JP2008309241A - Continuously variable transmission - Google Patents

Abstract

A continuously variable transmission having a simple structure and capable of easily preventing occurrence of slip at high speed rotation or high torque transmission.
A transmission rotator 5 is sandwiched between an input rotator 2, an output rotator 3 and a guide rotator 4 having the same taper angle α, and is arranged to support at least three points. The first friction surface 5a of the transmission rotor 5 is in contact with the friction surface 2a of the input rotor 2, and the second friction surface 5b of the transmission rotor 5 is the output rotor 3 and the guide rotation. It is configured to be able to move on the support shaft 9 while being in contact with the friction surfaces 3a, 4a of the body 4.
[Selection] Figure 7

Description

  The present invention relates to a continuously variable transmission, and more particularly to a continuously variable transmission suitable for continuously changing a gear ratio by friction.

  2. Description of the Related Art Conventionally, a friction type using friction is known as one type of continuously variable transmission capable of continuously changing a gear ratio.

  For example, in a vehicle such as a three-wheel or four-wheel vehicle, the driving force of an engine as a prime mover is input to a transmission (transmission) to control the driving force of the engine, and the controlled driving force of the engine is output to the transmission. Front engine / rear drive (FR) type driving force transmission that is input from the shaft to the differential (differential device) via the propeller shaft (propulsion shaft), and the driving force of the prime mover is transmitted to the wheel drive shaft by the differential. A driving force transmission device of a front engine / front drive (FF) system in which a driving force of an engine or an engine is transmitted from an output shaft of a transmission to a wheel driving shaft is used. And continuously variable transmissions, such as a belt type CVT (Continuously Variable Transmission) and toroidal CVT, are put into practical use as a transmission of a driving force transmission device.

  As is well known, the belt type CVT hangs a steel belt with a frame around two pulleys on the input side and the output side, and transmits rotation between the two pulleys on the input side and the output side by the steel belt. The speed ratio is changed by changing the width (groove width) of the two pulleys (see, for example, Patent Document 1).

  As is well known, the toroidal CVT sandwiches a power roller between two disks on the input side and the output side, and friction between the power roller and each of the two disks causes The transmission is transmitted between the disks, and the speed ratio is changed by changing the inclination of the power roller (see, for example, Patent Document 2).

  Also, as a continuously variable transmission using friction, a friction conical wheel is fixed to the input shaft, and a friction conical wheel having a conical direction opposite to the output shaft arranged in parallel to the input shaft is fixed. The intermediate transmission wheel is brought into contact with and separated from the conical wheel so that rotation is transmitted between the two conical wheels on the input side and the output side by friction between the intermediate transmission wheel and the two conical wheels. Some are configured to change the speed ratio by moving along the axial direction of the friction conical wheel (see, for example, Patent Document 3).

JP 2002-054691 A JP 2005-147258 A JP-A-2005-113969

  However, the conventional belt-type CVT has a problem that slip is likely to occur during high-speed rotation due to the centrifugal force caused by the weight of the steel belt.

  Further, in the conventional toroidal CVT, although slip does not easily occur during high-speed rotation or high torque transmission, there is a problem that the structure is complicated, the accuracy of parts is high, and the manufacturing cost tends to be high.

  Further, in the continuously variable transmission using the conventional friction cone wheel, the intermediate transmission wheel is brought into contact with the two friction cone wheels from the outer peripheral surface side of both friction cone wheels so as to be freely contacted and separated. There is a problem that the support shaft mechanism for moving the support shaft for supporting the intermediate transmission vehicle is required so that the intermediate transmission vehicle is brought into contact with and away from both friction cone wheels, the structure is complicated, and the device becomes large. . Furthermore, since the intermediate transmission wheel is brought into contact with the two friction cones so as to be freely contacted and separated from the outer peripheral surface side of both friction cones, slip is likely to occur during high-speed rotation and high torque transmission. There was a problem. Furthermore, at the time of starting rotation, the starting torque applied to the intermediate transmission vehicle applies a force in the direction of separating the intermediate transmission vehicle from the friction conical wheel so that the support shaft supporting the intermediate transmission vehicle bends along the axial direction. Therefore, there is a problem that it is easily deformed and slip is more likely to occur.

  Accordingly, there is a need for a continuously variable transmission that has a simple structure and can easily prevent slippage during high-speed rotation or high-torque transmission.

  The present invention has been made in view of this point, and it is an object of the present invention to provide a continuously variable transmission that has a simple structure and can easily prevent occurrence of slip at high speed rotation or high torque transmission. To do.

  In order to achieve the above-described object, the continuously variable transmission according to the present invention is characterized in that an input rotator that is coaxially attached to a rotationally driven input shaft and has an outer peripheral surface formed as a tapered friction surface, An output rotating body that is coaxially attached to the rotatable output shaft and has a tapered friction surface on the outer periphery, and a coaxial and rotatable attachment on the guide shaft that has a tapered friction surface on the outer periphery. In order to transmit the rotation of the input shaft and the input shaft to the output shaft, it is attached to the support shaft so as to be rotatable and movable along the axial direction of the support shaft. A tapered first friction surface abutted on the friction surface of the input rotator, and a tapered second friction surface abutted on the friction surfaces of the output rotator and the guide rotator. A rotating body for transmission comprising A transmission rotating body moving means for moving the rotating body along the axial direction on the support shaft, and the support shaft includes the input rotating body, the output rotating body, and the guide rotating body. The input rotator, the output rotator, and the guide rotator have the same taper angle of the friction surfaces, and the friction of the input rotator. The taper direction of the friction surface of each of the output rotator and the guide rotator is opposite to the taper direction of the surface, and supports at least three points with the transmission rotator interposed therebetween. The transmission rotator moving means is configured such that the first friction surface of the transmission rotator is in contact with the friction surface of the input rotator and the transmission rotator first 2 friction surface is the output In that the respective friction surface of the rotating body and the guide rotary member is configured so as to be movable on the support shaft while in contact there. Further, by adopting such a configuration, the input rotator, the output rotator, the guide rotator, and the transmission rotator that abuts each of them are mainly configured. In addition, since the transmission rotator is sandwiched between and supported by at least three rotators: an input rotator, an output rotator, and a guide rotator. Further, it is possible to easily prevent the occurrence of slip when transmitting high torque.

  In order to increase the contact force between the friction surface of the input rotator and the first friction surface of the transmission rotator, the input rotator is moved along the axial direction on the input shaft. It is preferable that a body moving means is provided. By adopting such a configuration, the contact force between the friction surface of the input rotor and the first friction surface of the transmission rotor is increased, so that slip at the time of high speed rotation and high torque transmission is increased. Occurrence can be easily and more reliably prevented.

  The input rotator moving means includes a slide mechanism disposed between the input rotator and the input shaft, a stopper attached to the input shaft, one end abutting the stopper, and the other end A spring member that is in contact with the small-diameter end of the input rotator and that is extendable along the axial direction of the input shaft; and the input rotator disposed on the large-diameter side of the input rotator It is preferable to have an actuator that moves along the longitudinal direction of the input shaft. By adopting such a configuration, in order to increase the abutting force between the friction surface of the input rotator and the first friction surface of the transmission rotator, the input rotator is axially moved on the input shaft. It can be easily and reliably moved with a simple structure.

