JP2007292140A - Continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To remove inconvenience such as an enlargement and reduction in a shift response for increasing strength or actuator capacity of a shift mechanism part (a pulley width adjusting mechanism). <P>SOLUTION: This continuously variable transmission has a V pulley composed of a fixed pulley member 14a fixed to an input shaft 12 and a movable pulley member 14b axially displaceably supported by the input shaft 12, torque cam mechanisms 52, 54 and 56 pressing the movable pulley member 14b to the fixed pulley member 14a side, first driving mechanisms 58, 60, 62 and 64 for axially moving the torque cam mechanisms, a toothed ring 18 clamped by the V pulley and supporting the outer periphery by a plurality of guide rollers 22a, 22b, 22c and 22d, an output gear 26 meshing with a gear arranged on the outer periphery of the toothed ring 18 and axially movably supported by an output shaft 28, an arm 24 rotatably and axially displaceably supporting the plurality of guide rollers and revolvable around the axis of the output shaft 28, and second driving mechanisms 48 and 50 for revolving the arm 24 around the axis of the output shaft 28. The first driving mechanisms and the second driving mechanisms are drive by single actuators 46, 68 and 70. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a continuously variable transmission, and can be used in automobiles and various industrial machines.

  For continuously variable transmissions for automobiles, mainly metal belt type CVT and half toroidal type CVT (traction drive type) have been put into practical use. The present applicant, as a continuously variable transmission of a new mechanism that solves the problems (smaller and lighter, improved efficiency) of the conventional continuously variable transmission, a toothed ring is clamped between a pair of pulleys, the pulley and the toothed A continuously variable transmission that enables power transmission and continuously variable transmission with a ring is proposed (Patent Documents 1 and 2). Here, the gear ratio is continuously changed by changing the pulley width using a cam or a feed screw.

  As shown in FIGS. 4 and 5, the main structure of the continuously variable transmission described in Patent Documents 1 and 2 is a toothed ring 18 in a groove of a V pulley formed of a pair of pulley members 14 movable in the axial direction. It is a structure that sandwiches. In the casing 10, rotating shafts 12 and 28 parallel to each other are rotatably supported via bearings. When torque is transmitted between the rotary shafts 12 and 28 and one rotary shaft (12 or 28) is used as an input shaft, the other rotary shaft (28 or 12) is used as an output shaft.

  The rotating shaft 12 supports a V pulley composed of a pair of pulley members 14. Each pulley member 14 can be moved in the axial direction of the rotary shaft 12 by a ball spline 16 and can be locked in the rotational direction to transmit torque. Each pulley member 14 includes a pulley width adjusting mechanism 34. This pulley width adjusting mechanism 34 is a ball screw type, and a circulation path is formed by a spiral groove formed on the inner periphery of the nut 36 and a spiral groove formed on the outer periphery of the screw shaft 38 so that a plurality of balls are circulated. It has become. The nut 36 is fixed to a stationary member such as the casing 10. Therefore, the screw shaft 38 is displaced in the axial direction as it rotates. The tip of the screw shaft 38 is in contact with the outer ring of the bearing 32 fitted to the boss portion of the pulley member 14.

  A gear 40 is fixed to the screw shaft 38. The gear 40 meshes with a gear 44 fixed to a transmission shaft 42 that is rotatably supported by the casing 10. When the transmission shaft 42 is rotated, the screw shaft 38 is rotated, and at the same time, the screw shaft 38 is moved in the axial direction to the right or left in the drawing depending on the rotation direction. Since the ball screws in the left and right pulley width adjusting mechanisms 34 in FIG. 6 are reverse to each other, the screw shafts 38 are moved in the opposite directions with the rotation of the transmission shaft 42 and therefore the gear 44. . In this way, the pair of pulley members 14 moves in the direction of approaching or separating, and the groove width of the V pulley changes.

