a priority order may be given as to which temperature sensor 81 is used for calculating the traction coefficient μ. For example, in a plurality of temperature sensors 81 provided on the input side (or output side), the detected temperature of the temperature sensor 81 on the input side (or output side) with the highest priority is the other plurality of input sides (or output sides). The temperature detected by the temperature sensor 81 on the second input side (or output side) having the second priority is used for the calculation of the traction coefficient μ.

  Further, in FIG. 4, temperature sensors 81 are respectively provided on the rolling surface between the first rotating member 10 and the planetary ball 30 and the rolling surface between the second rotating member 20 and the planetary ball 30. The case is shown as an example. 4 is a cross-sectional view taken along line XX and line YY in FIG. The temperature sensor 81 is a planetary ball on the rolling surface of the first rotating member 10 or the second rotating member 20 in consideration of, for example, the rotation direction when torque is input from a power source, as illustrated in FIGS. It is desirable that a value closest to the temperature of the contact portion is detected by disposing it at a location where the temperature immediately after passing through the contact portion with 30 is detected. The temperature sensor 81 may be provided for at least one planetary ball 30. The temperature sensor 81 is preferably attached to a member that does not rotate or move relative to the shaft 50 in the same manner as illustrated in FIGS. 4 includes a holding member 82 fixed to the connecting shaft 63 of the carrier 60, and the holding member 82 holds the temperature sensor 81.

  Thus, the temperature sensor 81 detects the rolling surface temperature of the first rotating member 10 and the second rotating member 20 and the rolling surface temperature of the planetary ball 30. For this reason, when calculating the target pressing force of the pressing device 70, the accuracy of the calculation result is increased by using the rolling contact surface temperature rather than replacing with the oil temperature of the lubricating oil.

  However, between the first and second rotating members 10 and 20 and the planetary ball 30, as shown in FIG. 5, the first and second rotating members 10 and 20 and the planetary ball 30 are caused by the pressing load Fn. It is elastically deformed and the trajectory of the rolling track changes. Therefore, at this time, a deviation occurs between the position of the detection portion of the temperature sensor 81 (hereinafter referred to as “sensor position”) arranged in accordance with the rolling trajectory before the change and the actual rolling trajectory. There is a possibility that. Since the difference may cause a difference between the temperature detected by the temperature sensor 81 and the actual temperature on the rolling track, the target pressing force of the pressing device 70 increases as the difference increases. In other words, the greater the amount of elastic deformation, the lower the accuracy of the calculation result.

  Therefore, in this embodiment, the temperature detected by the temperature sensor 81 is corrected in accordance with the amount of elastic deformation to obtain the rolling surface temperature on the actual rolling track, and this actual rolling surface temperature (temperature The target pressing force is calculated based on the temperature correction value detected by the sensor 81.

  First, here, an ideal rolling trajectory before elastic deformation that becomes a detection position by the temperature sensor 81 is referred to as a “reference rolling trajectory”, and the actual rolling trajectory after the elastic deformation described above. This is called “actual rolling track”. Therefore, an ideal rolling surface on the reference rolling track is a “reference rolling surface”, and a rolling surface on the actual rolling track is an “real rolling surface”.

  The pressing control device calculates the target pressing load Fn0. In this calculation, the temperature detected by the temperature sensor 81 is used. The target pressing load Fn0 is a control target value before the first and second rotating members 10 and 20 and the planetary ball 30 are elastically deformed, and is a provisional value. Therefore, in the following, the target pressing load is referred to as “temporary target pressing load”. The provisional target pressing load corresponds to the conventional target pressing load, and is calculated by the same calculation process as the conventional target pressing load.

  The first and second rotating members 10 and 20 and the planetary ball 30 are elastically deformed by performing pressing control with the provisional target pressing load. The amount of deviation between the sensor position of the temperature sensor 81 and the actual rolling trajectory at this time (hereinafter referred to as “sensor deviation amount”) is that of the first and second rotating members 10 and 20 and the planetary ball 30. It depends on the state of each elastic deformation. Here, the state of elastic deformation can be expressed by the amount of elastic deformation in the axial direction or radial direction, for example. In this embodiment, the amount of elastic deformation of the first and second rotating members 10 and 20 and the planetary ball 30 (an estimated value corresponding to actual measurement if the pressure control is actually executed, the pressure control is actually executed). If not, an elastic deformation amount calculation device capable of calculating an axial direction component and a radial direction component in an estimated value when it is assumed to be executed is provided. The elastic deformation amount calculation device is prepared as one of the arithmetic processing functions of the electronic control unit ECU.