  It is preferable that the input rotating body moving means is formed so that the rotation of the input shaft can be transmitted to the input rotating body. By adopting such a configuration, it is possible to easily and reliably rotate the input rotating body integrally with the rotation of the input shaft.

  The transmission rotator is disposed to face an input side transmission ring having an outer peripheral surface as the first friction surface and a large diameter side of the input side transmission ring with an interval, and the outer peripheral surface is the second friction surface. An output-side transmission ring, a plurality of coupling teeth arranged along the circumferential direction on each of the opposing surfaces of the two transmission rings and meshing with each other between the opposing surfaces of the two transmission rings, A preload spring member disposed between the opposing surfaces of the transmission rings and sandwiched by the opposing surfaces of the two transmission rings and biasing the transmission rings away from each other; and the opposite side of the opposing surfaces of the two transmission rings Torque receiving spring members arranged so as to abut each of the end faces of each of the two end faces through thrust bearings and biasing the two transmission rings toward each other, and the two transmission rings being rotatable via radial bearings Support And a cylindrical ring holder for holding both the torque receiving spring members, and an angle formed between the axis of the ring holder and the axis of the support shaft has the same angle as the taper angle. The connecting teeth are formed within an angle of 10 to 45 ° between the large-diameter end surface of the input-side transmission ring and the contact tangent of the teeth meshing with each other, The transmission rotating body moving means includes a feed screw mechanism disposed between the support shaft and the ring holder, and an actuator that is disposed on one end side of the support shaft and rotationally drives the support shaft. Preferably it is. By adopting such a configuration, the transmission rotating body self-holds the position on the support shaft by a configuration in which the axis of the ring holder is inclined with respect to the axis of the support shaft at the same angle as the taper angle. can do. Further, it is possible to prevent a speed change due to the movement of the position on the support shaft. Further, since it is possible to prevent a difference in rotational speed between the large diameter side and the small diameter side at the contact portion between the first friction surface and the friction surface of the input rotor, the large diameter side and the small diameter at the contact portion can be prevented. There is no micro-slip on the side. Furthermore, a plurality of coupling teeth having an angle between the large-diameter end surface of the input-side transmission ring and the contact tangent of the teeth meshing with each other between the opposing surfaces of both transmission rings are meshed. The structure that connects the rotating body and the rotating body for input and the rotating body for input, the rotating body for output, and the rotating body for guide can increase the abutting force at the abutting portion to prevent slipping. The rotating body moving means is configured such that the first friction surface of the transmitting rotating body is in contact with the friction surface of the input rotating body, and the second friction surface of the transmitting rotating body is the output rotating body and the guide rotating body. It is possible to easily and reliably move the support shaft while abutting against each friction surface with a simple structure.

  The feed screw mechanism includes a ball screw having a plurality of balls that circulate and move in a ball circulation path formed between the screw shaft and the nut, the support shaft being a screw shaft, the ring holder being a nut. It is preferable that By adopting such a configuration, it is possible to easily and reliably move the transmission rotator along the axial direction on the support shaft with a simple structure.

  A contact portion between the friction surface of the input rotor and the first friction surface of the transmission rotor; a contact portion between the friction surface of the output rotor and the second friction surface of the transmission rotor; It is preferable that each of the contact portions between the friction surface of the guide rotator and the second friction surface of the transmission rotator is in contact via a lubricating film. And by employ | adopting such a structure, rotation can be transmitted effectively and abrasion of each contact part can be reduced.

  According to the continuously variable transmission according to the present invention, an input rotator, an output rotator, a guide rotator, and a transmission rotator that abuts each of them are mainly configured. There are excellent effects such as. In addition, since the outer peripheral surface of the transmission rotating body is sandwiched and supported by the three rotating bodies of the input rotating body, the output rotating body, and the guide rotating body, they are in contact with each other. There are excellent effects such as the ability to easily prevent the occurrence of slip during torque transmission.

  The present invention will be described below with reference to embodiments shown in the drawings.

  First, a basic configuration of an embodiment of a continuously variable transmission according to the present invention will be described with reference to FIGS.

  1 to 5 show a basic configuration of an embodiment of a continuously variable transmission according to the present invention. FIG. 1 is a schematic front view of a main part, FIG. 2 is a schematic plan view of FIG. 1 is a schematic side view of FIG. 1, FIG. 4 is a schematic side view showing the rotating body for guide shown in FIG. 1, and FIG. 5 is a schematic cross-sectional view taken along line AA of FIG.

  As shown in FIGS. 1 to 5, the basic configuration of the continuously variable transmission 1 of the present embodiment includes an input rotary body 2, an output rotary body 3, and a guide rotary body 4 as three friction cone wheels, A transmission rotator 5 as a friction conical wheel for transmitting the rotation of the input rotator 2 to the output rotator 3 is mainly configured.

  The input rotator 2, the output rotator 3, and the guide rotator 4 are each formed in a truncated cone shape with a taper angle α having the same shape, and each outer peripheral surface is tapered. The friction surfaces 2a, 3a, and 4a. The input rotator 2, the output rotator 3, and the guide rotator 4 may have different sizes as long as the taper angle α is the same.

  The input rotator 2 is coaxially attached to an input shaft 6 that is rotated by receiving a driving force transmitted from a prime mover, and the output rotator 3 is coaxial with a rotatable output shaft 7. The guide rotating body 4 is coaxially and rotatably attached to the guide shaft 8 via a bearing (not shown) (FIG. 5).

  Therefore, the rotation center of the input rotating body 2 is coaxially arranged on the axis 10 of the input shaft 6, and the rotation center of the output rotating body 3 is coaxially arranged on the axis 11 of the output shaft 7, The rotation center of the rotating body 4 is arranged coaxially on the axis 12 of the guide shaft 8 (FIG. 5). The guide rotator 4 may be attached to the guide shaft 8 so that the guide shaft 8 is supported rotatably, or the guide rotator 4 may be formed integrally with the guide shaft 8 and supported rotatably. It is good.

  The transmission rotator 5 is generally formed in a middle-thick cylindrical shape with a large diameter in the center in the axial direction and a small diameter at both ends, and the outer peripheral surface shown on the right side of FIG. The first friction surface 5a is tapered so as to be in contact with the friction surface 2a of the rotator 2. The outer peripheral surface shown on the left side (lower side in FIG. 2) of FIG. 3 is the output rotator 3 and the guide. A tapered second friction surface 5b is provided in contact with each friction surface 3a, 4a of the rotating body 4. The transmission rotator 5 is sandwiched between the input rotator 2, the output rotator 3, and the guide rotator 4, and is supported at three points (FIG. 5).

  Note that the number of the guide rotating bodies 4 may be two or more. In this case, the transmission rotator 5 is supported at four or more points. That is, it is only necessary that the transmission rotator 5 is supported at least at three points.

