JPS612959A - Continuously variable transmission - Google Patents

Abstract

PURPOSE:To improve the durability of a continuously variable transmission and prevent creation of both vibration and noise by turning two eccentric rotary bodies, to oscillate carriers in the different phases and taking out those oscillation motions from a transmitting shaft. CONSTITUTION:When an input shaft 7 is turned, a primary eccentric rotary body 27 and a secondary eccentric rotary body 28 start turning and primary and secondary carriers 43 and 50 then start oscillating motion. The oscillating motions of said carriers are taken out as output of a high torque from an output shaft 14 via both a transmission shaft 37 and a speed changing wheel 18. To vary speed change ratio, an operating member 9 has only to be screwed forward or rearward. The rate of eccentricty between the primary and the secondary eccentric rotary bodies are thereby varied so that reduction ratio may be also varied.

Description

[Detailed description of the invention] A0 Purpose of invention (1) Industrial application fields The present invention relates to a continuously variable transmission.

(2) Conventional technology Conventionally, in a continuously variable transmission having a mechanical structure, power is generally generated by bringing a metal ball and a metal cone or disk into contact with each other under great pressure to prevent slippage between them. However, if the gear ratio is kept constant and the gear is operated for a long time, the contact parts will wear out significantly.
The contact parts may be scratched, making it difficult to operate at other gear ratios. In addition, the one-way clutch
・There are some that change speed by changing the loaf length, but wear of the one-way clutch is unavoidable.Secondly, there is little consideration given to the pulsation of the output rotation due to crank motion. There are some transmissions that transmit power using pulleys and belts, but due to their nature, it is not possible to arrange the power shaft and the output shaft on the same line, which makes it difficult to downsize the device and increase the gear ratio. There are some difficulties. Furthermore, although there are transmissions using hydraulic pumps and hydraulic motors, it is difficult to reduce the weight and size of piston-type transmissions, and it is difficult to suppress noise generation with vane-type transmissions.

(3) Problems to be solved by the invention The present invention has been made in view of the above circumstances, and aims to improve durability, prevent pulsation and vibration, suppress noise, achieve a large gear ratio, be compact, and The purpose is to provide a continuously variable transmission with high torque.

B. Structure of the Invention (1) Means for Solving the Problems The continuously variable transmission according to the present invention basically includes: a cylindrical casing; an input shaft rotatably supported at one end of the casing; It has a cylindrical shape, is movable along the input shaft, and is attached to the input shaft so that the amount of eccentricity with respect to the input shaft changes along a direction forming an angle with respect to the input shaft according to the axial movement thereof, a pair of first and second eccentric rotating bodies that rotate together with the input shaft; an output shaft that is arranged concentrically with the input shaft; and a speed changer that is attached to the output shaft to allow movement only in the axial direction. a plurality of transmission shafts arranged parallel to the input shaft at equal circumferential intervals around the input shaft and having one end fixed to the speed change wheel; fitted on the outer periphery of both eccentric rotating bodies; a pair of first and second bearings; a pair of first and second ring bodies surrounding both bearings; arranged parallel to the input shaft with equal intervals in the circumferential direction between the two bearings and the ring bodies; a plurality of first and second support shafts supported by both support shafts and abutting both the ring bodies and both bearings; It is swingable around an axis parallel to the input shaft, and its front end along the rotational direction of the input shaft is connected to both support shafts, and its rear end along the rotational direction is swingable in a direction in which the front end approaches the inner surface of the casing. a plurality of first and second carriers including engaging portions that engage with the transmission shaft during dynamic operation to move the transmission shaft forward in the rotational direction; a plurality of first and second springs that are provided across the respective support shafts on the rear side in the direction and bias each support shaft inward in the radial direction of the casing; and an operating member for moving both eccentric rotors along the input shaft.

(2) Effect The cam action of both eccentric rotating bodies causes each carrier to swing, and each transmission shaft is sequentially moved forward in the rotational direction. This is transmitted to the output shaft via the speed change wheel, and after the speed change output torque is extracted from the output shaft.

