JP4774759B2 - Shift control device for suppressing excessive displacement of rollers in disc / roller type continuously variable transmission - Google Patents

Description

  The present invention relates to a shift control device for a disk / roller type continuously variable transmission.

  As one of continuously variable transmissions suitable for vehicle transmissions, a pair of discs having operating surfaces whose radii change along an axis line, and pushing between the operating surfaces of the pair of discs are coaxially opposed. A plurality of rollers sandwiched between the pair of discs, and a rotational force is transmitted between the pair of discs via the plurality of rollers, and the angle of each roller relative to the pair of discs is changed. 2. Description of the Related Art A disk / roller type continuously variable transmission configured to continuously change a transmission gear ratio of a transmitted rotational force is known. Since the operating surface of the disk of such a disk / roller type continuously variable transmission is generally formed as a part of the toroidal surface, such a continuously variable transmission is usually called a toroidal type continuously variable transmission. The transmission ratio of the transmission is generally the ratio of the output rotational speed to the input rotational speed. Therefore, when the value is larger than 1, the transmission is in a deceleration operation state, and when the value is smaller than 1, the transmission is In speed-up operation. Also, in a vehicle transmission, there are forward rotation for forward travel and reverse rotation for reverse travel, so if the forward gear ratio is expressed as a positive value and the reverse gear ratio is expressed as a negative value. The gear ratio γ is γ> 1, 1> γ> 0, γ <−1, −1 <γ <0, respectively, during forward deceleration, forward acceleration, reverse deceleration, and reverse acceleration. Become.

  In this type of disk / roller type continuously variable transmission, when it is kept constant at an arbitrary gear ratio, the center axis of the roller intersects the center axis of the disk. When changing the transmission gear ratio, the roller center axis is temporarily displaced from the disk center axis so as to deviate from the intersecting state. This is because when the roller center axis is displaced so as to deviate from the intersection with the disk center axis, at the rolling contact portion between the roller and the disk, it is between the rotation direction of the roller and the disk rotation direction. An angle difference is generated in the roller, and this causes a force in a direction toward the center of the disk or away from the center of the disk at the rolling contact portion by an action similar to the steering action of the wheel, and the roller tilts with respect to the disk. . In this case, when both contact points are displaced in the rotation direction of the disk, the roller receives a force in the direction toward the center of the disk at the contact point, and both contact points are in a direction opposite to the rotation direction of the disk. The roller receives a force in a direction away from the center of the disk at the contact point.

The displacement of the roller with respect to the disk as described above is generally performed by driving a trunnion that supports the roller by a hydraulic piston. However, when the piston makes a large stroke in either direction, the piston moves to the end wall surface of the hydraulic chamber. Providing a stroke restricting part that restricts the stroke beyond the planned value of the piston so as to avoid the contacted bottoming state, improve the durability of the servo mechanism, and prevent the shift control from being affected. Is described in Patent Document 1 below. In such a toroidal-type continuously variable transmission, in view of the fact that slipping is more likely to occur as the shifting speed is higher, and slipping is likely to occur as the operating oil temperature is higher, the shifting speed is decreased as the operating oil temperature is higher. Is described in Patent Document 2 below. Further, in such a toroidal type continuously variable transmission, in consideration of the fact that the roller is more likely to slip as the rotational speed of the roller is higher, it is possible to control to suppress the slip based on the rotational speed of the roller. It is described in.
JP2000-18355 JP-A-6-257661 JP-A-7-208567

Further, in the disk / roller type continuously variable transmission as described above, if the displacement amount for displacing the roller center axis with respect to the disk center axis becomes too large in changing the gear ratio, the side slip of the roller with respect to the disk As a result, the gloss slip occurs and the rolling contact surface of the disk or roller may be damaged. Such an excessive side slip is caused when the angle formed by the roller center axis with respect to the disk center axis is 90 °, that is, when the speed ratio is 1 (or -1 during reverse travel), and the disk center axis increases. This is likely to occur at the contact point between the disk and the roller on the farther side, and particularly at the contact point between the output side disk and the roller that receives an enlarged torque when the gear ratio is large. In order to prevent such excessive tilting of the roller, when the tilting of the roller exceeds a predetermined angle, the hydraulic control valve of the hydraulic device that causes the displacement of the roller is switched by a cam that rotates along with the tilting of the roller, and the displacement of the roller is reduced. Inversion is described in Patent Document 4 below.
JP 2000-170902 A

  However, when the tilt of the roller exceeds a predetermined angle as described above, the hydraulic control valve of the hydraulic device that causes the displacement of the roller is switched by the cam that rotates with the tilt of the roller, and the structure in which the displacement of the roller is reversed is a response. Is expected to be delayed considerably. The present invention further provides a disc / roller type continuously variable transmission in which the displacement of the roller can be reversed without a delay in response when the tilt of the roller exceeds a predetermined angle. The problem is to improve.