  Here, the amount of elastic deformation includes the provisional target pressing load and the specification information of the continuously variable transmission 1 (geometric conditions, gear ratio γ, first and second rotating members 10 and 20, and the material of the planetary ball 30). Etc.) and the like. Since the specification information of the continuously variable transmission 1 can be grasped in advance, the elastic deformation amount calculation device includes, for example, the elastic deformation amounts of the first and second rotating members 10 and 20 and the planetary ball 30 with respect to the provisional target pressing load. By preparing the map in advance, each elastic deformation amount may be calculated based on the map and the provisional target pressing load. For example, each map shows an axial direction component and a radial direction component of the elastic deformation amount. The elastic deformation amount may be obtained from the detection values of the strain sensors provided on the first and second rotating members 10 and 20 and the planetary ball 30.

  From the axial direction component and the radial direction component of the elastic deformation amount of the first and second rotating members 10 and 20 and the planetary ball 30, the state of the respective elastic deformation can be known, and experiments and simulations are performed in advance. Thus, the position of the actual rolling surface, that is, the sensor deviation amount can be estimated. Therefore, the temperature estimation device is caused to obtain the sensor deviation amount based on the axial direction component and the radial direction component of the elastic deformation amount. Here, the sensor deviation amount may be obtained from the axial direction component and the radial direction component of the elastic deformation amount of the first rotating member 10, the second rotating member 20, or the planetary ball 30 in contact with the temperature sensor 81. . In the temperature estimation device, a map of sensor deviation amounts with respect to the axial direction component and the radial direction component of the elastic deformation amount is prepared in advance, and based on the map and the axial direction component and the radial direction component of the elastic deformation amount. Then, the sensor deviation amount may be calculated. Here, the temperature estimation device is prepared as one of the arithmetic processing functions of the electronic control unit ECU.

  On the other hand, the actual rolling surface and the temperature distribution near the actual rolling surface can be grasped in advance by experiments and simulations. For example, as shown in FIG. 6, this temperature distribution is from the actual rolling surface on the surface of the first rotating member 10, the second rotating member 20, and the planetary ball 30 with the actual rolling surface at the maximum temperature as a boundary. The temperature decreases as the distance increases. In the temperature distribution of FIG. 6, the horizontal axis represents distance, and the vertical axis represents temperature. As for the temperature reduction margin with respect to the distance from the actual rolling surface, the tendency is almost the same regardless of the level of the rolling surface temperature of the actual rolling surface. Therefore, on the horizontal axis, the sensor deviation amount starting from the position of the actual rolling surface can be expressed, and the sensor position on the temperature distribution can be known. On the vertical axis, the temperature that intersects the sensor position and the temperature distribution can be expressed as the temperature detected by the temperature sensor 81. In this temperature distribution, the difference between the detected temperature and the rolling contact surface temperature is the temperature correction amount. Therefore, the temperature estimation device estimates the rolling surface temperature of the actual rolling surface by adding the correction amount to the temperature detected by the temperature sensor 81.

  In the continuously variable transmission 1, the target pressing force of the pressing device 70 is obtained based on the estimated rolling surface temperature of the actual rolling surface, and the pressing control is performed so that the target pressing force is output. Hereinafter, the calculation processing operation at the time of the pressure control will be described based on the flowchart of FIG. When the above-described priority is set for the temperature detected by the temperature sensor 81, the detection temperature of the temperature sensor 81 used for the following calculation processing is determined based on the priority.

