WO2017073993A1

WO2017073993A1 - Continuously variable transmission

Info

Publication number: WO2017073993A1
Application number: PCT/KR2016/012040
Authority: WO
Inventors: 현경열
Original assignee: 현경열
Priority date: 2015-10-27
Filing date: 2016-10-26
Publication date: 2017-05-04

Abstract

Disclosed is a continuously variable transmission. The continuously variable transmission according to the present invention comprises a driving gear and a driven gear which are conical gears, and thus the transmission can be formed into a compact structure and the power transfer efficiency can also be improved.

Description

Continuously variable transmission

The present invention relates to a continuously variable transmission, and more particularly, to a continuously variable transmission in which an adjustment structure of a transmission range is improved.

Transmissions used in automobiles are classified into manual transmissions and automatic transmissions according to the transmission method, and automatic transmissions are classified into a stepped automatic transmission and a continuously variable transmission (CVT).

In addition to the function of converting the rotational force of the engine and transmitting it to the driving wheel, the transmission enables idling of the engine when the vehicle is stopped and enables the reverse by changing the rotational direction of the driving wheel.

In a conventional manual transmission or a stepped automatic transmission, the transmission ratio according to the rotational speed of the engine is extremely limited, and thus a shift stage is present because a shift stage is made between certain transmission ranges. However, in the continuously variable transmission, all transmission ratios within a given range can be selected continuously. Therefore, in a vehicle equipped with the continuously variable transmission, the transmission ratio for driving conditions is implemented so that the engine is operated at the required rotational driving point. It becomes possible.

In addition, since transmission of power is not interrupted even during shifting, there is almost no shift shock.

As a continuously variable transmission for automobiles, a method of continuously changing speed is adopted by changing the effective diameter of a pulley using a rubber belt. In the belt driving method, the speed ratio is changed steplessly by changing the width of both pulleys, and the width of each pulley is adjusted mainly by hydraulic pressure. When the effective diameter of the drive pulley is small, the effective diameter of the driven pulley is increased to obtain a low speed shift stage. On the contrary, when the effective diameter of the drive pulley is large, the effective diameter of the driven pulley decreases, the high speed shift stage can be obtained. have.

The prior art of such a conventional continuously variable transmission is disclosed in Korean Patent No. 10-0313808.

As disclosed, the conventional continuously variable transmission is variable in diameter while the variable side pulley of the primary pulley is moved left and right by hydraulic pressure, and thus the secondary pulley is different from the primary pulley while supporting the variable side pulley by the elastic force of the spring. Relative variable operation is made. Then, power is transmitted while shifting by a belt connected to the variable-controlled primary pulley and the secondary pulley.

However, the conventional continuously variable transmission controls the transmission ratio while the diameter of the pulley is variable in accordance with the supply of hydraulic pressure, so a separate hydraulic device is required, and the transmission is enlarged in size, and the power is transmitted by the belt. There is a problem that slip occurs between the power transmission efficiency is lowered.

The present invention has been made in view of the above, and according to the present invention, it is an object of the present invention to provide a continuously variable transmission in which the size of the transmission is made compact and the power transmission efficiency can be improved.

According to one embodiment of the invention, the drive shaft; A drive gear provided to be movable on the drive shaft and formed of a conical gear in which a plurality of first key grooves are formed in a radial direction along an inclined surface; A plurality of first keys parallel to the drive shaft and partially protruding from the inclined surface of the drive gear, and movably coupled to the plurality of first key grooves, respectively; Driven shaft; A driven gear provided to be movable on the driven shaft, the driven gear comprising a conical gear having a plurality of second key grooves in a radial direction along an inclined surface; A plurality of second keys parallel to the driven shaft and partially protruding from the inclined surface of the driven gear, and movably coupled to the plurality of second key grooves, respectively; A power transmission member interconnecting the drive gear and the driven gear through the plurality of first keys and the plurality of second keys, and transmitting a rotational force of the drive gear to the driven gear; And a speed change control unit configured to adjust the rotation radius of the plurality of first keys coupled to the drive gear and the rotation radius of the plurality of second keys coupled to the driven gear to increase and decrease in opposite directions. Can be provided.

According to another embodiment of the invention, the drive shaft; A drive gear provided to the drive shaft so as to be mutually accessible or spaced apart, a plurality of first key grooves formed in a radial direction along an inclined surface, the pair of conical gears being disposed to face each other; A plurality of first keys movably coupled to each first key groove of the drive gear to interconnect the pair of conical gears; Driven shaft; A driven gear provided to be mutually accessible or spaced apart from the driven shaft, the second key groove being formed in a radial direction along an inclined surface, and having a pair of conical gears arranged such that the inclined surfaces face each other; A plurality of second keys movably coupled to respective second key grooves of the driven gear and interconnecting the pair of conical gears; A power transmission member interconnecting the drive gear and the driven gear through the plurality of first keys and the plurality of second keys, and transmitting a rotational force of the drive gear to the driven gear; A continuously variable transmission may include a shift control unit configured to increase or decrease an interval between the drive gear and an interval between the driven gear.

According to the present invention, by improving the adjustment structure of the speed change range, the size of the transmission can be made compact, and the power transmission efficiency can be improved.

1 is a perspective view of a continuously variable transmission according to an embodiment of the present invention.

FIG. 2 is a perspective view of a holder and a screw shaft removed in FIG. 1; FIG.

3 is a perspective view of a state in which the power transmission member is removed in FIG.

4 is a perspective view of a state in which each guide is removed from FIG.

Figure 5 is a perspective view of one power transmission member assembled in Figure 4;

FIG. 6 is a perspective view of a main first key and a main second key in FIG. 4; FIG.

FIG. 7 is a perspective view of an auxiliary first key and an auxiliary second key in FIG. 4; FIG.

8 is a perspective view of each guide in FIG.

9 is a perspective view of the holder in FIG. 1;

10 is a perspective view of a continuously variable transmission according to another embodiment of the present invention.

11 is a perspective view of a state in which the drive motor is removed in FIG.

FIG. 12 is a perspective view of a state in which some gears are removed from FIG. 11; FIG.

13 is a perspective view of a state in which the screw shaft drive unit is removed in FIG.

14 is a perspective view of a state in which each guide plate is removed in FIG. 13.

15 is a perspective view of a state in which the power transmission member is removed in FIG.

FIG. 16 is a perspective view illustrating a coupling state of a driving shaft and a driving gear or a driven shaft and a driven gear in FIG. 15; FIG.

FIG. 17 is an explanatory diagram for explaining a speed increase process in FIG. 14; FIG.

Figure 18 is a perspective view of the main portion of the power transmission member commonly applied to various embodiments of the present invention.