In order to solve the above-described problems, the present invention is sandwiched between a pair of disks having an operating surface whose radius changes along the axis, and the operating surfaces of the pair of disks facing each other coaxially. A plurality of rollers, and a rotational force is transmitted between the pair of disks via the plurality of rollers, and the central axis of each roller is set to the pair of disks. The disc is configured to change the speed ratio of the rotational force transmitted between the pair of discs by causing the rollers to tilt with respect to the pair of discs by being displaced so as to deviate from the intersection with the central axis of the disc / in the shift control device of the roller type continuously variable transmission, when the tilting of the rollers with respect to the pair of disks is increased beyond a predetermined extent, the relative said disc b Wherein a displacement of the tilting of La with respect to the pair of disk rollers have a displacement transducer means for central axis of the respective roller into a displaced back to the position that intersects the central axis of the pair of disc, the displacement The converting means rotates relative to each other around one rotation axis to guide relative rotation displacements of the first and second members that guide the tilting of the rollers with respect to the pair of disks. The present invention proposes a speed change control device that is a cam that converts linear displacement along the rotation axis of the first and second members .

Wherein the displacement transducer means roller central axis of each roller relative to the pair of disk displaces in a direction back to the intersection of the disc center axis is the extent the tilting of predetermined each roller with respect to the pair of disks beyond increased, when the speed ratio is greater than a predetermined value than 1, or when the speed ratio is smaller than a predetermined value than 1 positive, or when the speed ratio is smaller than a predetermined value than -1 in the negative, or shift It may be when the ratio is negative and larger than the -1 by a predetermined value or more.

Said displacement conversion means changes the predetermined degree of the tilting depending on the operating temperature of the disk / roller type continuously variable transmission, a predetermined degree of the tilting than when the working temperature is not higher the operating temperatures when high You can make it smaller.

The cam may have one inclined cam surface provided on the first member and the other inclined cam surface provided on the second member and engaged with the one inclined cam surface. Furthermore, at least one of the position of the one inclined cam surface with respect to the first member and the position of the other inclined cam surface with respect to the second member depends on the operating temperature of the disc / roller type continuously variable transmission. The predetermined degree of tilting may be reduced when the operating temperature is high and when the operating temperature is not high. The first and second members may be a cylinder and a piston of a displacement actuator for a trunnion that supports the roller.

A plurality of disks having a working surface whose radius changes along the axis as described above, and a plurality of rollers pressed between the working surfaces of the pair of disks coaxially opposed to each other. Rotational force is transmitted between the pair of disks via the rollers, and the central axes of the rollers deviate from the intersection with the central axes of the pair of disks. A shift control device for a disk / roller type continuously variable transmission configured to cause each roller to tilt with respect to the pair of disks by changing the displacement to change a speed ratio of a rotational force transmitted between the pair of disks. And the roller is biased in a direction deviating from the state where the roller center axis intersects the disk center axis with respect to the disk. When against the roller center axis by a predetermined angle or more different tilt than 90 ° with respect to the disc center axis, i.e., when the tilt of each roller with respect to the pair of disks is increased beyond a predetermined extent relative to the disc long as the displacement conversion means are provided for converting the displacement of the tilting of the roller displacement returning the rollers to the pair of disk to position the central axis of the respective roller intersects the center axis of the pair of disc For example, when the angle formed by the roller center axis with respect to the disk center axis is 90 °, that is, when the transmission gear ratio is 1 (or -1), when tilting more than a predetermined angle, that is, with respect to the pair of disks, when the tilting of the rollers is increased beyond a predetermined extent, the immediately roller to the disk by the displacement is the displacement transducer device Over La central axis is converted into displacement in the direction returning to the intersection with the disk centerline axis, the side slip at the contact point between the disc and the roller can be securely prevented without delay to an excessive increase.

  Lubricating oil (also referred to as traction oil) is applied between the disk and the roller to prevent slipping at the contact portion between them and to secure traction engagement. As a result, the oil film formed at the contact portion between the disk and the roller becomes slippery when the temperature rises, and when the gear ratio change control for increasing the tilt of the roller with respect to the disk is performed, the roller tends to excessively tilt with respect to the disk. . Therefore, the predetermined angle for limiting the allowable value of the tilt of the roller center axis with respect to the disk center axis is changed according to the operating temperature of the disk / roller type continuously variable transmission by the roller displacement allowable value variable limiting means. If the predetermined angle is smaller than when the operating temperature is not high when the operating temperature is high, the tilt of the roller center axis with respect to the disc center axis becomes smaller in the gear ratio region where the tilt of the roller with respect to the disc increases. Suppression can be set more accurately in consideration of an increase in slipperiness at the rolling contact portion between the disk and the roller accompanying an increase in the operating temperature of the transmission.