  First, the electronic control unit ECU acquires calculation conditions (step ST1). The calculation conditions include specification information of the continuously variable transmission 1, input torque to the continuously variable transmission 1 (output torque of the power source), speed ratio γ of the continuously variable transmission 1, and temperature detected by the temperature sensor 81. Etc. Since the specification information of the continuously variable transmission 1 is an invariable value, it is stored in advance in, for example, a storage device of the electronic control unit ECU. The input torque to the continuously variable transmission 1 can be obtained from an output control signal of the power source. The speed ratio γ can be obtained from a speed change control signal to the continuously variable transmission 1 or the like.

  The electronic control unit ECU obtains a provisional target pressing load based on the obtained calculation condition (step ST2), and the first and second rotating members 10 and 20 and the planets when the pressure is controlled by the provisional target pressing load. The elastic deformation amount of the ball 30 is obtained (step ST3). Then, the electronic control unit ECU obtains a temperature correction amount for the temperature detected by the temperature sensor 81 based on the elastic deformation amount (step ST4).

  In step ST4, as described above, the first rotation member 10, the second rotation member 20, or the planetary ball 30 is in contact with the temperature sensor 81, but according to the axial direction component and the radial direction component of the elastic deformation amount. Obtain the sensor deviation. For example, in the illustration of FIG. 2 and FIG. 3, by comparing the axial direction component and the radial direction component of the elastic deformation amount of the planetary ball 30 with which the temperature sensor 81 is in contact with the above map, Each sensor deviation amount on the second rotating member 20 side is obtained. Moreover, in the illustration of FIG. 4, by comparing the axial direction component and the radial direction component of the elastic deformation amount of each of the first rotating member 10 and the second rotating member 20 with the above map, Each sensor deviation amount on the second rotating member 20 side is obtained. In step ST4, the temperature corresponding to the sensor position of the temperature sensor 81 on the map (temperature distribution) is obtained by comparing the sensor deviation amount with the map corresponding to the temperature distribution in FIG. In this step ST4, a difference between the temperature and the rolling surface temperature on the map (temperature distribution) is obtained, and this difference is set as a temperature correction amount. Here, the temperature correction amount between the first rotating member 10 and the planetary ball 30 and the temperature correction amount between the second rotating member 20 and the planetary ball 30 are obtained.

  The electronic control unit ECU estimates the rolling surface temperature on the actual rolling track based on the temperature correction amount and the temperature detected by the temperature sensor 81 (step ST5). In this step ST5, the temperature correction amount is added to the temperature detected by the temperature sensor 81, so that the added value becomes the rolling surface temperature of the actual rolling surface.

  The electronic control unit ECU performs the second rotation between the first rotating member 10 and the planetary ball 30 based on the estimated rolling surface temperature on the actual rolling track, the slip ratio of the corresponding contact portion, and the like. A traction coefficient μ between the member 20 and the planetary ball 30 is obtained (step ST6).

  Based on the traction coefficient μ and the target traction force Ft0, the electronic control unit ECU sets the target pressing load Fn0 between the first rotating member 10 and the planetary ball 30 and between the second rotating member 20 and the planetary ball 30. Is obtained (step ST7).

  The electronic control unit ECU sets a target pressing force based on each target pressing load Fn0, and controls the pressing device 70 to output the target pressing force (step ST8).

  As described above, the continuously variable transmission 1 according to this embodiment performs the actual rolling obtained by considering the elastic deformation of the first and second rotating members 10 and 20 and the planetary ball 30 when performing the pressure control. Information on the rolling surface temperature on the track is used. For this reason, in the continuously variable transmission 1, the target pressing force of the pressing device 70 can be set to an optimal size without excess or deficiency, and the first and second rotating members 10 and 20 and the planetary ball 30 can be set. It is possible to apply an optimal pressing load without excess or deficiency. Therefore, the continuously variable transmission 1 suppresses spin loss (driving loss) and gross slip (excessive slip) with respect to the contact portion between the first and second rotating members 10 and 20 and the planetary ball 30. Therefore, it is possible to improve the torque transmission efficiency and durability.

[Example 2]
Next, Embodiment 2 of the continuously variable transmission according to the present invention will be described.

  The pressing control described in the first embodiment can be applied to a so-called toroidal continuously variable transmission. Therefore, in this embodiment, a case where the pressing control of the first embodiment is applied to this type of continuously variable transmission will be described.