  The input rotator 2 has a large-diameter portion located on the front side in FIG. 1 (lower side in FIG. 2, left side in FIG. 3), and a small-diameter portion in the rear side in FIG. 1 (upper side in FIG. 2, right side in FIG. 3). ), The axis 10 is disposed so as to extend horizontally. The output rotator 3 is arranged on the lower left side of the input rotator 2 in FIG. 1 so as to face the input rotator 2, and the lower right side of FIG. The guide rotator 4 is arranged so as to face the input rotator 2. Further, the taper directions of the friction surfaces 3a and 4a of the output rotator 3 and the guide rotator 4 are opposite to the taper direction of the friction surface 2a of the input rotator 2, respectively. . That is, the output rotating body 3 and the guide rotating body 4 are arranged on the small diameter side of the input rotating body 2, and the output rotating body 3 and the guide are arranged on the small diameter side of the input rotating body 2. Each large-diameter portion side of the rotating body 4 is disposed. The positions of the output rotator 3 and the guide rotator 4 may be reversed.

  As shown in FIG. 4, the axis 11 of the output rotator 3 is at a lower angle with respect to the virtual reference line 14A parallel to the axis 10 of the input rotator 2 as seen from the side. In addition to being inclined with β, as shown in FIG. 2, the small-diameter portion side is inclined with a lateral angle γ inwardly approaching the small-diameter portion side of the guide rotating body 4 as viewed from above. That is, the axis 11 of the output rotator 3 is inclined with respect to the axis 10 of the input rotator 2 with a lower angle β and a lateral angle γ.

  As shown in FIG. 3, the axis 12 of the guide rotator 4 is at a lower angle with respect to the virtual reference line 14B parallel to the axis 10 of the input rotator 2 as seen from the side. In addition to being inclined with β, as shown in FIG. 2, the small-diameter portion side is inclined with a lateral angle γ inwardly approaching the small-diameter portion side of the output rotating body 3 as viewed from above. That is, the axis 12 of the guide rotator 4 is inclined with respect to the axis 10 of the input rotator 2 with a lower angle β and a lateral angle γ.

  In this manner, the axes 11 and 12 of the output rotator 3 and the guide rotator 4 are inclined with respect to the axis 10 of the input rotator 2 with the lower angle β and the lateral angle γ, thereby transmitting the signal. The rotating body 5 is configured such that the first friction surface 5a of the transmission rotating body 5 is in contact with the friction surface 2a of the input rotating body 2, and the second friction surface 5b of the transmission rotating body 5 is the output rotating body 3. The guide rotating body 4 can move linearly while being in contact with the friction surfaces 3a and 4a.

  As shown in FIGS. 3 and 4, the movement trajectory at the center of the transmission rotator 5 is formed in a straight line having a movement inclination angle δ that rises to the right when viewed from the side. The taper angle α is the same. Further, the movement locus of the center of the transmission rotator 5 is the axis 13 of the support shaft 9 to which the transmission rotator 5 is attached. In other words, the support shaft 9 is inclined with a moving inclination angle δ.

  When the transmission rotator 5 moves in contact with the input rotator 2, the output rotator 3, and the guide rotator 4, the first friction surface 5a and the friction surface 2a of the input rotator 2 The first contact line 15 that is the contact portion of the second friction line 5b, the second contact line 16 that is the contact portion of the second friction surface 5b and the friction surface of the output rotating body 3, and the second friction surface 5b and the guide rotation. The third contact line 17, which is a contact portion with the friction surface of the body 4, and the movement locus of the center of the transmission rotating body 5, that is, the axis 13 of the support shaft 9 are respectively linear and mutually It is arranged in parallel with.

  Here, the lower angle β and the lateral angle γ of the axes 11 and 12 of the output rotator 3 and the guide rotator 4 will be described with reference to FIG.

  FIG. 6 is an explanatory diagram for explaining the lower angle and the lateral angle of the respective axes of the output rotator and the guide rotator in the embodiment of the continuously variable transmission according to the present invention.

  The lower angle β and the lateral angle γ are components necessary for the transmission rotator 5 to move while being in contact with the input rotator 2, the output rotator 3, and the guide rotator 4, respectively. As shown in FIG. 6, when the output rotator 3 and the guide rotator 4 are cones, the diameter of the base of the cone is D, the length (height) of the cone is L, and the taper angle of the cone is α. To do. A contact point P is set on the outer periphery of the bottom of the cone. Then, the distance shown in the vertical direction in FIG. 6 from the contact point P to the outer periphery of the base is x, the distance shown in the vertical direction in FIG. 6 from the center of the cone to the contact point P is y, and from the center of the cone to the contact point P. The distance shown in FIG. 6 in the left-right direction is z. Further, the angle formed between the center line CL of FIG. 6 of the cone and the inclined line SA long in the horizontal direction of FIG. 6 connecting the apex of the cone and the contact point P is θ.

  Therefore, the lower angles β for tilting the axes 11 and 12 of the output rotator 3 and the guide rotator 4 downward are β = (α−θ) and tan θ = y / L, and the output rotator 3 The lateral angle γ for inclining the respective axes 11 and 12 of the guide rotator 4 inward is tan γ = z / L · cos (α−θ).

  Note that each of α, D, z, y, and L is set in the initial design according to the design concept and the specification of the apparatus.

  As the materials of the input rotator 2, the output rotator 3, the guide rotator 4, and the transmission rotator 5, steel materials having high wear resistance and high strength against friction are generally used as in the prior art. It is used for. In addition, you may perform hardening processing, such as carburizing, nitriding, induction hardening, and gas hardening, to the outer peripheral surface used as a friction part.

  Further, the input rotator 2, the output rotator 3, the guide rotator 4, and the transmission rotator 5 are configured such that the outer peripheral surface serving as the friction portion and the other portions are integrally formed of different materials. Also good.

  Furthermore, in order to improve the wear resistance of each of the rotating bodies 2, 3, 4, and 5 and thus the durability of the continuously variable transmission 1, a lubricating film is formed on the contact portion of each of the rotating bodies 2, 3, 4, and 5. It is good to intervene.

  Next, the continuously variable transmission 1 of the present embodiment will be specifically described with reference to FIG.

  FIG. 7 is a schematic configuration diagram showing a main part of an embodiment of a continuously variable transmission according to the present invention. For convenience of explanation, FIG. 7 is a state cut along the line BB in FIG. 5, and unlike the actual case, the axis 11 of the output rotating body 3 and the axis 12 of the input rotating body 2 Are shown in parallel.

  The continuously variable transmission 1 of the present embodiment is exemplified for use in an automobile transmission.

  As shown in FIG. 7, the continuously variable transmission 1 of the present embodiment includes an input rotary body 2 and an output rotary body 3 as three friction conical wheels in a mission case 21, and a guide omitted in the drawing. The rotating body 4 for transmission (see FIG. 1) and the rotating body 5 for transmitting the rotation of the rotating body 2 for input to the rotating body 3 for output are arranged.

  The arrangement of the input rotator 2, the output rotator 3, the guide rotator 4, and the transmission rotator 5 disposed in the mission case 21 has been described in the basic configuration described above. The explanation is omitted.