  In this type of disk / roller type continuously variable transmission, the inclination of the rotor center axis with respect to the disk center axis defining the transmission ratio rotates relative to each other around one rotation axis, and the disk Since the first and second members that guide the tilt of the roller center axis relative to the center axis are displaced by relative rotation (usually the rotation of the trunnion that supports the roller), the displacement converting means is not The relative rotational displacement of the first and second members (that is, the rotation of the trunnion around the rotational axis with respect to the transmission housing) is changed to the linear displacement along the rotational axis of the first and second members. If it is a cam to be converted, the setting state of the gear ratio is grasped as the rotation angle between the two members, and the tilt of the roller center axis with respect to the disk center axis is limited and the center of the disk is controlled accordingly. It is pushed back out from the intersection state of the roller center axis for a line, precisely performed by the cam mechanism.

  Also, such a cam mechanism has one inclined cam surface provided on the first member, and one inclined cam surface provided on the second member and the other inclined cam surface. Further, at least one of the position of the one inclined cam surface with respect to the first member and the position of the other inclined cam surface with respect to the second member depends on the operating temperature of the disc / roller type continuously variable transmission. If the operating temperature is high and the predetermined temperature is smaller than when the operating temperature is not high, the predetermined angle for limiting the tilt of the roller central axis with respect to the disk central axis is set to The change according to the operating temperature can be easily and accurately performed using the function of the cam mechanism. In this case, if the first and second members are cylinders and pistons of a displacement actuator for the trunnion that supports the roller, the cams are provided on the opposing surfaces, thereby providing an extremely simple structure. The present invention can be implemented.

  FIG. 1 is a partially longitudinal sectional view showing a roller support / transmission control device using a trunnion in a disk / roller type continuously variable transmission in a state in which the present invention is incorporated in one embodiment. It is a figure and the figure by a partial cross section. The cross section is due to the cut surface indicated as AA in the vertical section.

  In the figure, reference numeral 10 denotes a disk having a toroidal working surface 10a whose radius changes along an axis, which is carried by a shaft 12 supported by bearing means (not shown) and rotates together with the shaft. It is supposed to be. In this case, if the disk 10 is an input side disk and the illustrated transmission is a vehicle transmission, the disk 10 is driven clockwise in the figure when the vehicle moves forward, and counterclockwise in the figure when the vehicle moves backward. It is designed to rotate in the direction. The disk 10 is in contact with and engaged with the operating surface 10a on the back side of the operating surface 14a of the roller 14 as shown in the drawing, and an output (not shown) is provided on the front side of the roller 14 in the drawing. The disk on the side is in contact engagement with the front side of the operating surface 14a of the roller.

  The roller 14 is supported by a trunnion 24 via an eccentric shaft 16 and bearing devices 18, 20, 22. The trunnion 24 is connected to the links 30 and 32 via bearing devices 26 and 28, respectively, at positions above and below the roller bearing portion. These links 30 and 32 are stretched between another trunnion not shown in the figure paired with roller 14 but not shown in the figure carrying another roller, The pair of trunnions is held in an assembled state. The input side disk and the output side disk are pressed against each other in the axial direction with the pair of rollers interposed therebetween, and the rotation of the input side disk is reversed and the speed is changed via the pair of rollers. Removed from the output disk. The transmission ratio is the ratio of the radial distance formed by the contact point between the roller and the output side disk with respect to the disk center axis d, and the radial distance formed by the contact point between the roller and the input side disk with respect to the disk center axis d. 1 when the angle formed by the roller center axis r with respect to the disk center axis d is 90 °. From this, the roller 14 tilts with respect to the disk 10 in the clockwise direction around the trunnion rotation axis t as viewed in the section AA. On the contrary, the roller 14 decreases as the roller 14 tilts counterclockwise with respect to the disc 10 around the trunnion rotation axis t as viewed in the section AA.

  The lower end of the trunnion 24 is connected to the piston 36 of the hydraulic actuator 34, and is displaced in the vertical direction by supplying and discharging hydraulic pressure to and from the hydraulic chambers 38 and 40 formed below and above the piston. ing. The lower hydraulic chamber 38 and the upper hydraulic chamber 40 are supplied and discharged with a shift control valve (not shown) through oil passages 42 and 44, respectively. When the transmission ratio is maintained at an arbitrary constant value, the central axis r of the roller 14 intersects the central axis d of the disk 10, and at this time, the piston 36 is in the center between the hydraulic chambers 38 and 40 as shown in the figure. In position. When increasing the gear ratio, the hydraulic pressure is supplied to the hydraulic chamber 38, the piston 36 is temporarily displaced upward from the neutral position shown in the figure, and when decreasing the gear ratio, the hydraulic pressure is supplied to the hydraulic chamber 40. Is supplied, and the piston 36 is temporarily displaced downward from the neutral position shown in the figure.