  FIG. 8 shows a main part of the toroidal-type continuously variable transmission. Reference numeral 100 in FIG. 8 represents the toroidal continuously variable transmission.

  The continuously variable transmission 100 includes input disks 111 and 112 as first rotating elements, output disks 121 and 122 as second rotating elements, power rollers 131 and 132 as third rotating elements, and a power source. And a shaft 150 as an input shaft to which output torque is transmitted.

  In this continuously variable transmission 100, the input disks 111 and 112, the output disks 121 and 122 as the second rotating elements, and the shaft 150 have a common first rotation center axis R1, and the power rollers 131 and 132, respectively. Individually have a second rotation center axis R2. The first rotation center axis R1 and the second rotation center axis R2 are arranged on the same plane. The same plane is formed for each of the power rollers 131 and 132. In this embodiment, unless otherwise specified, the direction along the first rotation center axis R1 is referred to as an axial direction, and the direction around the first rotation center axis R1 is referred to as a circumferential direction. Further, the direction orthogonal to the first rotation center axis R1 is referred to as a radial direction, and among these, the inward side is referred to as a radial inner side, and the outward side is referred to as a radial outer side.

  The input disks 111 and 112 and the output disks 121 and 122 have a disk shape and are arranged concentrically with the shaft 150. At that time, the output disks 121 and 122 are arranged between the input disks 111 and 112. Contact surfaces 111a and 121a forming a cavity C1 are formed on the opposing surfaces of the input disk 111 and the output disk 121, respectively. Similarly, contact surfaces 112a and 122a forming a cavity C2 are formed on the opposing surfaces of the input disk 112 and the output disk 122, respectively.

  The input disks 111 and 112 are integral with the shaft 150 and rotate in the circumferential direction, and can be moved relative to the shaft 150 in the axial direction. For example, the input disks 111 and 112 are spline fitted to the shaft 150. As a result, the output torque of the power source is transmitted to the input disks 111 and 112. On the other hand, the output disks 121 and 122 can rotate relative to the shaft 150 in the circumferential direction via bearings (not shown). The output disks 121 and 122 are connected to the drive wheels through a gear group, and transmit the output torque of the power source transmitted through the power rollers 131 and 132 to the drive wheels.

  In the continuously variable transmission 100, a plurality of power rollers 131 are radially arranged around the first rotation center axis R1 in a cavity C1 formed between the input disk 111 and the output disk 121. . Similarly, in the cavity C2 formed between the input disk 112 and the output disk 122, a plurality of power rollers 132 are arranged radially about the first rotation center axis R1. In the continuously variable transmission 100, each power roller 131 is sandwiched between the input disk 111 and the output disk 121, and each power roller 132 is sandwiched between the input disk 112 and the output disk 122.

  Each of the power rollers 131 and 132 is individually supported by a trunnion 140 shown in FIGS. 9 and 10 and can rotate relative to the trunnion 140 around the second rotation center axis R2. In other words, the power rollers 131 and 132 are supported by the trunnion 140 so that they can rotate relative to the input disks 111 and 112 and the output disks 121 and 122. The trunnion 140 moves the power rollers 131 and 132 in the radial direction with respect to the input disks 111 and 112 and the output disks 121 and 122, and also powers the power rollers 131 with respect to the input disks 111 and 112 and the output disks 121 and 122. , 132 can be tilted.

  In the continuously variable transmission 100, the rotation angle between the input disk 111 and the output disk 121 and between the input disk 112 and the output disk 122 are changed by changing the tilt angles of the power rollers 131 and 132. The speed ratio γ is changed by changing the rotation ratio. Therefore, a tilting device that tilts the respective power rollers 131 and 132 is used for the transmission (not shown) of the continuously variable transmission 100. For example, as this transmission, a hydraulic servo that causes the power rollers 131 and 132 to tilt by causing the power rollers 131 and 132 to stroke from the neutral position by hydraulically moving the power rollers 131 and 132 from the neutral position. The mechanism is known. The neutral position means a state in which the second rotation center axis R2 of the power rollers 131 and 132 is orthogonal to the first rotation center axis R1. When the power rollers 131 and 132 are in the neutral position, the tilt angle is 0 degree, and the input disks 111 and 112 and the output disks 121 and 122 rotate at the same rotational speed, so the transmission ratio γ is 1. .