19 is an exploded state diagram for explaining a coupling relationship between each key formed on a driving gear side and a power transmission member in various embodiments of the present disclosure.

20 is a view illustrating a coupling state of a ratchet and a main first key and a ratchet and a main second key commonly applied to various embodiments of the present disclosure.

Hereinafter, with reference to the accompanying drawings will be described in detail an embodiment of the present invention.

1 to 9 illustrate a continuously variable transmission according to an embodiment of the present invention.

As shown in these drawings, the continuously variable transmission 1 according to the embodiment of the present invention includes a drive shaft 11, a drive gear 21 having a conical structure, a plurality of first keys 31, and a driven shaft 51. , A driven gear 61 having a conical structure, a plurality of second keys 71, a power transmission member 91, and a shift control unit 101.

The drive shaft 11 receives power for driving. The input power is output through the driven shaft 51 after being added or subtracted by the structure to be described later. Acceleration may include both speed and torque. A spline key 13 is formed in the drive shaft 11 so that the drive gear 21 is splined.

As shown in FIG. 4, the drive gear 21 is formed with a boss 23 through which the drive shaft 11 is penetrated. Spline grooves 23a which are splined to the spline key 13 of the drive shaft 11 are formed in the inner circumference of the boss 23. In addition, an inclined surface 25 that forms an inclination along the circumference of the boss 23 is formed at one side of the drive gear 21. The inclined surface 25 of the drive gear 21 is formed with a plurality of first key grooves 27 recessed in the radial direction along the inclined surface 25.

A plurality of first fitting protrusions 29 are formed to protrude from the plurality of first key grooves 27, and each of the first fitting protrusions 29 has an inclination angle of the inclined surface 25 of the drive gear 21. Has The plurality of first key grooves 27 are recessed from the inclined surface 25 of the drive gear 21 to the outer circumference of the boss 23.

The plurality of first keys 31 have a block shape having a predetermined length and are movable in the plurality of first key grooves 27 to be parallel to the driving shaft 11 and to partially protrude from the inclined surface 25 of the drive gear 21. To be combined.

As illustrated in FIG. 6, the plurality of first keys 31 are guide grooves for guiding sliding of the wedge groove 37 and the ratchet 97 to which the ratchet 97 of the power transmission member 91 to be described later engages. A plurality of main first keys 33 formed at intervals 39 and a pair of guide grooves 39 for guiding sliding of the ratchet 97 as shown in FIG. 7 are formed at intervals. Auxiliary first key 35 is included. At this time, in the wedge groove 37 and the guide groove 39 of the first key 31, the wedge groove 37 has a trapezoidal cross-sectional shape in close contact with the ratchet 97, as shown in FIG. The groove 39 has a rectangular cross-sectional shape having a clearance with the ratchet 97.

In addition, first fitting grooves 41 fitted to first fitting protrusions 29 of the first key grooves 27 on both side surfaces of the plurality of main first keys 33 and the plurality of auxiliary first keys 35. Each of these recesses is formed. In addition, the bottom surface of the wedge groove 37 and the guide groove 39 of the first key 31 interferes with the inclined surface 25 of the drive gear 21 by the ratchet 97 of the power transmission member 91. In order to prevent this from happening, it is spaced apart from the inclined surface 25 of the drive gear 21.

Here, in the present exemplary embodiment, the first fitting protrusion 29 protrudes from the first key groove 27, and the first fitting protrusion is formed on the plurality of main first keys 33 and the plurality of auxiliary first keys 35. Although the first fitting grooves 41 to be fitted into the 29 are shown as being recessed, but not limited thereto, the first keying grooves 27 are recessed and formed in the first key grooves 27. The first fitting protrusion 29 may be formed to protrude from the main first key 33 and the plurality of auxiliary first keys 35 to be fitted to the first fitting groove 41.

Accordingly, in the continuously variable transmission 1 according to the exemplary embodiment of the present invention, a plurality of main first keys 33 and a plurality of auxiliary first keys 35 may include a plurality of first key grooves 27 of the drive gear 21. Are alternately mounted along the circumference of the drive shaft 11. In addition, as shown in FIG. 19, each of the wedge grooves 37 of the pair of main first keys 33 disposed with the auxiliary first key 35 therebetween moves in the direction of movement of the power transmission member 91. Are alternately arranged alternately with respect to.

As described above, as the plurality of first keys 31 coupled to the plurality of first key grooves 27 of the drive gear 21 are spaced apart from the vertex area of the drive gear 21, the plurality of first keys 31 The radius of rotation becomes large. On the contrary, as the plurality of first keys 31 coupled to the plurality of first key grooves 27 of the drive gear 21 approach the vertex region of the drive gear 21, the rotation of the plurality of first keys 31 is performed. The radius becomes smaller. In addition, as the main first key 33 and the auxiliary first key 35 are alternately mounted on the drive gear 21, a plurality of agents coupled to each of the first key grooves 27 of the drive gear 21 are provided. When the rotation radius of the first key 31 is changed, the ratchet 97 of the power transmission member 91 is stably engaged without departing from the wedge groove 37 of the first key 31.

The driven shaft 51 is spaced apart in parallel with the drive shaft 11, and outputs the power input from the drive shaft 11. The spline key 53 is formed in the driven shaft 51 so that the driven gear 61 may spline-couple.

The driven gear 61 has the same shape and size as the drive gear 21, and as shown in FIG. 4, the driven shaft 51 so that the vertex area is disposed in a direction opposite to the vertex area of the drive gear 21. Is coupled to move. The driven gear 61 is formed with a boss 63 through which the driven shaft 51 is coupled in the center. On the inner circumference of the boss 63 is formed a spline groove 63a which is splined to the spline key 53 of the driven shaft 51. In addition, one side of the driven gear 61 is formed with an inclined surface 65 inclined along the circumference of the boss (63). On the inclined surface 65 of the driven gear 61, a plurality of second key grooves 67 are recessed in the radial direction along the inclined surface 65.

A plurality of second fitting protrusions 69 protruding from each other are formed in the plurality of second key grooves 67, and each second fitting protrusion 69 has an inclination angle of the inclined surface 65 of the driven gear 61. Has The plurality of second key grooves 67 are recessed from the inclined surface 65 of the driven gear 61 to the outer circumference of the boss 63.

The plurality of second keys 71 have a block shape of a predetermined length, and move in the plurality of second key grooves 67 to be parallel to the driven shaft 51 and to partially protrude from the inclined surface 65 of the driven gear 61. Possibly combined.