(3) Embodiment Hereinafter, an embodiment of the present invention will be explained with reference to the drawings. First, in FIG. 1, a casing 2 of a continuously variable transmission 1 is formed into a bottomed cylindrical shape with an end plate 3 at one end. has been
A bearing 5 is mounted on the inner surface of the boss portion 4 provided at the center of the end plate 3.
The input shaft 7 is rotatably supported via the input shaft 7. Further, a seal member 6 is disposed between the input shaft 7 and the inner surface of the boss portion 4.

On the other hand, a male thread 8 is formed on the other end of the 5 casing 2, and a female thread 10 of a cylindrical operating member 9 is screwed into this male thread 8. A slider 11 is slidably fitted to the other end of the casing 2, and an engagement pin 12 implanted on the outer surface of the slider 11 engages with an annular groove 13 provided on the inner surface of the operating member 9. Therefore, by screwing the operating member 9 forward or backward, the slider 11 moves forward and backward along the axial direction of the casing 2.

An output shaft 14 is arranged on the axial extension of the input shaft 7, and a bearing 1 is placed in a recess 15 provided at the inner end of the output shaft 14.
6, the inner end of the input shaft I is rotatably supported. Furthermore, a spline 17 extending along the axial direction is formed on the outer surface of the output shaft 14.
is engraved.

A spline 19 engraved on the inner surface of the speed change wheel 1B is fitted into this spline 17. The speed change wheel 18 is attached to the output shaft 14 by such spline connection,
The speed change wheel 18 is movable along the axial direction of the output shaft 14.

A seal member 20 and a bearing 21 are interposed between the outer surface of the speed change wheel 18 and the inner surface of the slider 11. Therefore, the speed change wheel 18 and the output shaft 14 are rotatably supported by the slider 11. Moreover, the forward and backward movement of the slider 11 is transmitted to the speed change wheel 18 via the bearing 21, and the speed change wheel 18 moves along the axial direction of the output shaft 14.

Referring also to FIG. 2, in the middle of the input shaft 7, a first angular shaft portion 22 and a second angular shaft portion 23 are provided adjacent to each other in order from the outer end side. The cross section of the first corner shaft portion 22 is formed, for example, in a square shape, and a pair of mutually parallel outer surfaces 22a, 22h are provided with first diagonal keys 24, 24,
are protruding from each other. These diagonal keys 24 rotate in the rotation direction 2 of the input shaft 70 as they move toward the outer end of the input shaft 7.
It is inclined forward along line 5. Further, the cross section of the second square shaft portion 23 is formed in a rectangular shape, and second diagonal keys 26 and 26 are provided protruding from a pair of mutually parallel outer surfaces 23 (1 and 23h). Both outer surfaces 23Q, 23h of the biangular shaft portion 230 are the bilateral surfaces 22α,
22b by an angle α5 of 18 degrees in this example. In addition, the inner and outer surfaces 23Q of the second square shaft portion 23
, 231) is set so that the second corner shaft portion 23 does not protrude to the side of the inner and outer surfaces 22Q and 22b of the first corner shaft portion 22 when the input shaft 7 is viewed from its inner end side. be done. Further, the second diagonal key 26.26 is tilted rearward along the rotational direction 25 as it goes toward the outer end of the input shaft 7, that is, toward the first square shaft portion 22.

A first eccentric rotating body 27 is attached to the first angular shaft portion 22 , and a second eccentric rotating body 28 is attached to the second angular shaft portion 23 . The outer peripheral surfaces of the first and second eccentric rotating bodies 27 and 28 are formed into cylindrical shapes with the same diameter, and the first eccentric rotating body 27 has a first
The first portion slides onto the inner and outer surfaces 220, 221) of the square shaft portion 22.
A rectangular hole 29 is formed in the second eccentric rotating body 28, and a second rectangular hole 30 is formed in the second eccentric rotating body 28 to slide on the inner and outer surfaces 23Q and 23h of the second square shaft portion 23. Furthermore, the inner surface of the first rectangular hole 29 has a first keyway 31. which fits into the first diagonal key 24.24.
31 is bored in the inner surface of the second rectangular hole 30, and a second keyway 32.32 is bored in the inner surface of the second rectangular hole 30 to fit into the second diagonal key 26.26. Therefore, the first and second eccentric rotating bodies 27.2
8 in the axial direction of input l117, the first
The outer peripheral surface of the second eccentric rotating body 27.28 is the outer surface 22Q, 22h of the first and second square shaft portions 22.23;
It is eccentric from the axis of the input shaft 1 along lines 3tt and 23h.