  The input rotary body 2 is disposed so as to extend horizontally inside the mission case 21 and is coaxially attached to an input shaft 6 that is rotatably supported by a bearing (not shown). Further, the input rotating body 2 has a small diameter portion arranged on the right side of FIG. 7 and a large diameter portion arranged on the left side of FIG. 7 on the input shaft 6. Further, the input rotator 2 is movable on the input shaft 6 along the direction of the axis 10 by a plurality of steel balls 22 arranged between the input shaft 6 as a slide mechanism and the input rotator 2. A spline or serration (not shown) formed on the mutually facing surfaces of the input shaft 6 and the input rotating body 2 as a driving force transmission mechanism is mounted around the axis 10 by a tooth and groove. It is formed so that it can rotate integrally along the direction. Further, the input shaft 6 is formed so that a driving force of a prime mover (not shown) is transmitted. When the driving force of the prime mover is input to the input shaft 6, the input rotator 2 is integrated with the input shaft 6. And is formed to rotate.

  A right end surface, which is a small diameter end of the input rotating body 2, is in contact with a left end surface of a spring member 23 attached to the input shaft 6. The spring member 23 is formed in an annular shape having a cross-sectional C shape as a whole by disposing the two disc springs so that the large-diameter portions thereof are opposed to each other, and extends along the direction of the axis 10 of the input shaft 6. And can be stretched. A right end surface of the spring member 23 is in contact with a left end surface of a stopper 25 made of a retaining ring attached to the right end side of the support shaft 9 via an annular ring plate 24.

  The ring plate 24 may be provided according to the design concept and the like, and is not necessarily required.

  In other words, the spring member 23 only needs to be brought into contact with the stopper 25 directly or via the ring plate 24 and with the left end being the other end in contact with the small-diameter end of the input rotating body 2.

  The spring member 23 may be any member that can expand and contract along the direction of the axis 10 of the input shaft 6. The spring member 23 may be configured such that two disc springs are arranged so that their small diameter portions face each other, or the support shaft 9. When there is a space on the right end side, a configuration using a compression coil spring may be adopted. Moreover, you may combine 3 or more disk springs as needed, such as a design concept.

  At the large diameter end shown on the left side of FIG. 7 of the rotating body 2 for input, there are an inclined surface 26 parallel to the friction surface 2a, and an inner peripheral surface 27 along the axis 10 larger in diameter than the outer periphery of the input shaft 6. Thus, an annular recess 28 having a triangular cross section is formed, and a portion located on the center side of the annular recess 28 is an inner cylindrical portion 29. Further, the left end surface of the inner cylindrical portion 29 is formed so as to be located on the inner side in the direction of the axis 10 (right side in FIG. 7) from the large diameter end of the input rotating body 2, and as a whole looks like a shade of a sideways electric lamp. It is a simple shape. The input rotating body 2 is placed on the left end surface of the inner cylindrical portion 29 along the direction of the axis 10 of the input shaft 6 via a bearing 30 made of a thrust ball bearing or the like that also serves to prevent the plurality of steel balls 22 from coming off. The bearing support 32 connected to the output shaft of the hydraulic cylinder 31 as an actuator to be moved is abutted. The hydraulic cylinder 31 is disposed inside the mission case 21 so as not to interfere with the input shaft 6, and the hydraulic pump 33 that drives the hydraulic cylinder 31 is disposed outside the mission case 21.

  Of course, the actuator may be driven electrically or pneumatically. Then, by driving the hydraulic pump 33 and extending the output shaft of the hydraulic cylinder 31, the input rotary body 2 is shown on the input shaft 6 along the direction of the axis 10 against the spring force of the spring member 23. It is comprised so that it can be moved toward the right side of 7. Further, by moving the input rotator 2 toward the right side in FIG. 7, the contact force between the friction surface 2 a of the input rotator 2 and the first friction surface 5 a of the transmission rotator 5 can be increased. It can be done. The increased contact force can be restored by the biasing force of the spring member 23 by contracting the output shaft after extending the output shaft of the hydraulic cylinder 31.

  By the plurality of steel balls 22, the stopper 25, the spring member 23, and the hydraulic cylinder 31 as the slide mechanism, the friction surface 2a of the input rotating body 2 and the first friction surface 5a of the transmitting rotating body 5 according to the present embodiment. In order to increase the abutting force, an input rotator moving means 34 is configured to move the input rotator 2 along the direction of the axis 10 on the input shaft 6.

  In the present embodiment, the plurality of steel balls 22 are arranged between the opposing surfaces of the splines or serrations, and the input rotary body 2 can be moved on the input shaft 6 along the axial direction. The rotation of the input shaft 6 can be transmitted to the input rotator 2. That is, the input rotating body moving means 34 of the present embodiment is formed so as to be able to transmit the rotation of the input shaft 6 to the input rotating body 2.

  Below the input rotator 2, an output rotator 3 and a guide rotator 4 (not shown in FIG. 7) are tapered on the friction surface 2a of the input rotator 2 in the same manner as the basic structure described above. The direction of taper of the friction surfaces 3a and 4a of the output rotator 3 and the guide rotator 4 is opposite to the direction, that is, the smaller diameter side of the output rotator 3 and the guide rotator 4 is shown in FIG. The large-diameter portion side is positioned so as to be positioned on the right side of FIG. 7, and is disposed so as to support at least three points with the transmission rotating body 5 interposed therebetween (see FIG. 1).

  The output rotator 3 is coaxially attached to the output shaft 7 so as to rotate integrally therewith, and the output shaft 7 is rotatably supported inside a mission case 21 by a bearing (not shown). . Further, the output from the output shaft 7 is transmitted to the axle via a transmission mechanism (not shown).

  The guide rotating body 4 is coaxially attached to and supported by a guide shaft 8 by a bearing (not shown), and the guide shaft 8 is attached and fixed inside the mission case 21.

  The output shaft 7 may be rotatably supported inside the mission case 21 by a bearing (not shown), and the guide rotating body 4 may be fixed to the guide shaft 8.

  The transmission rotator 5 is disposed inside the mission case 21 and is attached to a support shaft 9 that is rotatably supported by a bearing (not shown). Further, the transmission rotator 5 includes a tapered first friction surface 5a in contact with the friction surface 2a of the input rotator 2 shown on the right side of FIG. 7, and an output rotator 3 shown on the left side of FIG. And a tapered second friction surface 5b that comes into contact with the friction surfaces 3a and 4a of the guide rotator 4, respectively. Further, the support shaft 9 is a screw shaft in which a thread groove (not shown) is formed on the outer peripheral surface excluding both end portions. The support shaft 9 is a hydraulic motor as an actuator disposed outside the transmission case 21. It is formed so as to be rotationally driven in the forward rotation direction and the reverse rotation direction by the driving force of 36. Of course, the actuator may be an electric drive or pneumatic drive motor. However, in a cylinder such as a hydraulic cylinder that is linearly driven, the stroke of the output shaft is the maximum moving distance of the transmission rotating body 5 that moves on the support shaft 9 necessary for shifting. This is not preferable because it requires space and the apparatus becomes large.

  Here, the transmission rotator 5 and the support shaft 9 will be further described with reference to FIGS.