  Arc-shaped cams 48 and 50 are provided on the upper surface of the piston 36 and the end wall 46 of the hydraulic chamber 40, respectively. Cams 48 and 50 have inclined cam surfaces 48a and 50a, respectively. These cams do not engage with each other when the piston 36 is in the neutral position at or near the gear ratio 1 as shown in the drawing or at a position where the gear ratio is positive and smaller than this, but the hydraulic pressure is increased to increase the gear ratio to 1 when the vehicle moves forward. The hydraulic pressure is supplied to the chamber 38, the piston 36 is displaced upward in the figure, and the roller 14 is tilted in the clockwise direction as viewed in the AA section by the tilting force exerted from the disk. The cams 48 and 50 are engaged with the inclined cam surfaces 48a and 50a when they come to a position rotated by a predetermined angle in the clockwise direction as viewed from the AA cross section from the neutral position shown in the figure. As the rotation angle in the same direction further increases, the engagement between the inclined cam surfaces 48a and 50a deepens, and the piston 36 is gradually pushed back toward the neutral position.

  Similar cams are provided symmetrically with respect to the center axis t, that is, the cam 52 having an inclined cam surface 52a on the upper surface of the piston 36, and the inclined cam surface 54a on the end wall 46 of the hydraulic chamber 40. Cams 54 are provided, and these two sets of point-symmetrical cams operate simultaneously with the rotation of the piston 36 synchronized with the tilting of the roller 14.

  Thus, when the speed change ratio is increased within a range in which the tilt angle of the roller 14 in the forward speed ratio increase direction does not exceed a certain level, the upward displacement of the roller center axis relative to the disk center axis is caused by the cams 48 and 50 and Allowed within a relatively large range of values that is not limited by the engagement of 52 and 54, ensuring a rapid change of the gear ratio within those gear ratio regions. In addition, in a range where the forward gear ratio increases beyond a predetermined value, excessive tilting of the roller is reliably suppressed when the gear ratio is increased. Note that the heights of the cams 48, 50, 52, 54 in FIG. 1 are shown larger than the actual size for the sake of clarity. In an actual vehicle disk / roller type continuously variable transmission, the change in the roller center axis relative to the disk center axis for changing the gear ratio is a very small value of about 1 mm at most.

  Similarly, when the forward gear ratio is reduced, a cam that suppresses the roller from over-traveling in the gear ratio reduction direction beyond the minimum gear ratio position and a cam that suppresses tilting on the lower surface of the piston 36 and the end wall surface of the hydraulic chamber 38. 56. That is, an arc-shaped cam 58 having an inclined cam surface 58a is provided on the lower surface of the piston 36, and an arc-shaped cam having an inclined cam surface 60a is provided on the end wall surface 56 of the hydraulic chamber 38 correspondingly. A cam 60 is provided. These cams 58 and 60 also do not engage with each other when the piston 36 is in the neutral position of the gear ratio 1 as shown in the drawing, in the vicinity thereof, or in a position where the gear ratio is larger than this, but the gear ratio is reduced by a positive value. In order to achieve this, hydraulic pressure is supplied to the hydraulic chamber 40, the piston 36 is displaced downward in the figure, and accordingly the roller 14 is tilted counterclockwise as viewed in the AA section by the tilting force exerted from the disk. When the piston 36 comes to a position rotated by a predetermined angle in the counterclockwise direction when viewed in the AA section from the neutral position of the transmission gear ratio 1 shown in the figure, the cams 58 and 60 are portions of the inclined surfaces 58a and 60a. As the rotation angle in the same direction further increases, the engagement between the inclined cam surfaces 58a and 60a deepens, and the piston 36 is gradually pushed back toward the neutral position. .

  Also in this case, a similar cam is provided symmetrically with respect to the trunnion center axis t, that is, a cam 62 having an inclined cam surface 62 a on the lower surface of the piston 36 and an end wall 56 of the hydraulic chamber 38. A cam 64 having an inclined cam surface 64 a is provided, and each of these two point-symmetric cams is operated simultaneously with the rotation of the piston 36 synchronized with the tilting of the roller 14.

  In the state where the disk 10 is reversely rotated when the vehicle is moving backward, the gear ratio is normally maintained at a constant value by a speed reduction mechanism incorporated in a reversing mechanism such as a planetary gear device that reverses the rotation direction. However, when the absolute value of the gear ratio can be increased by the disc / roller type continuously variable transmission, the roller may tilt excessively beyond the maximum position of the gear ratio as seen in the absolute value. The cam which suppresses this may be provided in the lower surface of the piston 36 and the end wall surface 56 of the hydraulic chamber 38. That is, an arc-shaped cam 66 having an inclined cam surface 66a is provided on the lower surface of the piston 36, and an arc-shaped cam 66 having an inclined cam surface 68a is provided on the end wall surface 56 of the hydraulic chamber 38 correspondingly. A cam 68 is provided. These cams 66 and 68 also do not engage with each other when the piston 36 is at a neutral position where the gear ratio is 1 as shown in the drawing and in the vicinity thereof or at a position where the gear ratio viewed from the absolute value is small. Hydraulic pressure is supplied to the hydraulic chamber 40 in order to increase the transmission ratio as viewed in absolute value, the piston 36 is displaced downward in the figure, and the roller 14 is accompanied by the tilting force exerted from the disk, and is viewed in the AA cross section. When the piston 36 comes to a position rotated by a predetermined angle in the clockwise direction as viewed in the AA cross section from the neutral position of the transmission gear ratio 1 shown in the figure, the cams 66 and 68 are inclined. The surfaces 66a and 68a are engaged with each other, and as the rotation angle in the same direction further increases, the inclined cam surfaces 66a and 68a are deeply engaged, and the piston 36 is gradually pushed back toward the neutral position. Be It has become the jar.