  A small gear 26 is fixed to the rotary shaft 28. The small gear 26 meshes with the toothed ring 18. The toothed ring 18 has teeth that mesh with the teeth of the small gear 26 and a smooth cylindrical guide surface 20 (see FIG. 7), and the guide surface 20 contacts the guide roller. Only two of the three guide rollers 22a, 22b, and 22c shown in FIG. 5, that is, the guide roller 22a and the guide roller 22c appear in FIG. The guide rollers 22a and 22b are rotatably attached to the arm 24 via pins and bearings, respectively. The guide roller 22c is composed of a pair of disks arranged on both sides of the small gear 26.

The arm 24 has a ring shape as shown in FIG. 5, and guide rollers 22a, 22b, and 22c are arranged at predetermined intervals. Therefore, the positional relationship between these guide rollers is fixed. As shown in FIG. 6, the arm 24 is composed of two plates, and is rotatably supported by the sleeve 30 of the casing 10 coaxially with the rotary shaft 28. Since the toothed ring 18 is constrained from the outer periphery by three guide rollers 22a, 22b, and 22c, it can be rotated without a central axis (coreless roller). By rotating the arm 24 carrying the guide rollers 22a and 22b, the rotation center of the toothed ring 18 can be moved around the axis of the rotation shaft 28. The teeth on the outer periphery of the toothed ring 18 are always in mesh with the small gear 26. If the pulley member 14 and the arm 24 are controlled so that there is no gap between the toothed ring 18 and the pulley member 14, the pulley member moves as the toothed ring 18 moves around the axis of the rotary shaft 28. 14 is changed, and the speed of the pulley member 14 can be continuously changed with respect to a constant rotation speed of the small gear 26. In this way, a so-called CVT is configured.
JP 2004-263857 A JP 2005-226840 A

  The normal force required for friction transmission is obtained by the reaction force from the gear acting on the toothed ring and the wedge effect formed by the pulley, and the smaller the pulley inclination angle θ (see FIG. 7), the larger the normal force is. can get. On the other hand, when performing a shift that increases the gear ratio, in other words, when the toothed ring is displaced radially outward, it is necessary to apply an axial load to the pulley that can overcome this normal force. For this reason, problems such as an increase in the strength of the speed change mechanism (pulley width adjusting mechanism) or an increase in the actuator capacity and a reduction in the speed change response are caused.

  Further, the transmission ratio of the conventional structure is set by the pulley width. In this case, the gear ratio changes according to the load even if the pulley width is constant due to elastic deformation occurring in each part. For example, the change in the gear ratio increases as the pulley inclination angle decreases. However, the increase in the pulley inclination angle is restricted in terms of torque transmission capacity. An excessive change in the gear ratio due to a load change is not desirable, and a correction of the gear ratio is necessary. However, a sufficient gear ratio correction cannot be performed due to a reduction in the gear transmission performance due to the above problems.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a continuously variable transmission that eliminates the above-mentioned problems, that is, problems such as an increase in strength of a speed change mechanism (pulley width adjusting mechanism) or an increase in actuator capacity and a reduction in speed change response. There is to do.

  A continuously variable transmission according to the present invention includes a first rotating shaft rotatably supported by a casing, a second rotating shaft rotatably supported by the casing, and a fixed pulley member fixed to the first rotating shaft. And a movable pulley member supported by the first rotary shaft so as to be axially displaceable, a torque cam mechanism for pressing the movable pulley member toward the fixed pulley member, and a torque cam mechanism for moving the torque cam mechanism in the axial direction The first drive mechanism, a toothed ring clamped by a V pulley and supported by a plurality of guide rollers on its outer periphery, meshed with a gear provided on the outer periphery of the toothed ring, and axially movable to the second rotating shaft A supported small gear, a plurality of guide rollers that are rotatably and axially displaceable, an arm that can be swiveled around the axis of the second rotating shaft, and an arm that is swiveled around the second rotating shaft Second of And a kinematic mechanism, and is characterized in that the first drive mechanism and a second drive mechanism to be driven by a single actuator.