As shown in FIG. 6, the plurality of second keys 71 are guide grooves 79 for guiding sliding of the ratchet 97 and the wedge groove 77 to which the ratchet 97 of the power transmission member 91 is engaged. ) A plurality of auxiliary second keys 73 formed at intervals, and a plurality of auxiliary grooves formed at intervals to guide the sliding of the ratchet 97 as shown in FIG. 7. Two keys (75). The wedge groove 77 and the guide groove 79 of the second key 71 are the same as the wedge groove 37 and the guide groove 39 of the first key. It has a trapezoidal cross-sectional shape in close contact, and the guide groove 79 has a rectangular cross-sectional shape having a clearance with the ratchet 97.

In addition, second fitting grooves 81 fitted to the second fitting protrusions 69 of the second key grooves 67 on both side surfaces of the plurality of main second keys 73 and the plurality of auxiliary second keys 75. Each of these recesses is formed. In addition, the bottom surface of the wedge groove 77 and the guide groove 79 of the second key 71 has the ratchet 97 of the power transmission member 91 interfering with the inclined surface 65 of the driven gear 61. In order not to generate | occur | produce this, the space | interval is formed higher than the inclined surface 65 of the driven gear 61. FIG.

Here, in one embodiment of the present invention, the second fitting protrusion 69 is formed to protrude in the second key groove 67, and the second to the plurality of main second keys 73 and the plurality of auxiliary second keys 75 are second. Although the second fitting grooves 81 fitted to the fitting protrusions 69 are shown as being recessed, respectively, but are not limited thereto, the second fitting grooves 81 may be recessed in the second key groove 67. The second fitting protrusions 69 fitted into the second fitting grooves 81 may be formed in the plurality of main second keys 73 and the auxiliary second keys 75, respectively. In addition, the main second key 73 has the same shape and size as the main first key 33, and the auxiliary second key 75 preferably has the same shape and size as the auxiliary first key 35. .

Accordingly, in the continuously variable transmission 1 according to the exemplary embodiment of the present invention, a plurality of main second keys 73 and a plurality of auxiliary second keys 75 may include a plurality of second key grooves 67 of the driven gear 61. Are alternately mounted along the circumference of the driven shaft 51. Further, in the same structure as that of the drive gear 21 side (Fig. 19), each of the wedge grooves 77 of the pair of main second keys 73 disposed with the auxiliary second key 75 therebetween is power transmission. The members 91 are alternately arranged alternately with respect to the moving direction of the member 91.

As described above, as the plurality of second keys 71 coupled to the plurality of second key grooves 67 of the driven gear 61 are spaced apart from the vertex region of the driven gear 61, the plurality of second keys 71 The radius of rotation becomes large. On the contrary, as the plurality of second keys 71 coupled to the plurality of second key grooves 67 of the driven gear 61 approach the vertex region of the driven gear 61, the rotation of the plurality of second keys 71 is performed. The radius becomes smaller. In addition, by alternately mounting the main second key 73 and the auxiliary second key 75 to the driven gear 61, a plurality of agents coupled to each second key groove 67 of the driven gear 61. When the rotation radius of the two keys 71 is changed, the ratchet 97 of the power transmission member 91 is stably engaged without departing from the wedge groove 77 of the second key 71.

On the other hand, the power transmission member 91, as shown in Figure 18, a plurality of connecting links 93 having a predetermined length is connected by a pin 95 to form a closed loop shape, at the same time, a plurality of connections The link 93 has the shape of a chain conveyor arranged at intervals transversely with respect to the moving direction of the power transmission member 91.

A plurality of ratchets 97 are coupled to the power transmission member 91 as attachments, and the plurality of ratchets 97 are arranged at regular intervals along the moving direction of the power transmission member 91. The ratchet 97 is engaged with the

wedge grooves

37 and 77 formed in the plurality of first keys 31 and the plurality of second keys 71 or slides into the

guide grooves

39 and 79.

On the other hand, when the ratchet 97 is engaged with the

wedge grooves

37 and 77, power is transmitted by the ratchet 97 and the

wedge grooves

37 and 77, and the ratchet 97 is inserted into the

guide grooves

39 and 79. When the ratchet 97 is not engaged in the

guide grooves

39 and 79, the ratchet 97 slides, so that power is not transmitted. As a result, the power transmission member 91 interconnects the drive gear 21 and the driven gear 61 through the plurality of first keys 31 and the plurality of second keys 71, The rotational force is transmitted to the driven gear 61.

In addition, in one embodiment of the present invention, as shown in Figure 2 a pair of power transmission members (91a, 91b) are arranged in parallel so as to be able to rotate independently of each other. Thus, when the radius of rotation of the plurality of first keys 31 and the plurality of second keys 71 is changed, each ratchet 97 of the pair of

power transmission members

91a and 91b is connected to the first key 31. The wedge groove 37 and the second key 71 of the wedge groove 77 of each of them without departing from the stable engagement, it is possible to continuously transmit power.

More specifically, each of the wedge grooves 37 of the pair of main first keys 33 disposed with the auxiliary first key 35 therebetween is connected to the pair of

power transmission members

91a and 91b. Each pair of wedge grooves 77 of a pair of main second keys 73 arranged alternately laterally alternately with respect to the movement direction and arranged with the auxiliary second key 75 interposed therebetween is a pair of power transmission. A pair of power transmission members is disposed when the rotation radius of the plurality of first keys 31 and the plurality of second keys 71 is changed by alternately shifting horizontally with respect to the moving directions of the

members

91a and 91b. Since 91a and 91b rotate independently of each other, each ratchet 97 of one side power transmission member 91a has a wedge groove of first key 31 disposed along the moving direction of one side power transmission member 91a. 37) and stably engages without deviating from the wedge grooves 77 of the second key 71, respectively, and can continuously transmit power, and the other power transmission unit Each ratchet 97 of the ash 91b has a wedge groove 37 of the first key 31 and a wedge groove 77 of the second key 71 arranged along the direction of movement of the other power transmission member 91b. It is possible to reliably engage and transmit power continuously without deviating from each other.

In the shift control unit 101, the rotation radius of the plurality of first keys 31 coupled to the drive gear 21 and the rotation radius of the plurality of second keys 71 coupled to the driven gear 61 are increased or decreased in opposite directions. Adjust to That is, in the shift control unit 101, as the vertex regions of the drive gear 21 and the driven gear 61 are arranged in opposite directions, the plurality of first keys 31 and the plurality of second keys 71 are arranged. Is simultaneously moved to the vertex area of the drive gear 21, the rotation radius of the first key 31 decreases and the rotation radius of the second key 71 increases, and conversely, the plurality of first keys 31 and the plurality of By simultaneously moving the second key 71 to the vertex area of the driven gear 61, the rotation radius of the first key 31 increases and the rotation radius of the second key 71 decreases. Therefore, the rotation speeds of the plurality of first keys 31 and the plurality of second keys 71 are changed to adjust the speed change.