  Also in this case, the same cam is provided symmetrically with respect to the trunnion center axis t, that is, the cam 70 having the inclined cam surface 70a on the lower surface of the piston 36 and the end wall 56 of the hydraulic chamber 38 are also provided. A cam 72 having an inclined cam surface 72 a is provided, and two sets of these point-symmetrical cams are operated simultaneously with the rotation of the piston 36 synchronized with the tilting of the roller 14.

  In the same manner, when the absolute value of the reverse gear ratio of the vehicle is reduced, the cam that suppresses the tilting of the roller exceeding the minimum gear ratio absolute position in the direction of decreasing the gear ratio absolute value is a piston. The upper surface 36 may be provided on the end wall surface 46 of the hydraulic chamber 40. That is, an arcuate cam 74 having an inclined cam surface 74a is provided on the upper surface of the piston 36. Correspondingly, the end wall surface 46 of the hydraulic chamber 40 has an arcuate shape having an inclined cam surface 76a. A cam 76 is provided. These cams 74 and 76 are also engaged with each other when the piston 36 is in a neutral position with an absolute speed ratio of 1 as shown in the drawing, in the vicinity thereof, or in the vicinity thereof or when the speed ratio is greater than 1 with a reverse speed. However, hydraulic pressure is supplied to the hydraulic chamber 38 in order to reduce the gear ratio by an absolute value, the piston 36 is displaced upward in the figure, and the roller 14 is tilted by the tilting force exerted from the disk. When the piston 36 is tilted in the counterclockwise direction as viewed in the cross section, and the piston 36 comes to a position rotated by a predetermined angle in the counterclockwise direction as viewed in the AA cross section from the neutral position of the transmission gear ratio absolute value 1 shown in the figure, The cams 74 and 76 engage with each other at the inclined surfaces 74a and 76a. As the rotation angle in the same direction further increases, the engagement between the inclined cam surfaces 74a and 76a deepens, and the piston 36 becomes neutral. Gradually toward the position And it is made as to be returned.

  Also in this case, a similar cam is provided symmetrically with respect to the trunnion center axis t, that is, a cam 78 having an inclined cam surface 78 a on the upper surface of the piston 36 and an end wall 46 of the hydraulic chamber 40. A cam 80 having an inclined cam surface 80a is provided, and two sets of these point-symmetrical cams are operated simultaneously with the rotation of the piston 36 synchronized with the tilting of the roller 14.

  It should be noted that the cam sets 48/50, 52/54, 58/60, 62/64, 66/68, 70/72, 74/76, and 78/80 that are mutually engaged with each other are as described above. / 50 and 52/54 are provided symmetrically around the trunnion central axis t, and cam sets 58/60 and 62/64 are provided symmetrically around the trunnion central axis t. Cam sets 66/68 and 70/72 are provided symmetrically around the trunnion central axis t, and cam sets 74/76 and 78/80 are symmetrical with respect to the trunnion central axis t. Should be provided in positions 48/50 and 52/54, 58/60 and 62/64, 66/68 and 70/72, 74/76 and 78/80 A trunnion is a group unless it interferes with each other It may be provided at any location around the mandrel wire t.

  FIG. 2 shows that the predetermined angle relating to the tilting of the roller with respect to the disk by the displacement converting means is changed according to the operating temperature of the disk / roller type continuously variable transmission, and when the operating temperature is high, the operating temperature is not high. It is sectional drawing similar to the principal part of FIG. 1 which shows one Embodiment of the invention comprised so that a predetermined angle might be made small. In FIG. 2, the same reference numerals as in FIG. 1 are assigned to the portions corresponding to the portions shown in FIG.

  In this embodiment, the cams 50 and 54 for the forward high speed ratio provided on the end wall portion 46 of the hydraulic chamber 40 in the embodiment of FIG. 1 is provided on arc-shaped cam plates 82 and 84 that can be rotated around t, and is a cam for the forward low speed ratio provided in the end wall portion 56 of the hydraulic chamber 38 in the embodiment of FIG. Reference numerals 60 and 64 are formed on arcuate cam plates 86 and 88 that are rotatable around the trunnion center axis t along the end wall portion 56, respectively. In the embodiment of FIG. 1, the cams 68 and 72 for the reverse high speed ratio provided on the end wall portion 56 of the hydraulic chamber 38 rotate around the trunnion center axis t along the end wall portion 56. The cams 76 and 80 with respect to the forward low speed ratio provided on the end wall portion 46 of the hydraulic chamber 40 in the embodiment shown in FIG. It is provided on arcuate cam plates 94 and 96 that can rotate around the trunnion central axis t along the wall 46. These cam plates are displaced in the circumferential direction according to the operating temperature of the continuously variable transmission by temperature-sensitive actuators 98, 100, 102, 104, 106, 108, 110, 112, which detect the operating temperature of the continuously variable transmission, respectively. Thus, the allowable value of the tilting of the roller relative to the disk is changed by the displacement converting means in accordance with the operating temperature of the continuously variable transmission.