  FIG. 8 is a schematic enlarged half sectional view showing the main part in the vicinity of the transmission rotator, and FIG. 9 is a schematic front view showing the vicinity of the connecting tooth in FIG.

  As shown in FIG. 8, the transmission rotator 5 of this embodiment includes an input side transmission ring 41 in which the outer peripheral surface shown on the right side of FIG. 8 is a tapered first friction surface 5a, and the left side of FIG. The output side transmission ring 42 made into the 2nd friction surface 5b which makes the outer peripheral surface shown in FIG. And the input side transmission ring 41 and the output side transmission ring 42 are opposingly arranged at intervals so that each large diameter side may oppose. That is, the output-side transmission ring 42 is disposed so that the large-diameter side thereof is opposed to the large-diameter side of the input-side transmission ring 41 with an interval. The transmission rings 41 and 42 are respectively connected to a ring mounting portion 45 that is annularly recessed on the outer peripheral surface of a ring holder 44 formed in a substantially cylindrical shape via a radial bearing 43 formed of a needle roller bearing or the like. Arranged and supported rotatably.

  The ring holder 44 of this embodiment includes a holder body 44a including a left half portion of the ring mounting portion 45 shown on the left side of FIG. 8, and a right side of the ring mounting portion 45 attached to the holder body 44a and shown on the right side of FIG. The ring-shaped sub-ring 44b having an inverted L-shaped cross section is formed in two so as to include a half portion.

  A plurality of connecting teeth 46 (only part of which are shown in the figure) meshed with each other are provided along the circumferential direction on the opposing surfaces which are end surfaces on the large diameter side of the input side transmission ring 41 and the output side transmission ring 42. It is arranged. As shown in FIG. 9, these coupling teeth 46 are engaged with each other between the opposing surfaces of both transmission rings 41, 42 (only a part is shown in FIG. 9). Further, the connecting teeth 46 are meshed with each other at an angle ε between the large-diameter end surface of the input side transmission ring 41 and the contact tangents of the teeth meshing with each other.

  Returning to FIG. 8, a preload spring member 47 is disposed between the opposing surfaces of the transmission rings 41 and 42. The preload spring member 47 is formed in an annular shape having a V-shaped cross section, and is disposed inside the formation region of the connecting teeth 46 on the opposing surfaces of the transmission rings 41 and 42. The preload spring member 47 is extendable along the axial direction shown in the left-right direction in FIG. 8, and is sandwiched between the opposing surfaces of the transmission rings 41, 42, and the transmission rings 41, 42 are connected to each other. It is possible to urge in directions away from each other.

  Each of the end faces opposite to the opposing faces of the transmission rings 41 and 42, more specifically, the right end face shown on the right side of the input side transmission ring 41 in FIG. 8 and the left end of the output side transmission ring 42 shown on the left side in FIG. One end surface of a thrust bearing 48 made of a thrust needle roller bearing or the like is in contact with each of the surfaces. The other end face of these thrust bearings 48 is in contact with the end face on the outer peripheral face side of a torque receiving spring member 50 formed in a substantially disc spring shape through an annular guide ring 49. The inner peripheral surface of the torque receiving spring member 50 is held in contact with the bottom corner of the ring mounting portion 45 of the ring holder 44, and the torque receiving spring member 50 holds both transmission rings 41 and 42 together. The ring holders 44 are arranged in the ring mounting portion 45 so as to be biased in directions approaching each other.

  That is, the torque receiving spring member 50 is disposed so as to abut each of the end surfaces opposite to the opposing surfaces of the two transmission rings 41, 42 via the thrust bearing 48, so that the two transmission rings 41, 42 are mutually connected. It can be urged in the direction approaching.

  Therefore, the transmission rotator 5 is disposed to face the input-side transmission ring 41 whose outer peripheral surface is the first friction surface 5a and the large-diameter side of the input-side transmission ring 41 at an interval, and the outer peripheral surface is the second outer surface. The output side transmission ring 42 that is the friction surface 5b and the opposing surfaces of the two transmission rings 41, 42 are arranged along the circumferential direction, and meshed with each other between the opposing surfaces of the two transmission rings 41, 42 in advance. A plurality of connecting teeth 46 having a set angle ε are disposed between the opposing surfaces of the transmission rings 41 and 42 and are sandwiched between the opposing surfaces of the transmission rings 41 and 42. The two transmission rings are arranged so as to come into contact with the preloading spring member 47 for biasing them in a direction away from each other and the end surfaces opposite to the opposing surfaces of the transmission rings 41 and 42 via the thrust bearings 48, respectively. 41 Torque receiving spring member 50 that urges 42 in a direction approaching each other, and both transmission rings 41 and 42 are rotatably supported via radial bearings 43, and both torque receiving spring members 50 are held. A cylindrical ring holder 44 is provided.

  The rotation centers of the transmission rings 41 and 42 are arranged coaxially with an axis 51 that is the center line of the inner hole of the ring holder 44, and the axis 51 of the ring holder 44 is relative to the axis 13 of the support shaft 9. Thus, the input side transmission ring 41 side is inclined with an angle η so that the input side transmission ring 41 side is on the upper side. This angle η is the same as the taper angle α. That is, the axis 51 of the ring holder 44 serving as the rotation center of the transmission rings 41 and 42 is inclined with an angle η formed by the axis 13 of the support shaft 9 being the same as the taper angle α (η = α). ing.

  The preload spring member 47 and the torque receiving spring member 50 may be any one that can expand and contract along the rotation centers of the two transmission rings 41 and 42. When there is a space in the direction along the rotation center of the transmission rings 41 and 42, a configuration using a compression coil spring may be used.

  A feed screw mechanism 52 is disposed between the ring holder 44 and the support shaft 9. The feed screw mechanism 52 of the present embodiment includes a plurality of balls that circulate and move in a ball circulation path formed between the screw shaft and the nut, with the support shaft 9 as a screw shaft and the ring holder 44 as a nut. It is composed of a ball screw, and the support shaft 9 is driven to rotate in the forward rotation direction and the reverse rotation direction by the driving force of the hydraulic motor 36, so that the ring holder 44, and consequently the transmission rotating body 5, is axially moved on the support shaft 9. It is comprised so that it can be reciprocated along 13 directions.

  The ball circulation path may be an internal circulation system or an external circulation system.

  The feed screw mechanism 52 disposed between the support shaft 9 and the ring holder 44 and the hydraulic motor 36 serving as an actuator that is disposed on one end side of the support shaft 9 and rotationally drives the support shaft 9 are used in the present embodiment. A transmitting rotator 5 moving means is configured to enable the transmitting rotator 5 to move on the support shaft 9 along the direction of the axis 13 thereof.

  Note that, in the continuously variable transmission 1 of the present embodiment, as described above, in order to improve the wear resistance of each of the rotating bodies 2, 3, 4, and 5 and consequently the durability of the continuously variable transmission 1, A lubricating film may be interposed between the contact portions of the rotating bodies 2, 3, 4, and 5.