The shift control unit 101 includes a pair of first guides 103, a pair of second guides 107, a pair of holders 111, a screw shaft 121, and a screw shaft driver 125. ).

The pair of first guides 103 are reciprocally coupled to the drive gear 21 with a plurality of first keys 31 coupled to the plurality of first key grooves 27 interposed therebetween. Each first guide 103 is provided with a first pusher 105 which is inserted into a plurality of first key grooves 27 and presses both ends of the first key 31 as shown in FIG. 8.

The pair of second guides 107 are reciprocally coupled to the driven gear 61 with a plurality of second keys 71 coupled to the plurality of second key grooves 67 interposed therebetween. Each second guide 107 is provided with a second pusher 109 inserted into the plurality of second key grooves 67 and pressing both ends of the second key 71 as shown in FIG. 8.

The pair of holders 111 are interconnected at intervals by brackets 117 as shown in FIG. 9, and the pair of first guides 103 and the pair of second guides 107 are thrust bearings. And rotatably supported by 113. A screw portion 115 is provided in the center of each holder 111, and the screw portion 115 has a screw penetratingly formed in parallel with the drive shaft 11. The pair of holders 111 are supported by a structure such as a frame by a support 119 coupled to the bracket 117.

The screw shaft 121 has a rod shape having a predetermined length having a screw formed on an outer circumference thereof, and is screwed to the threaded portion 115 of the holder 111 to linearly move the holder 111. When the screw shaft 121 is rotated in the forward direction, the holder 111 moves in the direction of the vertex region of the drive gear 21, and the

pushers

105 and 109 of the first guide 103 and the second guide 107 are moved. One end of the first key 31 and the second key 71 is pressed by the first key 31 and moves in the direction of the vertex area of the drive gear 21, so that the rotation radius of the first key 31 decreases and the second key 71 The rotation radius is increased, so that the continuously variable transmission 1 according to the embodiment of the present invention is decelerated.

On the contrary, when the screw shaft 121 is rotated in the reverse direction, the holder 111 moves in the direction of the vertex region of the driven gear 61 and at the same time, each pusher of the first guide 103 and the second guide 107 ( One end of the first key 31 and the second key 71 is pressed by 105 and 109 and moves in the direction of the vertex region of the driven gear 61 so that the first radius 31 has an increased radius of rotation and a second key. Reference numeral 71 is a rotation radius is reduced, the continuously variable transmission 1 according to an embodiment of the present invention is to increase the speed.

The screw shaft driver 125 is connected to the screw shaft 121 to rotate the screw shaft 121 forward and backward. In this embodiment, although the motor directly connected to the screw shaft 121 is shown as the screw shaft driver 125, the present invention is not limited thereto. The screw shaft driver is coupled to the motor, the screw shaft 121, and the motor shaft, respectively. It can be made of a sprocket of the chain, connecting a pair of sprockets and transmitting power.

By such a configuration, a description will be given of the various shifting process of the continuously variable transmission 1 according to an embodiment of the present invention.

A. 변속이 없는 경우 A. No shift

The first key 31 coupled to the first key groove 27 of the drive gear 21 is positioned at the center of the drive gear 21 and the second key coupled to the second key groove 67 of the driven gear 61. When the key 71 is positioned at the center of the driven gear 61, the rotation radius of the first key 31 coupled to the first key groove 27 of the drive gear 21 and the second key groove of the driven gear 61 are shown. The rotation radius of the second key 71 coupled to the 67 is the same, so that a shift does not occur between the drive gear 21 and the driven gear 61.

Accordingly, the power input through the drive shaft 11 is driven by the drive gear 21, the plurality of first keys 31, the power transmission member 91, the plurality of second keys 71, and the driven gear ( 61 is sequentially passed through the driven shaft (51). At this time, a shift does not occur between the drive gear 21 and the driven gear 61, and the drive shaft 11 and the driven shaft 51 rotate at the same rotational speed.

B. B. 증속되도록To increase 변속하는 경우 When shifting

In the state where the rotation radius of the first key 31 of the drive gear 21 and the rotation radius of the second key 71 of the driven gear 61 are the same, the holder 111 is in the vertex region direction of the driven gear 61. Rotate the screw shaft 121 in the reverse direction to move to.

As the screw shaft 121 rotates in the reverse direction, the other ends of the first key 31 and the second key 71 are formed by the

pushers

105 and 109 of the first guide 103 and the second guide 107. Pressurized and moved together in the direction of the vertex region of the driven gear 61, the first key 31 coupled to the first key groove 27 of the driven gear 61 is increased in the radius of rotation, and of the driven gear 61 The radius of rotation of the second key 71 coupled to the second key groove 67 is reduced.

As described above, the rotation radius of the plurality of first keys 31 coupled to the drive gear 21 is adjusted by the shift adjustment unit 101 to the plurality of second keys 71 coupled to the driven gear 61. As the relative radius is larger than the rotation radius, the speed increase occurs by a ratio of the rotation radius of the plurality of first keys 31 and the rotation radius of the plurality of second keys 71.

Accordingly, the power input through the drive shaft 11 is driven by the drive gear 21, the plurality of first keys 31, the power transmission member 91, the plurality of second keys 71, and a pair of pairs. The driven gear 61 is sequentially transmitted through the driven shaft 51. At this time, between the drive gear 21 and the driven gear 61, an increase in speed is generated by a ratio of the rotation radius of the plurality of first keys 31 and the rotation radius of the plurality of second keys 71. 51 rotates with the rotation speed which speeded up with respect to the drive shaft 11. As shown in FIG.

C. 감속되도록 변속하는 경우C. When shifting to decelerate

In the state where the rotation radius of the first key 31 of the drive gear 21 and the rotation radius of the second key 71 of the driven gear 61 are the same, the holder 111 is in the vertex region direction of the drive gear 21. Rotate the screw shaft 121 in the forward direction to move to.

As the screw shaft 121 rotates in the forward direction, one end of the first key 31 and the second key 71 is pressed by the

pushers

105 and 109 of the first guide 103 and the second guide 107. The first key 31 coupled to the first key groove 27 of the drive gear 21 is reduced in rotation radius, and the first gear 31 of the driven gear 61 is moved together. The rotation radius of the second key 71 coupled to the two key grooves 67 increases.