  Any of the temperature sensitive actuators 98 to 112 may be of the same type, and the temperature sensitive actuator 96, which is one of them, has a temperature sensitive portion 114 supported by the end wall portion 46 of the hydraulic chamber 40, and The operator 116 protruding from the side protrudes more greatly as the operating temperature of the continuously variable transmission sensed by the temperature sensing unit 114 increases, and this actuator causes a part of the cam plate 82 to protrude. The provided lug 118 is driven in a tangential direction along the periphery of the piston 36, and the cam plate 82 is rotationally displaced in the counterclockwise direction as viewed in the AA section in accordance with the increase in the operating temperature of the continuously variable transmission. It is like that. Reference numeral 120 denotes a stay supported by the end wall 46 of the hydraulic chamber 40 in the same manner as the temperature sensing unit 114. The stay 120 holds a compression coil spring 122 between the lug 118 and the continuously variable transmission sensed by the temperature sensing unit 96. The spring force in the return direction is applied to the lug against the movement of the lug 100 due to the increase in the operating temperature. The temperature sensitive actuator 100 similarly drives a cam plate 84 that is 180 ° apart from the cam plate 82, and the same rotational displacement of the pair of cams 82 and 84 according to the operating temperature of the continuously variable transmission is obtained.

  That is, when the operating temperature of the continuously variable transmission rises, the cam plates 82 and 84 are displaced counterclockwise by the temperature-sensitive actuators 98 and 100 when viewed in the AA section, respectively, and the inclined cam surface 50a of the cam 50 and Since the inclined cam surface 54a of the cam 54 is brought closer to the inclined cam surface 48a of the cam 48 formed on the piston 36 and the inclined cam surface 52a of the cam 52, the cams 48 and 50 are engaged with each other. In the region where the gear ratio is large due to the engagement of 54, the limitation on the maximum angle of the tilt of the roller with respect to the disk in order to increase the gear ratio is lower than that when the operating temperature of the continuously variable transmission is low. It is done.

  In the same manner, when the operating temperature of the continuously variable transmission rises, the arc-shaped cam plates 86 and 88 are displaced in the clockwise direction by the temperature-sensitive actuators 102 and 104 in the section AA, and the cam 60 The inclined cam surface 60a and the inclined cam surface 64a of the cam 64 are brought closer to the inclined cam surface 58a of the cam 58 and the inclined cam surface 62a of the cam 62 formed on the piston 36, respectively. When the operating temperature of the continuously variable transmission is low, the limit of the maximum tilt angle of the roller with respect to the disk in order to reduce the speed ratio in the region where the speed ratio is small due to the engagement of the cams 62 and 64 is smaller. This is done with a larger gear ratio.

  Further, in the same manner, when the operating temperature of the continuously variable transmission rises, the arc-shaped cam plates 90 and 92 are displaced counterclockwise by the temperature-sensitive actuators 106 and 108 as viewed in the section AA, The inclined cam surface 68a of the cam 68 and the inclined cam surface 72a of the cam 72 are brought closer to the inclined cam surface 66a of the cam 66 and the inclined cam surface 70a of the cam 70 formed on the piston 36, respectively. The maximum angle of the tilting of the roller with respect to the disk in order to increase the absolute value of the gear ratio in the region where the gear ratio is large in the absolute value when the vehicle is driven backward by the engagement of 68 and the cams 70 and 72 is continuously variable. This is performed at a smaller absolute value gear ratio than when the operating temperature of the transmission is low.

  Further, in the same manner, when the operating temperature of the continuously variable transmission rises, the arc-shaped cam plates 94 and 96 are displaced clockwise by the temperature-sensitive actuators 110 and 112 as viewed in the section AA, and the cams The inclined cam surface 76a of 76 and the inclined cam surface 80a of the cam 80 are brought closer to the inclined cam surface 72a of the cam 72 and the inclined cam surface 78a of the cam 78 formed on the piston 36, respectively. The maximum angle of the tilt of the roller with respect to the disk for the reduction of the absolute value of the speed ratio in the region where the speed ratio is small in the absolute value when the vehicle moves backward by the engagement of the cams 78 and 80 is continuously variable. This is performed at an absolute speed ratio larger than that when the operating temperature of the transmission is low.