  That is, the contact portion between the friction surface 2 a of the input rotator 2 and the first friction surface 5 a of the transmission rotator 5, the friction surface 3 a of the output rotator 3 and the second friction surface 5 b of the transmission rotator 5. It is preferable that a lubricating film (not shown) is interposed in each of the contact portion between the friction surface 4a of the guide rotator 4 and the second friction surface 5b of the transmission rotator 5.

  Next, the operation of the present embodiment having the above-described configuration will be described.

  According to the continuously variable transmission 1 of the present embodiment, when the prime mover is driven and the driving force of the prime mover is transmitted to the input shaft 6, the input shaft 6 starts to rotate integrally with the input rotator 2. . The rotation of the input rotator 2 is transmitted to the output rotator 3 and the guide rotator 4 via the transmission rotator 5, and the output rotator 3 rotates integrally with the output shaft 7. At the same time, the guide rotating body 4 rotates.

  At this time, since the input rotator 2, the output rotator 3, and the guide rotator 4 are disposed so as to support at least three points with the transmission rotator 5 interposed therebetween, the transmission rotator 5 is supported. It is possible to prevent the support shaft 9 from being deformed so as to bend along the direction of the axis 13, and it is possible to prevent a slip from occurring during high-speed rotation or high torque transmission.

  Here, when the transmission rotator 5 is positioned on the small-diameter portion side (right side in FIG. 7) of the input rotator 2, the input rotator 2 abutting on the first friction surface 5 a of the transmission rotator 5. The diameter of the friction surface 2a is smaller than the diameter of the friction surface 3a of the output rotating body 3 in contact with the second friction surface 5b of the transmission rotating body 5, so that the output surface with respect to the rotation of the input rotating body 2 is used. The rotation of the rotating body 3 is decelerated.

  Further, when the transmission rotator 5 is positioned on the large-diameter portion side (left side in FIG. 7) of the input rotator 2, the input rotator 2 in contact with the first friction surface 5 a of the transmission rotator 5. The diameter of the friction surface 2 a is larger than the diameter of the friction surface 3 a of the output rotating body 3 that contacts the second friction surface 5 b of the transmission rotating body 5. The rotation of the rotating body 3 is increased.

  Accordingly, the transmission rotating body 5 is output while the first friction surface 5a of the transmission rotating body 5 is in contact with the friction surface 2a of the input rotating body 2 and the second friction surface 5b of the transmission rotating body 5 is output. By rotating along the direction of the axis 13 of the support shaft 9 while abutting against the friction surfaces 3a, 4a of the rotating body 3 for guide and the rotating body 4 for guide, the rotation on the input side is smoothly stepless on the output side. It can be shifted.

  Note that the speed ratio of the rotation of the output rotator 3 relative to the rotation of the input rotator 2 is N for the number of rotations of the input rotator 2, n for the number of rotations of the output rotator 3, and The output rotator that contacts the second friction surface 5b of the transmission rotator 5 has a maximum diameter Dmax and a minimum diameter Dmin at the contact portion of the friction surface 2a of the input rotator 2 that contacts the first friction surface 5a. 3 can be expressed as n / N = ((Dmax + Dmin) / 2) / ((dmax + dmin) / 2) where dmax is the maximum diameter at the contact portion of the friction surface 3a and dmin is the minimum diameter.

  Therefore, by increasing the taper angle α, it is possible to easily set a large gear ratio without providing a reduction gear.

  When the rotation of the input rotator 2 is transmitted to the transmission rotator 5, the input rotator 2 is moved to the right in FIG. By increasing the contact force between the friction surface 2a and the first friction surface 5a of the transmission rotator 5, it is possible to prevent the occurrence of slip.

  Furthermore, the rotation input to the transmission rotator 5 is transferred from the input-side transmission ring 41 to the output-side transmission ring 42 by a plurality of coupling teeth 46 meshing with each other between the opposing surfaces of both transmission rings 41, 42. Communicated.

  At this time, since the radial bearing 43 and the thrust bearing 48 have a very small friction, a reaction force is generated on the support shaft 9 by the input to the input side transmission ring 41. Here, in FIG. 8, the input point to the input side transmission ring 41 is indicated by a black square, the input tangential force is F1, the input point and the axis 51 of the ring holder 44 (the center of rotation of both transmission rings 41, 42). ) Is the distance L1, the input torque is T1, the friction coefficient of the radial bearing 43 is μ1, the friction coefficient of the thrust bearing 48 is μ2, the moment with respect to the input around the ring holder 44 is M1, and the reaction force acting on the support shaft 9 is f1, F1 = T1 / L1, M1 = (μ1 + μ2) · F1 · L1, and f1 = M1 / L2 = (μ1 + μ2) where L2 is the distance between the axis 13 of the support shaft 9 and the axis 51 of the ring holder 44 at the reaction force point. ) · F1 · L1 / L2.

  Here, when the angle η formed by the axis 51 of the ring holder 44 and the axis 13 of the support shaft 9 is 0 °, the feed screw mechanism 52 is disposed between the support shaft 9 and the ring holder 44. Therefore, there arises a disadvantage that the ring holder 44 and, therefore, the transmission rotating body 5 moves on the support shaft 9 with a small force transmitted to the ring holder 44 via the radial bearing 43 and the thrust bearing 48.

  Therefore, the transmission rotating body 5 is prevented from moving on the support shaft 9 by inclining the axis 51 of the ring holder 44 with respect to the axis 13 of the support shaft 9. The inclination angle, that is, the angle η formed by the axis 51 of the ring holder 44 and the axis 13 of the support shaft 9 can be made equal to the taper angle α to reliably cancel the reaction force generated on the support shaft 9. Is preferable in the sense that the reaction force generated on the support shaft 9 can be offset by friction when the transmission rotator 5 attempts to move on the support shaft 9.

  Further, the contact portion between the second friction surface 5b of the output-side transmission ring 42 and the friction surface 3a of the output rotating body 3, and the friction between the second friction surface 5b of the output-side transmission ring 42 and the guide rotating body 4 In each of the contact portions with the surface 4a, a reaction force is generated on the support shaft 9, and these reaction forces also taper an angle η formed by the axis 51 of the ring holder 44 and the axis 13 of the support shaft 9. The angle can be canceled by setting the same angle as the angle α.

  Therefore, by setting the angle η formed by the axis 51 of the ring holder 44 and the axis 13 of the support shaft 9 to be the same as the taper angle α (η = α), the transmission rotator 5 can be mounted on the support shaft 9. The position can be self-held.

  Therefore, it is possible to more reliably and easily prevent slip from occurring during high-speed rotation or high torque transmission.

  Further, the angle η formed by the axis 51 of the ring holder 44 and the axis 13 of the support shaft 9 is set to the same angle (η = α) as the taper angle α, so that transmission on the support shaft 9 is performed for shifting. When the rotating body 5 moves, the transmitting rotating body 5 can be moved smoothly while always maintaining the posture shown in FIG.

  That is, the configuration in which the angle η formed by the axis 51 of the ring holder 44 and the axis 13 of the support shaft 9 is the same as the taper angle α (η = α) is transmitted by driving the transmission rotating body moving means 53. A posture control function for always maintaining the same posture when the rotary body 5 moves on the support shaft 9 is exhibited.