[2, the inner and outer surfaces 22Q, 221); 23Q, 2
The angle formed by 3Q is 18 degrees, and the front diagonal directions of the first and second diagonal keys 24 and 26 are opposite to each other along the axis of the input shaft 7, so that the first and second eccentric rotation Body 27.
When moved in the same direction along the input shaft 7, the centers of the input shafts 28 approach or move away from the axis of the input shaft 7 at positions shifted by 162 degrees (=180-18).

Flange portions 27α, 28a are provided at mutually opposing ends of the first and second eccentric rotating bodies 27, 28, respectively, and these collar portions 27Q, 2BQ are in sliding contact with each other. Furthermore, first and second bearings 33.34 are fitted onto the outer peripheral surfaces of the first and second eccentric rotating bodies 27.28. One end of the outer ring of the first bearing 33 is brought into contact with the support ring 35, and the other end of the inner ring is brought into contact with the flange 27a of the first eccentric rotating body 27.

A bearing 36 is interposed between the support ring 35 and the outer surface of the boss portion 4, and the support ring 35 is rotatably supported by the boss portion 4 and is movable in the axial direction along the outer surface of the bearing 36. It is.

One end of the inner ring of the second bearing 34 is brought into contact with the flange 28Q of the second eccentric rotating body 28, and the other end of the outer ring is brought into contact with the speed change wheel 18.

Referring also to FIG. 3, one ends of a plurality of transmission shafts 37, for example, five, parallel to the input shaft 7 are fitted into the speed change wheel 18 at positions equally spaced in the circumferential direction. These transmission shafts 37 pass through a ring-shaped partition wall 38 disposed centrally between the speed change wheel 18 and the support ring 35, and are respectively coupled to the support ring 35. Therefore, in accordance with the axial movement of the variable speed wheel 18, the first and second eccentric rotating bodies 27.28, the first and second bearings 33.34. The partition wall 38 and the support ring 36 move along the axial direction of the input shaft 7.

A first bearing 33 is located between the partition wall 38 and the support ring 36.
A first ring body 39 surrounding the second bearing 34 is disposed between the partition wall 38 and the speed change wheel 18.
A ring body 40 is arranged.

These ring bodies 39, 40 are formed to have a smaller diameter than the casing 2 and the same diameter.

Between the first bearing 33 and the first ring body 39, each transmission shaft 3
7, a first support 41 parallel to the transmission shaft 37 is disposed between each of them, and a first roller 42 that slides in contact with the outer ring outer surface of the first bearing 33 and the inner surface of the 11th J song 39 is arranged between each of them. It is rotatably supported by a support shaft 41. Also, each sentence
Front ends of the pair of first carriers 43 along the rotation direction 25 are connected to both ends of the carrier 1141 . Each first carrier 43 is formed in an arc shape, and a pivot portion 44 that abuts against the inner surface of the casing 2 is provided in the middle of its outer surface.

Further, an arcuate rolling surface 45 is not provided on the outer surface of the rotor 44 on the front side of the pivot portion 44 along the [m rotation direction 25]. Furthermore, an engaging portion 46 cut out in a semicircular shape is provided on the inner surface of the rear end of the first carrier 43 to engage with the transmission shaft 37 .

A first torsion spring 47 is wound around the transmission shaft 37 in front of the first support shaft 41 along the rotation direction 25 of the input shaft 70, and one end of the first torsion spring 47 is connected to the transmission shaft 37.
137, the first support shaft 41 on the rear side along the rotational direction 25
The other end of the first torsion spring 47 is engaged with the IJ.
is engaged with the ring body 39.

Due to the spring force of the first torsion spring 47, the first ring body 39 is biased radially inward, and the first support shaft 41 is also biased radially inward of the casing 2. Moreover, the 1st branch 1
11141 is the rolling shaft 3 on the front side along the rotation direction 25
7 via a first screw spring 47.