  FIG. 3 shows that the predetermined angle relating to the tilting of the roller with respect to the disk by the displacement converting means is changed according to the operating temperature of the disk / roller type continuously variable transmission, and when the operating temperature is high, the operating temperature is not high. FIG. 5 is a cross-sectional view similar to FIG. 1 or FIG. 2 showing another embodiment of the invention configured to reduce the predetermined angle. In FIG. 3, the same reference numerals as those in FIG. 1 or 2 are assigned to the portions corresponding to the portions shown in FIG. 1 or FIG.

  In this embodiment, the cams 48 and 52 for the forward high speed ratio provided on the upper surface 36 of the piston in the embodiment of FIG. 1 are arranged around the trunnion central axis t along the upper surface of the piston 36. The cams 58 and 62 for the forward low speed ratio provided on the lower surface of the piston in the embodiment of FIG. 1 are provided on the rotatable arcuate cam plates 124 and 126, respectively. Are provided on arcuate cam plates 128 and 130 that can be rotated around the trunnion central axis t. Further, in the embodiment of FIG. 1, the cams 66 and 70 for the reverse high speed ratio provided on the lower surface of the piston are arc-shaped that can rotate around the trunnion central axis t along the lower surface of the piston 36, respectively. The cams 74 and 78 for the reverse low gear ratio provided on the cam plates 132 and 134 and provided on the upper surface of the piston in the embodiment of FIG. Are provided on arc-shaped cam plates 136 and 138 which can be rotated around the center. These cam plates respectively detect the operating temperature of the continuously variable transmission in the circumferential direction according to the operating temperature of the continuously variable transmission by temperature-sensitive actuators 140, 142, 144, 146, 148, 150, 152, 154. By being displaced, the allowable angle of tilting of the roller with respect to the disk is changed by the displacement converting means in accordance with the operating temperature of the continuously variable transmission.

  The temperature-sensitive actuators 140 to 154 may be of the same type, and they are attached to an annular plate or an arc shape that is slidable along the peripheral edge of the upper surface or the lower surface of the piston 36. Except for the plate, it may be the same type as the temperature-sensitive actuators 98 to 112 in the embodiment shown in FIG. However, in this case, the temperature-sensitive actuator 140, which is one of them, has a temperature-sensitive portion 156 supported from the upper surface of the piston 36, and the actuator 158 protruding from the side of the temperature-sensitive actuator 156 is formed by the temperature-sensitive portion 156. As the operating temperature of the continuously variable transmission is sensed, it protrudes more greatly, and the lug 160 provided on a part of the cam plate 124 is tangentially along the peripheral edge of the piston 36 by this actuator. Driven, the cam plate 124 is rotated and displaced in the clockwise direction as seen in the section AA in accordance with the increase in the operating temperature of the continuously variable transmission. 162 is a stay supported from the upper surface of the piston 36 in the same manner as the temperature sensing unit 128, and holds the compression coil spring 136 between the lug 160 and increases the operating temperature of the continuously variable transmission sensed by the temperature sensing unit 128. The spring force in the returning direction is applied to the lug against the movement of the lug 136 due to the above.

  When the operating temperature of the continuously variable transmission rises, the cam plates 124 and 126 are displaced clockwise by the temperature-sensitive actuators 140 and 142, respectively, as viewed in the AA section, and the inclined cam surface 48a of the cam 48 and the cam 52 The inclined cam surface 52a is brought closer to the inclined cam surface 50a of the cam 50 and the inclined cam surface 54a of the cam 54 formed on the end wall portion 46 of the hydraulic chamber 40, respectively. In the region where the gear ratio is large due to the engagement of the cams 52 and 54, the restriction on the maximum angle of the roller tilting with respect to the disk for increasing the gear ratio is lower than when the operating temperature of the continuously variable transmission is low. It is performed at a gear ratio.

  In the same manner, when the operating temperature of the continuously variable transmission rises, the cam plates 128 and 130 are displaced counterclockwise by the temperature-sensitive actuators 144 and 146 when viewed in the AA section, and the cam 58 is tilted. The surface 58a and the inclined cam surface 62a of the cam 62 are brought closer to the inclined cam surface 60a of the cam 60 and the inclined cam surface 64a of the cam 64 formed on the end wall portion 56 of the hydraulic chamber 38, respectively. When the operating temperature of the continuously variable transmission is low, the maximum angle of the tilt of the roller with respect to the disk in order to reduce the transmission ratio in the region where the transmission ratio is small due to the engagement of 60 and the engagement of the cams 62 and 64. The transmission is performed at a larger gear ratio.