  According to a second aspect of the present invention, in the continuously variable transmission according to the first aspect of the present invention, there is provided a nut that prevents the cam member from being supported via the bearing, and a male screw member that is supported by the bearing relative to the first rotary shaft or the casing. The feed screw mechanism is configured as described above.

  According to a third aspect of the present invention, in the continuously variable transmission according to the first or second aspect, the second drive mechanism is attached to an arm such that the center of the pitch circle coincides with the axis of the second rotating shaft. It comprises a gear and a small gear meshing with the large gear.

  According to a fourth aspect of the present invention, in the continuously variable transmission according to the third aspect, the large gear is a worm wheel and the small gear is a worm. By adopting such a configuration, the rotation around the output shaft of the arm can be controlled and held at the target angular position.

  According to a fifth aspect of the present invention, in the continuously variable transmission according to any one of the second to fourth aspects, the first drive mechanism includes a large gear provided on a male screw member and a small gear meshing with the large gear. It is characterized by this.

  According to a sixth aspect of the present invention, in the continuously variable transmission of the fifth aspect, the large gear is a worm wheel and the small gear is a worm.

  According to the present invention, it is possible to eliminate the gear ratio due to load change by controlling the gear ratio by directly setting the rotation angle around the output shaft of the arm, that is, the position of the pulley / toothed ring contact portion. . In addition, the change resulting from the slip which arises in a contact part may arise. Further, since the load necessary for moving the toothed ring in the radial direction is considerably smaller than the normal force of the contact portion, the control actuator can be downsized and the entire transmission can be downsized.

  Embodiments of the present invention will be described below with reference to the drawings.

  First, as shown in FIG. 2, the basic structure of the continuously variable transmission is a structure in which a ring 18 is sandwiched between grooves of a V pulley comprising a pair of pulley members 14a and 14b. Since the ring 18 has gear teeth on the outer periphery, the ring 18 is hereinafter referred to as a toothed ring. In the casing 10, rotating shafts 12 and 28 parallel to each other are rotatably supported via bearings. When torque is transmitted between the rotary shafts 12 and 28 and one rotary shaft (12 or 28) is used as an input shaft, the other rotary shaft (28 or 12) is used as an output shaft.

  Of the pair of pulley members 14a and 14b constituting the V pulley, one pulley member 14a is formed integrally with the rotary shaft 12, and the other pulley member 14b is separate from the rotary shaft 12 and is a rotary shaft. An axial displacement and relative rotation with respect to 12 is possible. The rotating shaft 12 is provided with a ball spline or a cam member 54 that is spline-fitted as indicated by reference numeral 16. A compression coil spring 56 is interposed between the cam member 54 and the pulley member 14b. A groove having a depth changed in the circumferential direction is formed between the movable pulley member 14b and the cam member 54, and a steel ball 52 is incorporated in the groove to constitute a torque cam mechanism. Torque transmission between the cam member 54 and the movable pulley member 14b is performed by this torque cam mechanism. Further, a pulley clamping force is generated by the torque cam mechanism and the spring 56. Since the torque cam mechanism generates a pulley clamping force according to the transmission torque, it is effective in preventing excessive slip (gross slip) at the contact portion between the pulley and the toothed ring due to torque increase. The torque cam mechanism is not limited to the one exemplified here, for example, a roller may be used as a rolling element, and a type that does not use a rolling element is also possible.

  The applied pressure generated by the torque cam depends on the angle of the cam curve, and it is generally difficult for the torque cam alone to achieve both increased applied pressure and increased axial movement. The addition of a mechanism for moving the entire torque cam mechanism is effective for achieving this, and the embodiment shown in FIG. 2 is an example in which a combination of a feed screw and an actuator is employed as the mechanism for this purpose. The feed screw includes a nut 58 that is rotatably installed on the outer periphery of the cam member 54 via a bearing, and a male screw member 60 that is rotatably installed on the rotary shaft 12 via a bearing. A thrust bearing 66 is interposed between the male screw member 60 and the casing 10. Since the nut 58 is engaged with the guide 62 fixed to the casing 10 to prevent rotation, the nut 58 moves in the axial direction when the male screw member 60 rotates.