  At the contact portions of the power rollers 131 and 132 with the input disks 111 and 112 and the output disks 121 and 122, axial force (pushing force) from the input disks 111 and 112 and the output disks 121 and 122 toward the power rollers 131 and 132 is determined. By applying pressure), a pressing load (normal force) Fn in the normal direction according to the shape of the power rollers 131 and 132 and the cavities C1 and C2 is applied. The continuously variable transmission 100 is provided with a pressing device 170 that generates the pressing force. The pressing device 170 generates a pressing force from at least one of the input disks 111 and 112 toward the output disks 121 and 122. For example, the illustrated pressing device 170 controls the hydraulic pressure in the hydraulic chamber provided on the back side (the side opposite to the power roller 131) of the input disk 111 by increasing / decreasing the pressure from the input disk 111 to the power roller 131. The target pressing force toward is generated. The pressing control device is prepared as one of arithmetic processing functions of the electronic control unit ECU.

  The target pressing force of the pressing device 170 depends on the target pressing load Fn0 from the input disks 111 and 112 and the output disks 121 and 122 to the power rollers 131 and 132 and the geometric conditions of the continuously variable transmission 100. Determined. The geometric condition is a shape that determines the load direction of the pressing load Fn (shape of the cavities C1, C2, power rollers 131, 132, etc.) and the like, and is one of the specification information of the continuously variable transmission 100. is there. The target pressing load Fn0 is calculated by the target traction force Ft0 and the traction coefficient μ (Fn = Ft / μ) as described in the first embodiment. The traction coefficient μ is a contact portion between the input disks 111 and 112 and the power rollers 131 and 132 (contact portion on the input side) or a contact portion between the output disks 121 and 122 and the power rollers 131 and 132 (output). It is determined by the surface pressure, slip ratio, temperature, etc. That is, when the pressing control device sets the target pressing force of the pressing device 170, the traction coefficient μ is obtained based on the temperature of the contact portion, and the target pressing load Fn0 is obtained from the traction coefficient μ and the target traction force Ft0. Ask. Then, the electronic control unit ECU calculates the target pressing force based on the target pressing load Fn0 and the geometric condition of the continuously variable transmission 100. These calculations themselves are well known in the technical field of this type of traction drive device, as described above.

  Also in the continuously variable transmission 100, when the electronic control unit ECU sets the target pressing force of the pressing device 170, the temperature on the rolling track between the input disks 111 and 112 and the power rollers 131 and 132 or At least one of the temperatures on the rolling track between the output disks 121 and 122 and the power rollers 131 and 132 is used.

  The temperature of the contact portion on the input side is the temperature on the rolling track between the input disks 111 and 112 and the power rollers 131 and 132, and between the input disks 111 and 112 in the power rollers 131 and 132. Measure the rolling surface temperature. Further, the temperature of the contact portion on the output side is the temperature on the rolling track between the output disks 121 and 122 and the power rollers 131 and 132, and the output disks 121 and 122 in the power rollers 131 and 132. Measure the rolling surface temperature during In order to measure the rolling surface temperature, the continuously variable transmission 100 is provided with a temperature detection device having a temperature sensor 181.

  This exemplary temperature detection device has a holding member 182 fixed to the sensor holding portion 141 of the trunnion 140, and the holding member 182 holds the temperature sensor 181. The temperature sensor 181 is provided for at least one of the power rollers 131 and 132. Here, all the power rollers 131 and 132 are provided.

  This temperature sensor 181 takes into account the rotational direction when torque is input from the power source, for example, and immediately after passing through the contact portions of the rolling surfaces of the power rollers 131 and 132 with the input disks 111 and 112 and the output disks 121 and 122. It is desirable to place it where the temperature is detected. Thereby, since the value closest to the temperature of the contact portion can be detected, the estimation accuracy of the traction coefficient μ is improved. Here, in the case of providing only one power roller 131 (132), a place where the temperature immediately after passing through the contact portion with the input disk 111 (112) and the contact portion with the output disk 121 (122) is detected. It is preferable to arrange the temperature sensors 181 respectively. However, in this case, there is a possibility that the detected temperature of one contact portion may change due to the influence of the temperature of the other contact portion. Therefore, when detecting the temperatures on the input side and the output side, as shown in FIG. 11 and FIG. As described above, it is preferable to arrange the temperature sensors 181 for two or more power rollers 131 and 132 separately for the input side and the output side.