  Further, in the same manner, when the operating temperature of the continuously variable transmission rises, the arc-shaped cam plates 132 and 134 are displaced clockwise by the temperature-sensitive actuators 148 and 150 as viewed in the section AA, and the cams The inclined cam surface 66 a of 66 and the inclined cam surface 70 a of the cam 70 are brought closer to the inclined cam surface 68 a of the cam 68 and the inclined cam surface 72 a of the cam 72 formed on the end wall portion 56 of the hydraulic chamber 38, respectively. Limiting the maximum angle of tilting of the roller with respect to the disk in order to increase the absolute value of the gear ratio in the region where the gear ratio is large in the absolute value when the vehicle moves backward by the engagement of the cams 66 and 68 and the cams 70 and 72 Is performed at a smaller absolute value gear ratio than when the operating temperature of the continuously variable transmission is low.

  Further, in the same manner, when the operating temperature of the continuously variable transmission rises, the arc-shaped cam plates 136 and 138 are displaced counterclockwise by the temperature-sensitive actuators 152 and 154 as viewed in the section AA, The inclined cam surface 74a of the cam 74 and the inclined cam surface 78a of the cam 78 are brought closer to the inclined cam surface 76a of the cam 76 and the inclined cam surface 80a of the cam 80 formed on the end wall portion 46 of the hydraulic chamber 40, respectively. Therefore, the maximum angle of the tilt of the roller with respect to the disk for reducing the absolute value of the gear ratio in the region where the gear ratio is small in the absolute value when the vehicle moves backward by the engagement of the cams 74 and 76 and the cam 78 and 80. This restriction is performed at a larger absolute value gear ratio than when the operating temperature of the continuously variable transmission is low.

  While the present invention has been described in detail with respect to several embodiments thereof, it will be apparent to those skilled in the art that various modifications can be made to these embodiments within the scope of the present invention. .

BRIEF DESCRIPTION OF THE DRAWINGS Schematic which shows one Embodiment of the roller excessive displacement suppression type transmission control apparatus of the disc / roller type continuously variable transmission by this invention about the principal part of invention. FIG. 5 is a schematic diagram showing another embodiment of a roller control device for suppressing excessive displacement of a disc / roller type continuously variable transmission according to the present invention with respect to the main part of the invention. Schematic which shows another one Embodiment of the roller excessive displacement suppression type transmission control apparatus of the disc / roller type continuously variable transmission by this invention about the principal part of invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Disc, 10a ... Disc working surface, 12 ... Disc drive shaft, 14 ... Roller, 14a ... Roller working surface, 16 ... Eccentric shaft, 18, 20, 22 ... Bearing device, 24 ... Trunnion, 26, 28 ... Bearing device, 30, 32 ... Link, 34 ... Hydraulic actuator, 36 ... Piston, 38, 40 ... Hydraulic chamber, 42, 44 ... Oil passage, 46 ... End wall surface, 48, 50, 52, 54 ... Cam, 48a, 50a, 52a, 54a ... inclined cam surface, 56 ... end wall surface, 58, 60, 62, 64, 66, 68, 70, 72, 74, 76, 78, 80 ... cam, 58a, 60a, 62a, 64a, 66a , 68a, 70a, 72a, 74a, 76a, 78a, 80a ... inclined cam surface, 82, 84, 86, 88, 90, 92, 94, 96 ... arc-shaped cam plate, 98, 100, 102, 104, 106, 108, 110, 112 ... temperature sensitive actuators, 114, 156 ... temperature sensitive parts, 116, 158 ... actuators, 118, 160 ... lugs, 120, 162 ... stays, 122, 164 ... compression coil springs

Claims (4)

A pair of disks having an operating surface whose radius changes along an axis, and a plurality of rollers pressed between the operating surfaces of the pair of disks coaxially opposed to each other. A rotational force is transmitted between the pair of discs, and the rollers are displaced with respect to the pair of discs so that the center axis of each roller is away from the intersection with the center axis of the pair of discs. A shift control device for a disc / roller type continuously variable transmission configured to cause each roller to tilt with respect to the pair of discs and to change the gear ratio of the rotational force transmitted between the pair of discs, when the tilting of the rollers with respect to the pair of disks is increased beyond a predetermined extent, the displacement of the tilting of the roller relative to the disk to the pair of disks Above the rollers have a displacement converting means for converting the displacement center axis of the respective roller returns to the position that intersects the central axis of the pair of disks, each other around said displacement transducer means is one of the rotation axis Relative rotational displacements of the first and second members that relatively rotate and guide the tilting of the rollers with respect to the pair of disks are applied to the rotational axes of the first and second members. A shift control device characterized by being a cam that converts to a linear displacement along .   The cam has one inclined cam surface provided on the first member and the other inclined cam surface provided on the second member and engaged with the one inclined cam surface. The shift control device according to claim 1. At least one of the position of the one inclined cam surface with respect to the first member and the position of the other inclined cam surface with respect to the second member is changed according to the operating temperature of the disk / roller type continuously variable transmission, 3. The speed change control device according to claim 1, wherein the predetermined degree of tilting is made smaller when the operating temperature is high than when the operating temperature is not high.   The shift control device according to claim 2, wherein the first and second members are a cylinder and a piston of a displacement actuator for a trunnion that supports the roller.

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