Between the second bearing 34 and the second ring body 40, the first
Similarly to the case between the bearing 33 and the first ring body 39, the second
A support shaft 48, a second roller 49, a second carrier 50, and a second torsion spring 51 are respectively arranged.

Next, to explain the operation of this embodiment, the first and second eccentric rotating bodies 27, 28 are placed on one side of the input 111+7, for example, on the outer end side of the input shaft 7 as shown in FIG. The center of the outer peripheral surface of the first and second rotating bodies 27 and 28 is 0. ．． 02 is eccentric from the axis O1 of the input shaft 7 by an eccentric amount E, and a case is assumed in which a rotational driving force is applied to the input shaft 7 from a motor (not shown). The first and second eccentric rotating bodies 27 and 28 rotate eccentrically in response to the input shaft 70 rotation, and the first and second carriers 43 and 50 swing in response to the rotational movement of the transmission shaft 37 and The output shaft 14 is rotated via the variable speed wheel 18, and a high torque output can be obtained from the output shaft 14.

Here, since the operations of the parts related to the first eccentric rotating body 27 and the parts related to the second eccentric rotating body 28 are basically the same, only the operations of the parts related to the first eccentric rotating body 27 will be described below. I'll decide.

Regarding the movement of the first bearing 33 due to the rotational movement of the first eccentric rotating body 27, if we pay attention to the specific position on the outer circumferential surface of the first bearing 33, the specific position will change according to one eccentric rotation of the first eccentric rotating body 27. A forward motion in a direction away from the axis O2 of the input shaft 7 and a backward motion in a direction close to the axis Oi are performed. Further, focusing on a specific first roller 42, the fifth first roller 42 moves along the axis O according to the forward movement of the first bearing 33.
Move in the direction away from 2. By kneading, the front end of the first carrier 43 rotates in the rotation direction 25 in a direction approaching the inner surface of the casing 2 with the pivot portion 44 as a fulcrum, and the rolling surface 45 rolls along the inner surface of the casing 2. move.

In response, the engaging portion 46 of the first carrier 43 engages with the transmission shaft 37 and moves the transmission shaft 37 forward in the rotational direction 25. This movement of the transmission shaft 37 is transmitted to the output shaft 14 via the variable speed wheel 18, and the output shaft 14 rotates.

−18= When the first Illll receiver 33 returns, the first torsion spring 4
7, the first roller 43 is attracted forward along the rotational direction 25, and the first roller 42 is pulled forward by the 11th J song 3.
9, it is pulled back in a direction approaching the input shaft I.

Such an operation is performed for each first carrier 43, but since five first carriers 45 are provided, driving force is transmitted to the output shaft 14 every time the input shaft 7 is angularly displaced by 72 degrees. be done.

On the other hand, due to the eccentric rotation operation of the second eccentric rotating body 28,
A driving force is transmitted to the output shaft 14 every time the input shaft 7 is angularly displaced by 72 degrees. Moreover, the first and second eccentric rotating bodies 27
．． The eccentric rotation phases of 28 are shifted by 162 degrees (=180-18), thereby making it possible to minimize the pulsation of the output shaft 14. That is, if we now assume that the deviation in the eccentric direction of both eccentric rotating bodies 27 and 28 is 180 degrees,
Every time the input shaft 7 makes one rotation, that is, 360 degrees of angular displacement, the first eccentric rotor 27 and the second eccentric rotor 28 transfer five waves of rotational power to the output shaft 14, each with a phase shift of 180 degrees. are transmitted, and when they are combined, the output is obtained from the output shaft 14 by pulsating five times while the input shaft 7 is angularly displaced by 180 degrees. Therefore, in order to make this pulsating wave occur 10 times and virtually eliminate pulsation, it is necessary to
÷IO,=-18, and the first and second eccentric rotating bodies 2
The deviation in the eccentric direction of 7.28 may be 18 degrees. In this way, pulsation can be substantially eliminated and pulsation can be suppressed accordingly.

In order to change the gear ratio, the operation member 9 may be screwed forward or backward, and the first and second eccentric rotating bodies 27 and 28 will then move along the axial direction of the input shaft 1. Therefore, the eccentricity E can be changed steplessly from the state where the eccentricity is 9E=Q as shown in FIG. 4 to the state where the eccentricity E is the maximum value as shown in FIG. 1, and a large gear ratio can be achieved. I can do it.