As described above, the rotation radius of the plurality of first keys 31 coupled to the drive gear 21 is adjusted by the shift adjustment unit 101 to the plurality of second keys 71 coupled to the driven gear 61. As the relative radius becomes smaller than the rotation radius, deceleration occurs by the ratio of the rotation radius of the plurality of first keys 31 and the rotation radius of the plurality of second keys 71.

Accordingly, the power input through the drive shaft 11 is driven by the drive gear 21, the plurality of first keys 31, the power transmission member 91, the plurality of second keys 71, and a pair of pairs. The driven gear 61 is sequentially transmitted through the driven shaft 51. At this time, between the drive gear 21 and the driven gear 61, deceleration is generated by the ratio of the rotation radius of the plurality of first keys 31 and the rotation radius of the plurality of second keys 71, and the driven shaft 51 rotates with the rotation speed decelerated with respect to the drive shaft 11. As shown in FIG.

Hereinafter, with reference to the accompanying drawings will be described in detail another embodiment of the present invention.

10 to 16 show a continuously variable transmission 2 according to another embodiment of the invention.

As shown in these drawings, the continuously variable transmission 2 according to another embodiment of the present invention includes a drive shaft 211, a drive gear 220 formed of a pair of conical gears 221, and a plurality of first keys ( 231, a driven shaft 241, a driven gear 250 formed of a pair of conical gears 251, a plurality of second keys 261, a power transmission member 271, and a shift control unit 281. do.

The drive shaft 211 receives power for driving. The input power is output through the driven shaft 241 after being added or subtracted by a structure to be described later. Acceleration may include both speed and torque. The drive shaft 211 is formed with a spline key 213 so that the drive gear 221 is splined.

Conical gears 221 forming the drive gear 220 are formed in the same structure with each other, as shown in Figure 16, the spline groove 223 is splined to the spline key 213 of the drive shaft 211 in the center Is formed, the inclined surface 225 is formed on one side inclined along the circumference of the spline groove 223. The conical gears 221 are coupled to the drive shaft 211 so that each inclined surface 225 opposes each other and are spaced apart from each other. In addition, the inclined surface 225 of the conical gear 221 is formed with a plurality of first key grooves 227 recessed to a predetermined depth in the radial direction along the inclined surface 225.

The plurality of first keys 231 have a bar shape having a predetermined length and are provided between the pair of conical gears 221 to interconnect the pair of conical gears 221. In this case, the plurality of first keys 231 are movably engaged with the first key grooves 227 at positions corresponding to each other of the driving gear 220.

Accordingly, the plurality of first keys 231 move along the radial direction of the drive shaft 211, that is, along the radial direction of the drive gear 220.

Accordingly, when the distance between the drive gears 220 is narrowed, the plurality of first keys 231 move along the plurality of first key grooves 227 in a direction away from the drive shaft 211, and thus, the plurality of first keys. The radius of rotation of 231 becomes large. On the contrary, when the distance between the drive gears 220 increases, the plurality of first keys 231 move along the plurality of first key grooves 227 toward the driving shaft 211, and thus, the plurality of first keys 231 The radius of rotation becomes smaller.

In addition, the plurality of first keys 231 are spaced between the wedge groove 237 to which the ratchet 277 of the power transmission member 271 to be described later engages, and the guide groove 239 for guiding the sliding of the ratchet 277. The plurality of main first keys 233 and the pair of guide grooves 239 for guiding the sliding of the ratchet 277 include a plurality of auxiliary first keys 235 formed at intervals. At this time, the wedge groove 237 of the first key 231 has a trapezoidal cross-sectional shape in close contact with the ratchet 277, and the guide groove 239 of the first key 231 has a square having a clearance with the ratchet 277. In the cross-sectional shape of, as shown in FIG. 10, the same shape as that of one embodiment of the present invention may be taken.

Accordingly, in the continuously variable transmission 2 according to another embodiment of the present invention, a plurality of main first keys 233 and a plurality of auxiliary first keys 235 may include a plurality of first key grooves 227 of the drive gear 220. Are alternately mounted along the circumference of the drive shaft 211. In addition, as illustrated in FIG. 19, each of the wedge grooves 237 of the pair of main first keys 233 disposed with the auxiliary first key 235 therebetween moves in the direction of movement of the power transmission member 271. Are alternately arranged alternately with respect to.

As described above, as the main first key 233 and the auxiliary first key 235 are alternately mounted on the drive gear 220, the radius of rotation of the plurality of first keys 231 formed on the drive gear 220 is changed. When changed, the ratchet 277 of the power transmission member 271 is stably engaged without departing from the wedge groove 237 of the first key 231.

The driven shaft 241 is spaced apart in parallel with the drive shaft 211 and outputs power input from the drive shaft 211. A spline key 243 is formed on the driven shaft 241 so that the pair of conical gears 251 forming the driven gear 250 are splined together.

The pair of conical gears 251 forming the driven gear 250 are formed in the same structure, and as shown in FIG. 16, a spline splined to the spline key 243 of the driven shaft 241 at the center thereof. The groove 253 is formed. In addition, the inclined surface 255 is formed on one side inclined along the circumference of the spline groove 253. The pair of conical gears 251 are coupled to the driven shaft 241 so that each of the inclined surfaces 255 face each other, so as to approach or be spaced apart from each other. In addition, the inclined surface 255 of each conical gear 251 is formed with a plurality of second key grooves 257 recessed in a radial direction along the inclined surface 255 to a predetermined depth. The driven gear 250 has the same shape and size as the drive gear 220.

The plurality of second keys 261 have a bar shape having a predetermined length, and are connected to a pair of conical gears 251 provided on the driven gear 250 to form the driven gear 250. The plurality of second keys 261 are movably engaged with the second key grooves 257 at positions corresponding to the driven gears 250. Here, the second key 261 preferably has the same shape and size as the first key 231. Thus, the plurality of second keys 261 are moved along the radial direction of the driven shaft 241, that is, along the radial direction of the driven gear 250.

Accordingly, when the distance between the driven gears 250 becomes small, the plurality of second keys 261 connecting between the pair of conical gears 251 are driven along the plurality of second key grooves 257. The rotational radius of the plurality of second keys 261 is increased by moving in the direction away from the second key 261. On the contrary, when the distance between the driven gears 250 increases, the plurality of second keys 261 move along the plurality of second key grooves 257 toward the driven shaft 241, and thus the plurality of second keys 261. ) The radius of rotation becomes smaller.