  Further, the angle η formed by the axis 51 of the ring holder 44 and the axis 13 of the support shaft 9 is set to the same angle (η = α) as the taper angle α, so that the speed change due to the movement of the position on the support shaft 9 can be achieved. Can be prevented. Further, since it is possible to prevent a difference in rotational speed between the large diameter side and the small diameter side at the contact portion between the first friction surface 5a and the friction surface 2a of the input rotor 2, the large diameter at the contact portion can be prevented. Small slip does not occur on the side and small diameter side.

  Further, the rotation input to the input side transmission ring 41 is transmitted to the output side transmission ring 42 by a plurality of connecting teeth 46 meshing with each other between the opposing surfaces of both transmission rings 41, 42. In this case, a reaction force indicated by a broken line arrow below the FIG. 9 is generated on the output side transmission ring 42 with respect to the input indicated by the arrow above the input side transmission ring 41 in FIG. This reaction force decreases when the angle ε formed by the large-diameter end face of the input-side transmission ring 41 and the contact tangent of the teeth meshing with each other is large, and increases when the angle ε is small. The reaction force acts in the direction in which both transmission rings 41 and 42 are separated from each other, as indicated by the dashed white arrow on the right side of FIG. 9 and the white arrow on the left side of FIG. The rings 41 and 42 move slightly so as to increase the distance between the opposing surfaces of the two transmission rings 41 and 42. By this movement, the transmission rotating body 5 sandwiched between the input rotating body 2, the output rotating body 3 and the guide rotating body 4 and supported at three points becomes the input rotating body 2 and the output rotating body 2. The function of increasing the abutting force at the abutting portion with each of the rotator 3 and the guide rotator 4 to prevent slipping is exhibited.

  Therefore, it is possible to more reliably and easily prevent slip from occurring during high-speed rotation or high torque transmission.

  The angle ε is 10 to 45 °, preferably 15 to 30 °.

  Therefore, in the continuously variable transmission 1 of the present embodiment, the first configuration is such that the transmission rotating body 5 is sandwiched between the input rotating body 2, the output rotating body 3, and the guide rotating body 4 and is supported at three points. Anti-slip function, a second anti-slip function in which the input rotor 2 moves on the input shaft 6 along the direction of the axis 10, and the axis of the ring holder 44 relative to the axis 13 of the support shaft 9. A plurality of connecting teeth 46 having a third anti-slip function having a configuration in which 51 is inclined with the same angle as the taper angle α and an angle ε set in advance between the opposing surfaces of both transmission rings 41, 42. Four slip prevention functions including a fourth slip prevention function are provided. In addition, by providing four anti-slip functions, even when a lubricating film is interposed in the contact portion of each of the rotating bodies 2, 3, 4, and 5, the occurrence of slip at the contact portion is prevented. it can. That is, it is possible to achieve both friction and lubrication under pressure at the contact portion of each of the rotating bodies 2, 3, 4, and 5, and to prevent occurrence of slip.

  Thus, according to the continuously variable transmission 1 of the present embodiment, the transmission rotator 5 has the same taper angle α, the input rotator 2, the output rotator 3, and the guide rotator 4. The first friction surface 5a of the transmission rotator 5 is in contact with the friction surface 2a of the input rotator 2 and the second of the transmission rotator 5 is interposed between the two. Since the friction surface 5b is configured to move on the support shaft 9 while being in contact with the friction surfaces 3a and 4a of the output rotator 3 and the guide rotator 4, rotation on the input side is performed on the output side. The gear can be smoothly shifted in a stepless manner, the structure is simple, and the occurrence of slip during high-speed rotation or high torque transmission can be easily and reliably prevented.

  Further, according to the continuously variable transmission 1 of the present embodiment, the input rotor is increased in order to increase the contact force between the friction surface 2a of the input rotor 2 and the first friction surface 5a of the transmission rotor 5. 2 is provided on the input shaft 6 along the direction of the axis 10, so that the input rotating body moving means 34 and the input rotating body 2 friction surface 2a and the transmission rotating body 5 first friction surface 5a are provided. Can be easily and more reliably prevented from occurring during high speed rotation and high torque transmission.

  Further, according to the continuously variable transmission 1 of the present embodiment, the input rotating body moving means 34 is connected to the input shaft 6 and the input as a slide mechanism disposed between the input rotating body 2 and the input shaft 6. A plurality of steel balls 22 disposed between the rotating body 2 and a stopper 25 attached to the input shaft 6, one end abutting against the stopper 25 and the other end being a small diameter end of the rotating body 2 for input. The spring member 23 that is in contact with and expandable along the direction of the axis 10 of the input shaft 6 and the input rotary body 2 that is arranged on the large-diameter side of the input rotary body 2 are arranged along the longitudinal direction of the input shaft 6. And the hydraulic cylinder 31 as an actuator to be moved in order to increase the contact force between the friction surface 2a of the input rotary body 2 and the first friction surface 5a of the transmission rotary body 5. It is easy to move the rotating body 2 along the axis 10 direction on the input shaft 6. It can be easily and reliably in a structure.

  Further, according to the continuously variable transmission 1 of the present embodiment, the transmission rotating body has a configuration in which the axis 51 of the ring holder 44 is inclined with respect to the axis 13 of the support shaft 9 at the same angle η as the taper angle α. 5 can self-hold the position on the support shaft 9 and can exhibit a function of preventing a speed change caused by the movement of the position on the support shaft 9, that is, slipping, between the opposing surfaces of the two transmission rings 41 and 42. With a configuration in which a plurality of connecting teeth 46 having a preset angle ε are engaged and connected, the contact portions of the input rotating body 2, the output rotating body 3, and the guide rotating body 4 are in contact with each other. The function of increasing the contact force to prevent slipping can be exhibited. The transmission rotating body moving means 53 is configured so that the first friction surface 5a of the transmission rotating body 5 is in contact with the friction surface 2a of the input rotating body 2 and , Transmission The second friction surface 5b of the rotating body 5 can be moved on the support shaft 9 while being in contact with the friction surfaces 3a and 4a of the output rotating body 3 and the guide rotating body 4, respectively. it can.

  Further, according to the continuously variable transmission 1 of the present embodiment, the feed screw mechanism 52 uses the support shaft 9 as a screw shaft, the ring holder 44 as a nut, and a ball circulation path formed between the screw shaft and the nut. The transmission rotating body 5 can be moved along the direction of the axis 13 on the support shaft 9 easily and reliably with a simple structure. .

  Further, according to the continuously variable transmission 1 of the present embodiment, the contact portion between the friction surface 2 a of the input rotating body 2 and the first friction surface 5 a of the transmission rotating body 5, the friction surface of the output rotating body 3. 3a and the second friction surface 5b of the transmission rotator 5, and the contact portion of the friction surface 4a of the guide rotator 4 and the second friction surface 5b of the transmission rotator 5 are lubricated. By adopting a configuration in which they are in contact with each other through the film, it is possible to improve the wear resistance of each of the rotating bodies 2, 3, 4, and 5 and consequently the durability of the continuously variable transmission 1. That is, it is possible to achieve both friction and lubrication under pressure at the contact portion of each of the rotating bodies 2, 3, 4, and 5, and to prevent occurrence of slip.