  Further, when the temperature sensors 181 are provided for each of the plurality of power rollers 131 and 132, for example, a priority order may be given as to which temperature sensor 181 is used for calculating the traction coefficient μ. Good. For example, in the plurality of temperature sensors 181 provided on the input side (or output side), the detected temperature of the temperature sensor 181 on the input side (or output side) with the highest priority is the other input side (or output side). The temperature detected by the temperature sensor 181 on the input side (or output side) with the second priority is used for the calculation of the traction coefficient μ.

  Here, the temperature sensor 181 is arranged to measure the temperature of the reference rolling surface (FIG. 10) of the power rollers 131 and 132. However, also in this continuously variable transmission 100, the input disks 111 and 112, the output disks 121 and 122, and the power rollers 131 and 132 are elastically deformed by the pressing load Fn therebetween (FIG. 13 illustrates the cavity C1 side). ). Since the trajectory of the rolling track changes due to the elastic deformation, also in this continuously variable transmission 100, the sensor position of the temperature sensor 181 deviates from the actual rolling track, and the detected temperature of the temperature sensor 181 and the actual rotation are detected. There may be a difference between the temperature on the running track. FIG. 10 illustrates the reference rolling surface and the actual rolling surface of the power rollers 131 and 132.

  Therefore, also in the present embodiment, the rolling surface temperature on the actual rolling track is obtained by correcting the temperature detected by the temperature sensor 181 according to the amount of elastic deformation, and this actual rolling surface temperature (of the temperature sensor 181). The target pressing force is calculated based on the detected temperature correction value). And this continuously variable transmission 100 performs press control with the target pressing force calculated | required in this way. Since the pressing control is performed in substantially the same manner as in the first embodiment, it will be briefly described with reference to the flowchart of FIG. When the above-described priority is set for the temperature detected by the temperature sensor 181, the temperature detected by the temperature sensor 181 used for the following arithmetic processing is determined based on the priority.

  First, the electronic control unit ECU acquires calculation conditions (step ST1). Then, the electronic control unit ECU obtains a provisional target pressing load based on the obtained calculation condition (step ST2), and the input disks 111 and 112, the output disk 121, when the pressing control is performed with the provisional target pressing load, The amount of elastic deformation of 122 and the power rollers 131 and 132 is obtained (step ST3).

  Here, the amount of elastic deformation includes the provisional target pressing load, the specification information of the continuously variable transmission 100 (geometric conditions, gear ratio γ, input disks 111 and 112, output disks 121 and 122, and power rollers 131 and 132. Information on the material, etc.). Since the specification information of the continuously variable transmission 100 can be grasped in advance, the elastic deformation amount calculation device includes, for example, elastic deformation of the input disks 111 and 112, the output disks 121 and 122, and the power rollers 131 and 132 with respect to the provisional target pressing load. By preparing an amount map in advance, each elastic deformation amount may be calculated based on the map and the provisional target pressing load. For example, each map shows an axial direction component and a radial direction component of the elastic deformation amount. The elastic deformation amount may be obtained from the detection values of strain sensors provided on the input disks 111 and 112, the output disks 121 and 122, and the power rollers 131 and 132.

  The electronic control unit ECU obtains a temperature correction amount for the temperature detected by the temperature sensor 181 based on the elastic deformation amount in step ST3 (step ST4).