In addition, the plurality of second keys 261 are formed at intervals between the wedge groove 267 to which the ratchet 277 of the power transmission member 271 engages and the guide groove 269 for guiding the sliding of the ratchet 277. The plurality of main second keys 263 and the pair of guide grooves 269 for guiding the sliding of the ratchet 277 include a plurality of auxiliary second keys 265 spaced apart from each other. At this time, the wedge groove 267 of the second key 261 has a trapezoidal cross-sectional shape in close contact with the ratchet 277, and the guide groove 269 of the second key 261 has a square having a clearance with the ratchet 277. In cross-sectional shape. As shown in FIG. 10, the shape may be the same as that of the exemplary embodiment of the present invention.

Accordingly, in the continuously variable transmission 2 according to another embodiment of the present invention, a plurality of main second keys 263 and a plurality of auxiliary second keys 265 may include a plurality of second key grooves 257 of the driven gear 250. Are alternately mounted along the circumference of the driven shaft 241. Further, the wedge grooves 267 of the pair of main second keys 263 disposed with the auxiliary second key 265 interposed therebetween in the same structure as the drive gear 221 side (Fig. 19) are the power transmission member. It is alternately shifted laterally with respect to the moving direction of 271.

As such, as the main second key 263 and the auxiliary second key 265 are alternately mounted on the driven gear 250, the rotation of the plurality of second keys 261 mounted on the driven gear 250 is performed. When the radius is changed, the ratchet 277 of the power transmission member 271 is stably engaged without departing from the wedge groove 267 of the second key 261.

The power transmission member 271 is formed in the same structure as the power transmission member 91 applied in one embodiment of the present invention, and as shown in FIG. 18, the plurality of connection links 273 having a predetermined length include a pin 275. At the same time to form a closed loop, a plurality of connecting links (273) has a shape of a chain conveyor arranged at intervals horizontally with respect to the moving direction of the power transmission member (271).

A plurality of ratchets 277 are coupled to the power transmission member 271 as attachments, and as illustrated in FIG. 9, the plurality of ratchets 277 are disposed at regular intervals along the moving direction of the power transmission member 271. At the same time, the power transmission member 271 is arranged horizontally with respect to the moving direction. The ratchet 277 is engaged with the wedge grooves 237 and 267 formed in the plurality of first keys 231 and the plurality of second keys 261 or slidable to the guide grooves 239 and 269.

On the other hand, when the ratchet 277 is engaged with the wedge grooves 237 and 267, power is transmitted by the ratchet 277 and the wedge grooves 237 and 267, and the ratchet 277 is inserted when the ratchet 277 is inserted into the guide grooves 239 and 269. In the guide grooves 239 and 269, the sliding does not engage and the power is not transmitted. As a result, the power transmission member 271 interconnects the drive gear 220 and the driven gear 250 through the plurality of first keys 231 and the plurality of second keys 261. The rotational force is transmitted to the driven gear 250.

The shift adjusting unit 281 adjusts the gap between the drive gear 220 and the gap between the driven gear 250 to increase and decrease in opposite directions. That is, in the shift control unit 281, the plurality of first keys 231 and the plurality of second keys 261 are opposite to each other along the plurality of first key grooves 227 and the plurality of second key grooves 257, respectively. Direction, for example, by changing each rotation radius of the plurality of first keys 231 and the plurality of second keys 261 to adjust the shift.

The shift control unit 281 includes a pair of drive screw shafts 283, a pair of driven screw shafts 285, a pair of first guide plates 287, and a pair of second guide plates 291. ) And a screw shaft drive unit 301.

The pair of driving screw shafts 283 are formed in parallel with the driving shaft 211 and provided with the driving gear 220 interposed therebetween. Both ends of the pair of drive screw shafts 283 are provided with screws in mutually different thread directions, and a pair of first guide plates 287 are screwed to these screws.

The pair of driven screw shafts 285 are in parallel with the driven shaft 241, and are provided with the driven gear 250 interposed therebetween. Both ends of the pair of driven screw shafts 285 are provided with screws in mutually different thread directions, and a pair of second guide plates 291 are screwed to these screws.

The pair of first guide plates 287 are provided with the drive gear 220 interposed therebetween, and the pair of drive screw shafts 283 are screwed together while the drive shaft 211 is penetrated and defective. As shown in FIG. 4, the first guide plate 287 is provided with a pair of screw holes 289 in which a pair of drive screw shafts 283 are screwed together.

The pair of second guide plates 291 are provided with the driven gear 250 interposed therebetween, while the driven shaft 241 penetrates through defects, and the pair of driven screw shafts 285 are each screwed together. The second guide plate 291 is formed with a pair of screw holes 293 in which a pair of driven screw shafts 285 are screwed together.

The screw shaft driver 301 adjusts the distance of the drive gear 220 by a pair of first guide plates 287, and is driven opposite to the drive gear 220 by a pair of second guide plates 291. The pair of drive screw shafts 283 and the pair of driven screw shafts 285 are rotated so that the distance between the gears 250 is adjusted.

The screw shaft drive unit 301 includes a drive motor 303, a drive motor gear 305, a first gear 307, a pair of drive sprockets 309, a drive chain 311, and a second gear. 315, a pair of driven sprockets 317, and a driven chain 319.

The drive motor gear 305 has a form of an outer tooth in which a plurality of gear teeth are formed, and is coupled to an axis of the drive motor 303 to rotate by the rotation of the drive motor 303.

The first gear 307 has the form of an external tooth having the same gear tooth size as that of the drive motor gear 305, and is coupled to any one of the pair of drive screw shafts 283, so as to be coupled to the drive motor gear 305. Rotate to interlock. The first gear 307 has a larger diameter than the drive motor gear 305. Thus, as the driving motor gear 305 and the first gear 307 mesh with each other and rotate, the rotation speed of the driving motor 303 is reduced by the ratio of the diameters of the driving motor gear 305 and the first gear 307.

The pair of drive sprockets 309 are respectively coupled to one end of the pair of drive screw shafts 283.

The drive chain 311 connects a pair of drive sprockets 309 and transmits power between the pair of drive sprockets 309.

The second gear 315 has the form of an external tooth having the same gear tooth size as the first gear 307, and is coupled to any one of the pair of driven screw shafts 285, so as to be coupled to the first gear 307. Rotate to interlock. The second gear 315 has the same diameter as the first gear 307. As a result, the second gear 315 and the first gear 307 rotate at the same rotational speed.

The pair of driven sprockets 317 are respectively coupled to one end of the pair of driven screw shafts 285.

The driven chain 319 connects a pair of driven sprockets 317 and transmits power between the pair of driven sprockets 317.

By such a configuration, a description will be given of the various shifting process of the continuously variable transmission 2 according to an embodiment of the present invention.