  Therefore, according to the continuously variable transmission 1 of the present embodiment, since the structure is simple, it is possible to easily reduce the manufacturing cost, improve the workability at the time of service and maintenance, and prevent fuel consumption by preventing slipping. And the durability of the rotation transmission part can be easily improved.

  The continuously variable transmission of the present invention can be used not only for automobile transmissions but also for various devices that require a speed change function.

  Furthermore, the continuously variable transmission according to the present invention has a wet specification in which a lubricant film is provided at the contact portion of each rotating body for high torque specifications, and a lubricant film at the contact portion of each rotating body for low torque specifications. It can be used properly such as dry specifications.

  The present invention is not limited to the above-described embodiments, and various modifications can be made as necessary.

The typical front view showing the important section of the basic composition of the embodiment of continuously variable transmission concerning the present invention. Schematic plan view of FIG. Schematic side view of FIG. FIG. 1 is a schematic side view showing the rotating body for guide shown in FIG. Schematic cross-sectional view along line AA in FIG. Explanatory drawing explaining the lower angle and lateral angle of each axis of the output rotary body and the guide rotary body in the embodiment of the continuously variable transmission according to the present invention. The schematic block diagram which shows the principal part of embodiment of the continuously variable transmission which concerns on this invention. FIG. 7 is a schematic enlarged half sectional view showing the main part in the vicinity of the transmission rotating body in FIG. Schematic front view showing the vicinity of the connecting teeth in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Continuously variable transmission 2 Input rotating body 2a Friction surface 3 Output rotating body 3a Friction surface 4 Guide rotating body 4a Friction surface 5 Transmission rotating body 5a First friction surface 5b Second friction surface 6 Input shaft 7 Output shaft 8 Guide shaft 9 Support shaft 10 (Input shaft) axis 11 (Output shaft) axis 12 (Guide shaft) axis 13 (Support shaft) axis 21 Mission case 22 Steel ball 23 Spring member 25 Stopper 30 Bearing 31 Hydraulic cylinder 33 Hydraulic pump 34 Rotating body moving means for input 36 Hydraulic motor 41 Input side transmission ring 42 Output side transmission ring 43 Radial bearing 44 Ring holder 46 Connecting teeth 47 Preload spring member 48 Thrust bearing 50 Torque receiving spring member 51 (Ring Axis of holder 52 Feed screw mechanism 53 Rotating body moving means for transmission α Taper angle β Lower angle γ Lateral angle δ Movement inclination angle ε (Formed by the contact tangent of the teeth that mesh with the large-diameter end face of the input-side transmission ring of the connecting tooth) Angle η (Formed by the axis of the ring holder with respect to the axis of the support shaft)

Claims (7)

An input rotator that is coaxially attached to the rotationally driven input shaft and whose outer peripheral surface is a tapered friction surface;
An output rotator that is coaxially attached to a rotatable output shaft and whose outer peripheral surface is a tapered friction surface;
One or a plurality of guide rotating bodies that are coaxially and rotatably attached to the guide shaft, and whose outer peripheral surface is a tapered friction surface;
In order to transmit the rotation of the input shaft to the output shaft, it is attached to the support shaft so as to be rotatable and movable along the axial direction of the support shaft, and is brought into contact with the friction surface of the input rotating body on the outer peripheral surface. A first rotating friction surface, and a transmission rotating body having a tapered second friction surface in contact with the respective friction surfaces of the output rotating body and the guide rotating body,
A transmission rotating body moving means for moving the transmission rotating body along the axial direction on the support shaft;
The support shaft is disposed between the input rotator, the output rotator, and the guide rotator,
The input rotator, the output rotator, and the guide rotator have the same taper angle of the friction surface, and the direction of the taper of the friction surface of the input rotator. The direction of taper of the friction surface of each of the output rotator and the guide rotator is disposed in the opposite direction, and is disposed so as to support at least three points with the transmission rotator interposed therebetween,
The transmission rotating body moving means is configured such that the first friction surface of the transmission rotating body is in contact with the friction surface of the input rotating body, and the second friction surface of the transmission rotating body is the output rotation. A continuously variable transmission configured to be able to move on the support shaft while being in contact with the respective friction surfaces of the body and the guide rotating body.   In order to increase the contact force between the friction surface of the input rotator and the first friction surface of the transmission rotator, the input rotator is moved along the axial direction on the input shaft. The continuously variable transmission according to claim 1, further comprising body moving means.   The input rotator moving means includes a slide mechanism disposed between the input rotator and the input shaft, a stopper attached to the input shaft, one end abutting the stopper, and the other end A spring member that is in contact with the small-diameter end of the input rotator and that is extendable along the axial direction of the input shaft; and the input rotator disposed on the large-diameter side of the input rotator The continuously variable transmission according to claim 2, further comprising an actuator that moves along a longitudinal direction of the input shaft.   4. The continuously variable transmission according to claim 2, wherein the input rotating body moving unit is configured to be able to transmit the rotation of the input shaft to the input rotating body. 5. The transmission rotator is disposed to face an input side transmission ring having an outer peripheral surface as the first friction surface and a large diameter side of the input side transmission ring with an interval, and the outer peripheral surface is the second friction surface. An output-side transmission ring, a plurality of coupling teeth arranged along the circumferential direction on each of the opposing surfaces of the two transmission rings and meshing with each other between the opposing surfaces of the two transmission rings, A preload spring member disposed between the opposing surfaces of the transmission rings and sandwiched by the opposing surfaces of the two transmission rings and biasing the transmission rings away from each other; and the opposite side of the opposing surfaces of the two transmission rings Torque receiving spring members arranged so as to abut each of the end faces of each of the two end faces through thrust bearings and biasing the two transmission rings toward each other, and the two transmission rings being rotatable via radial bearings Support Together, it has a cylindrical ring holder where the spring member for receiving both a torque is maintained,
The angle formed between the axis of the ring holder and the axis of the support shaft is inclined with the same angle as the taper angle,
The connecting teeth are formed such that the angle formed between the large-diameter end face of the input-side transmission ring and the contact tangents of the teeth meshing with each other is in the range of 10 to 45 °.
The transmission rotating body moving means includes a feed screw mechanism disposed between the support shaft and the ring holder, and an actuator disposed on one end side of the support shaft to rotate the support shaft. The continuously variable transmission according to any one of claims 1 to 4, wherein the continuously variable transmission is provided.   The feed screw mechanism includes a ball screw having a plurality of balls that circulate and move in a ball circulation path formed between the screw shaft and the nut, the support shaft being a screw shaft, the ring holder being a nut. The continuously variable transmission according to claim 5, wherein the continuously variable transmission is provided.   A contact portion between the friction surface of the input rotor and the first friction surface of the transmission rotor; a contact portion between the friction surface of the output rotor and the second friction surface of the transmission rotor; 7. A lubricating film is interposed in each of the contact portions between the friction surface of the guide rotator and the second friction surface of the transmission rotator. The continuously variable transmission according to item 1.

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