  An example of means for rotationally driving the male screw member 60 includes an actuator using a motor and a gear transmission mechanism. In the case of FIG. 2, a worm 64 that is rotationally driven by a motor (not shown) meshes with a worm wheel (not indicated) formed on the male screw member 60, and the male screw member 60 is rotated by the rotation of the worm 64.

  A small gear 26 is fixed to the rotary shaft 28. The small gear 26 meshes with the toothed ring 18. The toothed ring 18 has teeth that mesh with the teeth of the small gear 26 and a smooth cylindrical guide surface 20 (see FIG. 6), and the guide surface 20 contacts the guide roller. As shown in FIG. 1, four guide rollers 22a, 22b, 22c, and 22d are provided. In FIG. 2, only two of them, that is, only the guide roller 22a and the guide roller 22d appear. In this way, three or more guide rollers are provided and receive a tangential force acting mainly at the contact portion between the pulleys 14a and 14b and the toothed ring 18 (guide roller 22a), mainly with a large to small gear ratio. When switching the gear, the toothed ring 18 is displaced (guide roller 22b), and when the gear ratio is switched from small to large, the toothed ring 18 is displaced (guide roller 22c). Is desirable.

  Each guide roller is rotatable and axially movable. The guide rollers 22a, 22b, and 22c are attached to the arm 24 via pins and bearings, and FIG. 2 shows an example in which a needle roller bearing is adopted as the bearing. The guide roller 22 d is composed of a pair of disks disposed on both sides of the small gear 26, and can move in the axial direction with respect to the rotating shaft 28 together with the small gear 26. The small gear 26 is connected to the rotating shaft 28 by torque transmitting means that is axially slidable and is not relatively rotatable. FIG. 2 shows an example in which a ball spline 72 is employed as such torque transmission means.

  As shown in FIG. 1, the arm 24 has a ring shape, and guide rollers 22a, 22b, 22c, and 22d are arranged at intervals of approximately 90 °. The positional relationship between these guide rollers is fixed. As shown in FIG. 2, the arm 24 is composed of two plates, and is rotatably supported by the sleeve 30 of the casing 10 coaxially with the rotary shaft 28. Since the toothed ring 18 is constrained from the outer periphery by four guide rollers 22a, 22b, 22c, and 22d, it can rotate without a central axis (coreless roller). By rotating the arm 24 carrying the guide rollers 22a, 22b, 22c, the rotation center O of the toothed ring 18 can be moved around the axis of the rotation shaft 28. The teeth on the outer periphery of the toothed ring 18 are always in mesh with the small gear 26.

  If the pulley members 14a, 14b and the arm 24 are controlled so that there is no gap between the toothed ring 18 and the pulley members 14a, 14b, the toothed ring 18 moves around the axis of the rotary shaft 28. Accordingly, the contact point P with the pulley member 14 is changed, and the speeds of the pulley members 14a and 14b can be continuously changed with respect to the constant rotation speed of the small gear 26. In this way, a so-called CVT is configured.

  For example, when the rotary shaft 12 is on the input side, as shown in FIG. 3, the state in which the toothed ring 18 is pushed inward in the radial direction of the pulley members 14a and 14b is a deceleration state. When a rotational force is input from the pulley members 14a and 14b, a force acts on the toothed ring 18 from the pulley members 14a and 14b, and a force of almost the same magnitude acts on the small gear 26, thereby rotating the rotary shaft 28. The rotation is transmitted to.