A. 변속이 없는 경우A. No shift

A plurality of first keys mounted on the drive gear 220 in a state where the distance between the drive gear 220 formed by a pair of

conical gears

221 and 251 and the distance between the driven gear 250 are the same. The rotation radius of the 231 and the rotation radius of the plurality of second keys 261 mounted on the driven gear 250 are the same, so that a shift does not occur between the drive gear 220 and the driven gear 250.

Accordingly, the power input through the drive shaft 211 is driven by the drive gear 220, the plurality of first keys 231, the power transmission member 271, the plurality of second keys 261, and the driven gear ( 250 is sequentially passed through the driven shaft 241. At this time, the shift does not occur between the drive gear 220 and the driven gear 250, the drive shaft 211 and the driven shaft 241 is rotated at the same rotational speed.

B. B. 증속되도록To increase 변속하는 경우 When shifting

In the state where the distance between the drive gear 220 and the driven gear 250 formed by the pair of

conical gears

221 and 251 are the same, as shown in FIG. 17, the distance between the drive gears 220 is reduced. The drive motor 303 is rotated in one direction.

The rotational force of the drive motor 303 is transmitted to the drive motor gear 305, a part of the rotational force of the drive motor 303 is transmitted to the first gear 307, the rest of the rotational force of the drive motor 303 is the first It is transmitted to the second gear 315 which rotates in engagement with the gear 307.

The rotational force of the drive motor 303 transmitted to the first gear 307 is transmitted to the pair of drive sprockets 309 and the drive chain 311 to rotate the pair of drive screw shafts 283 in the same direction. . At this time, the drive motor 303 and the first gear 307 is rotated in the opposite direction, and at the same time a pair of drive screw shaft 283 also rotates in the opposite direction to the drive motor 303. Thus, as the pair of drive screw shafts 283 rotate in the opposite direction to the drive motor 303, the pair of first guide plates 287 screwed with the pair of drive screw shafts 283 is one By the screw movement with the pair of drive screw shafts 283 are mutually approached, the distance between the drive gear 220 is reduced. Therefore, the plurality of first keys 231 mounted on the drive gear 220 are moved along the plurality of first key grooves 227 in a direction away from the drive shaft 211, thereby driving the drive gear 220. The rotation radius of the plurality of mounted first keys 231 is relatively larger than when the shift is not performed.

Meanwhile, the remaining rotational force of the drive motor 303 transmitted to the second gear 315 is transmitted to the pair of driven sprockets 317 and the driven chain 319 to move the pair of driven screw shafts 285 in the same direction. Rotate At this time, the driving motor 303 and the second gear 315 rotate in the same direction, and at the same time, the pair of driven screw shafts 285 also rotate in the same direction with the driving motor 303. Thus, as the pair of driven screw shafts 285 rotates in the same direction as the drive motor 303, the pair of second guide plates 291 screwed with the pair of driven screw shafts 285 become one. Unlike the first guide plate 287 of the pair, they are spaced apart from each other by a screw movement with the pair of driven screw shafts 285, thereby increasing the distance of the driven gear 250. Accordingly, the plurality of second keys 261 mounted on the driven gear 250 are moved toward the driven shaft 241 along the plurality of second key grooves 257, whereby the plurality of second keys 261 are mounted on the driven gear 250. The rotation radius of the plurality of second keys 261 becomes relatively smaller than when the shift is not performed.

As described above, the rotation radius of the plurality of first keys 231 mounted on the drive gear 220 is adjusted by the shift adjustment unit 281 of the plurality of second keys 261 mounted on the driven gear 250. As the relative radius is larger than the rotation radius, the speed increase occurs by a ratio of the rotation radius of the plurality of first keys 231 and the rotation radius of the plurality of second keys 261.

Accordingly, the power input through the drive shaft 211 is driven by the drive gear 220, the plurality of first keys 231, the power transmission member 271, the plurality of second keys 261, and the driven gear ( 250 is sequentially passed through the driven shaft 241. At this time, between the drive gear 220 and the driven gear 250, the speed is increased by the ratio of the rotation radius of the plurality of first keys 231 and the rotation radius of the plurality of second keys 261, the driven shaft 241 is rotated at an increased speed with respect to the drive shaft 211.

C. 감속되도록 변속하는 경우C. When shifting to decelerate

conical gears

221 and 251 are the same, the drive motor 303 is increased so that the distance between the drive gear 220 is increased. Rotate in the other direction.

The rotational force of the drive motor 303 transmitted to the first gear 307 is transmitted to the pair of drive sprockets 309 and the drive chain 311 to rotate the pair of drive screw shafts 283 in the same direction. . At this time, the drive motor 303 and the first gear 307 is rotated in the opposite direction, and at the same time a pair of drive screw shaft 283 also rotates in the opposite direction to the drive motor 303. Thus, as the pair of drive screw shafts 283 rotate in the opposite direction to the drive motor 303, the pair of first guide plates 287 screwed with the pair of drive screw shafts 283 is one They are spaced apart from each other by a screw movement with the pair of drive screw shafts 283, thereby increasing the distance of the drive gear 220. Therefore, the plurality of first keys 231 mounted on the drive gear 220 are moved toward the drive shaft 211 along the plurality of first key grooves 227, whereby the plurality of first keys 231 are mounted on the drive gear 220. Rotation radius of the first key 231 is relatively smaller than when the shift does not occur.

Meanwhile, the remaining rotational force of the drive motor 303 transmitted to the second gear 315 is transmitted to the pair of driven sprockets 2117 and the driven chain 319 to move the pair of driven screw shafts 285 in the same direction. Rotate At this time, the driving motor 303 and the second gear 315 rotate in the same direction, and at the same time, the pair of driven screw shafts 285 also rotate in the same direction with the driving motor 303. Thus, as the pair of driven screw shafts 285 rotates in the same direction as the drive motor 303, the pair of second guide plates 291 screwed with the pair of driven screw shafts 285 become one. Unlike the pair of first guide plates 287, the pair of driven screw shafts 285 approach each other by a screw movement, thereby reducing the distance between the driven gears 250. Accordingly, the plurality of second keys 261 mounted on the driven gear 250 move in a direction away from the driven shaft 241 along the plurality of second key grooves 257, thereby driving the driven gear 250. The radius of rotation of the plurality of second keys 261 mounted on the is relatively smaller than when the shift does not occur.

As described above, the rotation radius of the plurality of first keys 231 mounted on the drive gear 220 is adjusted by the shift adjustment unit 281 of the plurality of second keys 261 mounted on the driven gear 250. As the relative radius becomes smaller than the rotation radius, deceleration occurs by a ratio of the rotation radius of the plurality of first keys 231 and the rotation radius of the plurality of second keys 261.