Also, during the speed change operation, the rolling surface 45 of each carrier 43,50 rolls along the inner surface of the casing 2 (so,
Unlike the conventionally known friction conduction method, it causes less wear, increases durability, and suppresses noise generation.

C9 Effects of the Invention As described in -1-, in the continuously variable transmission according to the present invention, the first and second carriers are shifted out of phase by the eccentric rotation of the first and second eccentric rotors in accordance with the rotation of the input shaft. Since the output shaft is oscillated and the output shaft is rotated by the oscillation via the transmission shaft, durability can be improved and pulsation can be reduced to prevent vibration and noise from occurring. Moreover, the first and second eccentric rotors are attached to the input shaft such that the amount of eccentricity changes according to the axial movement of the input shaft, and an operating member for moving both eccentric rotors is attached to the casing. Therefore, the gear ratio can be adjusted steplessly. Furthermore, since two sets of structures for transmitting power from the input shaft to the transmission shaft are arranged in parallel, the overall structure can be made more compact and the torque can be increased.

[Brief explanation of drawings]

The drawings show one embodiment of the present invention, and FIG. 1 is a longitudinal sectional side view, FIG. 2 is a sectional view taken along line I'l-'II in FIG. 1, and FIG. 3 is a sectional view taken along line III-- in FIG. 5. FIG. 4 is a longitudinal sectional side view corresponding to FIG. 1 when the amount of eccentricity of both eccentric rotating bodies is set to zero. DESCRIPTION OF SYMBOLS 1...Continuously variable transmission, 2...Casing 57...Input shaft, 9...Operation member, 11...Slider, 14...
・Output shaft, 18... Variable speed wheel, 25... Rotation direction,
27... First eccentric rotating body, 28... Second eccentric rotating body, 33... First bearing, 34... Second bearing, 37...
Transmission shaft, 39...first ring body, 40...second ring body, 41...first support shaft, 42...first roller, 43
...First carrier, 47...First torsion spring, 48.
...Second spindle, 49...Second roller, 50...Second
Carrier, 51...Second screw spring

Claims (2)

[Claims] (1) A basically cylindrical casing; an input shaft rotatably supported at one end of the casing; the outer peripheral surface is cylindrical, and is movable along the input shaft and can be moved in the axial direction. a pair of first and second eccentric rotating bodies that are mounted on the input shaft and rotate together with the input shaft such that the amount of eccentricity with respect to the input shaft changes along a direction that makes an angle with respect to the input shaft; an output shaft arranged concentrically with the input shaft; a variable speed wheel mounted on the output shaft to allow movement only in the axial direction; a plurality of transmission shafts arranged in the transmission wheel and having one end fixed to the speed change wheel; a pair of first and second bearings fitted on the outer periphery of both the eccentric rotating bodies; a pair of first and second bearings surrounding both the bearings; a second ring body; a plurality of first and second support shafts arranged parallel to the input shaft at equal intervals in the circumferential direction between the two bearings and both ring bodies; a plurality of first and second rollers that abut on both the ring bodies and both bearings; a plurality of first and second rollers that abut on the inner surface of the casing and are swingable around an axis parallel to the input shaft, and along the rotational direction of the input shaft; A front end is connected to both of the support shafts, and a rear end along the rotational direction engages with the transmission shaft when the front end swings in a direction approaching the inner surface of the casing to move the transmission shaft forward in the rotational direction. a plurality of first and second carriers provided with engaging portions for holding the transmission shaft; provided between the transmission shaft and each of the support shafts on the rear side in the rotational direction of the transmission shaft; a plurality of first and second springs biasing one side; and an operating member attached to the casing for moving both eccentric rotors along the input shaft via the speed change wheel; Features a continuously variable transmission. (2) Five of the support shafts, carriers, rollers, and springs are arranged for both eccentric rotating bodies, and five transmission shafts are arranged in common for both eccentric rotating bodies. The continuously variable transmission according to claim 1, wherein the rotating body is mounted on the input shaft so that the amount of eccentricity changes in a direction shifted by 162 degrees.