  The embodiment shown in FIG. 1 is an example in which a combination of a worm 48 and a worm wheel 50 is adopted as a mechanism for controlling the turning of the arm 24 around the output shaft 28. The worm 48 is rotationally driven by a motor 46. The worm wheel 50 corresponds to a part of a gear, and is attached to the arm 24 so that the pitch circle center coincides with the axis of the output shaft 28. By appropriately setting the worm advance angle and the like, the turning angle of the arm 24 can be maintained even when the motor is not energized, and the gear ratio can be maintained. Further, as shown in FIG. 2, spur gears 68 and 70 are provided coaxially with the worms 48 and 64, respectively, and meshed with each other, so that both worms 48 and 64 can be driven by a single motor 46 (FIG. 1). Can be driven. In this case, the axial load on the drive pulley 14b and the arm 24 operate synchronously. However, since a part of the axial load on the drive pulley 14b is absorbed by the compression coil spring 56, the load on the drive pulley 14b is excessive. Damage is prevented without applying a heavy load.

  A gear transmission system other than the worm and the worm wheel can be employed as the turning drive means of the arm 24. For example, a large gear (or a part thereof) attached to the arm 24 so that the center of the pitch circle coincides with the axis of the output shaft 28 and a small gear meshing with the large gear may be driven by a motor.

Schematic side view of continuously variable transmission showing an embodiment of the present invention 1 is a longitudinal sectional view of the continuously variable transmission of FIG. Side schematic view similar to FIG. 1 showing a low gear ratio state Side schematic diagram of continuously variable transmission showing conventional technology 4 is a longitudinal sectional view of the continuously variable transmission of FIG. Enlarged view of the contact portion between the pulley and the toothed ring in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Casing 12 Rotating shaft 14a Fixed pulley member 14b Movable pulley member 16 Ball spline 18 Toothed ring 20 Guide surface 22a, 22b, 22c, 22d Guide roller 24 Arm 26 Small gear 28 Rotating shaft 30 Sleeve 46 Motor 48 Worm 50 Worm wheel 52 Steel ball 54 Cam member 56 Compression coil spring 58 Nut 60 Male thread member 62 Guide 64 Worm 66 Thrust bearing 68, 70 Spur gear 72 Ball spline

Claims (6)

A second rotating shaft rotatably supported by the casing;
A V pulley constituted by a fixed pulley member fixed to the first rotating shaft and a movable pulley member supported by the first rotating shaft so as to be axially displaceable;
A cam member supported on the first rotating shaft so as to be capable of axial displacement and torque transmission, and a torque cam mechanism interposed between the cam member and the movable pulley member;
A feed screw mechanism for moving the cam member in the axial direction;
A first drive mechanism for driving the feed screw mechanism;
A toothed ring clamped by a V pulley and supported by a plurality of guide rollers on the outer periphery;
A small gear meshing with the toothed ring and supported on the second rotating shaft so as to be axially movable;
An arm that supports a plurality of guide rollers so as to be rotatable and axially displaceable, and is capable of turning about the axis of the second rotation shaft;
A continuously variable transmission having a second drive mechanism for driving the arm to pivot, and driving the first drive mechanism and the second drive mechanism with a single actuator.   The continuously variable transmission according to claim 1, wherein the feed screw mechanism is constituted by a nut that prevents rotation of the cam member through a bearing and a male screw member that is supported by the bearing relative to the input shaft or the casing.   The said 2nd drive mechanism is comprised with the large gear attached to the arm so that a pitch circle center may correspond with the axial center of a 2nd rotating shaft, and the small gear which meshes with the said large gear. Continuously variable transmission.   The continuously variable transmission according to claim 3, wherein the large gear is a worm wheel and the small gear is a worm.   The continuously variable transmission according to any one of claims 2 to 4, wherein the first drive mechanism includes a large gear provided on a male screw member and a small gear meshing with the large gear.   6. The continuously variable transmission according to claim 5, wherein the large gear is a worm wheel and the small gear is a worm.

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