  From the axial direction component and the radial direction component of the elastic deformation amounts of the input disks 111 and 112, the output disks 121 and 122, and the power rollers 131 and 132, the respective elastic deformation states can be known, and experiments and simulations are performed in advance. By performing the above, the position of the actual rolling surface, that is, the sensor deviation amount can be estimated. Therefore, the temperature estimation device is caused to obtain the sensor deviation amount based on the axial direction component and the radial direction component of the elastic deformation amount. Here, the sensor deviation amount may be obtained from the axial direction component and the radial direction component of the elastic deformation amount of the power rollers 131 and 132 in contact with the temperature sensor 181. The temperature estimation device calculates the sensor deviation amount based on the map of the sensor deviation amount with respect to the axial direction component and the radial direction component of the elastic deformation amount and the axial direction component and the radial direction component of the elastic deformation amount. In step ST4, the temperature corresponding to the sensor position of the temperature sensor 181 on the map (temperature distribution) is obtained by comparing the sensor deviation amount with a map corresponding to the temperature distribution equivalent to FIG. In this step ST4, a difference between the temperature and the rolling surface temperature on the map (temperature distribution) is obtained, and this difference is set as a temperature correction amount.

  The electronic control unit ECU estimates the rolling surface temperature on the actual rolling track based on the temperature correction amount and the temperature detected by the temperature sensor 181 (step ST5), and the estimated actual rolling track. Based on the upper rolling surface temperature, the slip ratio of the corresponding contact portion, and the like, between the input disks 111 and 112 and the power rollers 131 and 132 and between the output disks 121 and 122 and the power rollers 131 and 132. A traction coefficient μ is obtained (step ST6). The electronic control unit ECU determines the distance between the input disks 111 and 112 and the power rollers 131 and 132 and between the output disks 121 and 122 and the power rollers 131 and 132 based on the traction coefficient μ and the target traction force Ft0. The target pressing load Fn0 at is determined (step ST7). The electronic control unit ECU sets a target pressing force based on each target pressing load Fn0, and controls the pressing device 170 to output the target pressing force (step ST8).

  Thus, also in the continuously variable transmission 100 of the present embodiment, when pressing control is performed, the elastic deformation of the input disks 111 and 112, the output disks 121 and 122, and the power rollers 131 and 132 is taken into consideration. Information on the rolling surface temperature on the actual rolling track is used. For this reason, in the continuously variable transmission 100, the target pressing force of the pressing device 170 can be set to an optimal size without excess or deficiency, and the input disks 111 and 112, the output disks 121 and 122, and the power roller 131. , 132 can be applied with an optimal pressing load without excess or deficiency. Accordingly, the continuously variable transmission 100 can generate a tangential force having an optimum magnitude with reduced spin loss and gloss slip at the contact portion therebetween, thereby improving torque transmission efficiency and durability. Is possible.

1,100 continuously variable transmission 10 first rotating member (first rotating element)
20 Second rotating member (second rotating element)
30 Planetary ball (third rotating element)
40 Sunroller (fourth rotating element)
60 Carrier (fixed element)
70,170 Pressing device 81,181 Temperature sensor 111,112 Input disk (first rotating element)
121, 122 Output disk (second rotating element)
131,132 Power roller (third rotating element)
140 trunnion ECU electronic control unit R1 first rotation center axis R2 second rotation center axis

Claims (2)

First and second rotational elements that are relatively rotatable and have a common first rotational center axis disposed opposite to each other;
A third rotation element having a second rotation center axis disposed on the same plane as the first rotation center axis and sandwiched between the first and second rotation elements;
A transmission that changes a rotation ratio between the first rotating element and the second rotating element by a tilting operation of the third rotating element;
A pressing device that outputs a pressing load from the first rotating element to the third rotating element and a pressing force for generating a pressing load from the second rotating element to the third rotating element;
At least one of a temperature on a reference rolling path between the first rotating element and the third rotating element or a temperature on a reference rolling path between the second rotating element and the third rotating element. A temperature detection device arranged to detect
With
The elastic deformation amount of the first rotation element, the second rotation element, and the third rotation element generated according to the pressing force of the pressing device is calculated, and detected by the temperature detection device based on the calculated elastic deformation amount. A stepless speed change characterized in that the temperature on the actual rolling track is estimated by correcting the measured temperature, and the pressing force of the pressing device is controlled based on the estimated temperature on the actual rolling track. Machine.   When estimating the temperature on the actual rolling track, a shift amount between the position of the detection unit of the temperature detection device and the actual rolling track is calculated based on the elastic deformation amount, and according to the shift amount The continuously variable transmission according to claim 1, wherein the temperature detected by the temperature detection device is corrected.

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