Accordingly, the power input through the drive shaft 211 is driven by the drive gear 220, the plurality of first keys 231, the power transmission member 271, the plurality of second keys 261, and the driven gear ( 250 is sequentially passed through the driven shaft 241. At this time, between the drive gear 220 and the driven gear 250, the deceleration occurs by a ratio of the rotation radius of the plurality of first keys 231 and the rotation radius of the plurality of second keys 261, the driven shaft 241 is rotated at a reduced speed with respect to the drive shaft 211.

As described above, according to the present invention, the transmission structure is improved so that the speed change range can be adjusted by screwing motion without shifting by using hydraulic pressure, thereby making the transmission size compact compared to the prior art, thereby improving power transmission efficiency. It can be improved.

Claims

A drive shaft;

A drive gear provided to be movable on the drive shaft and formed of a conical gear in which a plurality of first key grooves are formed in a radial direction along an inclined surface;

A plurality of first keys parallel to the drive shaft and partially protruding from the inclined surface of the drive gear, and movably coupled to the plurality of first key grooves, respectively;

Driven shaft;

A driven gear provided to be movable on the driven shaft, the driven gear comprising a conical gear having a plurality of second key grooves in a radial direction along an inclined surface;

A plurality of second keys parallel to the driven shaft and partially protruding from the inclined surface of the driven gear, and movably coupled to the plurality of second key grooves, respectively;

A power transmission member interconnecting the drive gear and the driven gear through the plurality of first keys and the plurality of second keys, and transmitting a rotational force of the drive gear to the driven gear;

And a speed change control unit configured to adjust the rotation radius of the plurality of first keys coupled to the drive gear and the rotation radius of the plurality of second keys coupled to the driven gear to increase and decrease in opposite directions.
A drive shaft;

A drive gear provided to the drive shaft so as to be mutually accessible or spaced apart, a plurality of first key grooves formed in a radial direction along an inclined surface, the pair of conical gears being disposed to face each other;

A plurality of first keys movably coupled to each first key groove of the drive gear to interconnect the pair of conical gears;

Driven shaft;

A driven gear provided to be mutually accessible or spaced apart from the driven shaft, the second key groove being formed in a radial direction along an inclined surface, and having a pair of conical gears arranged such that the inclined surfaces face each other;

A plurality of second keys movably coupled to respective second key grooves of the driven gear and interconnecting the pair of conical gears;

A power transmission member interconnecting the drive gear and the driven gear through the plurality of first keys and the plurality of second keys, and transmitting a rotational force of the drive gear to the driven gear;

And a shift control unit configured to increase or decrease the gap between the drive gear and the distance between the driven gear.
The method of claim 1,

The shift control unit,

A pair of first guides reciprocally coupled to the drive gear with the plurality of first keys coupled to the plurality of first key grooves therebetween;

A pair of second guides reciprocally coupled to the driven gear with the plurality of second keys coupled to the plurality of second key grooves therebetween;

A holder rotatably supporting the pair of first guides and the pair of second guides, the holder having a threaded portion through which female threads are formed;

A screw shaft which is screwed to the screw portion of the holder and reciprocally moves the holder to reciprocally move the pair of first guides and the pair of second guides from the drive gear and the driven gear, respectively;

And a screw shaft driver for forward and reverse rotating the screw shaft.
The method of claim 1,

And the drive gear and the driven gear are movably coupled to the drive shaft and the driven shaft so that each vertex region is disposed in the opposite direction.
The method of claim 1,

And the drive gear and the driven gear have the same shape and size.
The method of claim 2,

The shift control unit,

A pair of drive screw shafts provided with the drive gears interposed therebetween, and formed with screws in different screw directions at both ends;

A pair of driven screw shafts provided with the driven gears interposed therebetween, and formed with screws in different screw directions at both ends thereof;

A pair of first guide plates provided with the drive gears interposed therebetween, wherein the drive shafts are penetrated by defects and the pair of drive screw shafts are respectively screwed together;

A pair of second guide plates provided with the driven gears interposed therebetween, in which the driven shafts are penetrated with defects, and the pair of driven screw shafts are respectively screwed together;

The pair of conical gears forming the drive gear are approached or spaced apart by the pair of first guide plates, and the pair of conical gears forming the drive gear are approached or spaced apart by the pair of second guide plates. And a screw shaft driver for rotating the pair of drive screw shafts and the driven screw shafts so as to space apart or approach each other the pair of conical gears forming the driven gears as opposed to the spaced apart state.
The method of claim 6,

The screw shaft drive unit,

A drive motor;

A drive motor gear coupled to the shaft of the drive motor;

A first gear meshed with the drive motor gear to rotate and coupled to any one of the pair of drive screw shafts;

A pair of drive sprockets respectively coupled to the pair of drive screw shafts;

A drive chain connecting the pair of drive sprockets and transmitting power;

A second gear that meshes with the first gear and rotates and is coupled to any one of the pair of driven screw shafts;

A pair of driven sprockets respectively coupled to the pair of driven screw shafts;

And a driven chain for connecting the pair of driven sprockets and transmitting power.
The method according to claim 1 or 2,

And the drive shaft, the drive gear, the driven shaft, and the driven gear are each splined to each other.
The method according to claim 1 or 2,

The power transmission member has a closed loop shape, and further includes a plurality of ratchets provided at a predetermined interval in the transverse direction with respect to the movement direction of the power transmission member and the movement direction of the power transmission member,

Each of the plurality of first keys and the plurality of second keys, respectively,

A plurality of main first keys and a plurality of main second keys formed at intervals between the wedge grooves to which the ratchet is engaged and the guide grooves for guiding the sliding of the ratchet;

A continuously variable transmission comprising a plurality of auxiliary first keys and a plurality of auxiliary second keys formed at intervals of a pair of guide grooves for guiding the sliding of the ratchet.
The method of claim 9,

The plurality of main first keys and the plurality of auxiliary first keys are alternately mounted in the plurality of first key grooves.

And a plurality of main second keys and a plurality of auxiliary second keys are alternately mounted in the plurality of second key grooves.
The method of claim 10,

The first fitting protrusion protrudes from the inclination angle of the inclined surface of the driving gear in the plurality of first key grooves, and the first fitting protrusion is coupled to the first fitting protrusion in the plurality of main first keys and the plurality of auxiliary first keys. Each of the fitting grooves are formed recessed,

A second fitting protrusion protrudes at an inclination angle of the driven gear inclined surface in the plurality of second key grooves, and the second fitting protrusion is fitted to the second fitting protrusion in the plurality of main second keys and the plurality of auxiliary second keys. Continuously variable transmission characterized in that each of the fitting grooves are formed.
The method of claim 10,

Each of the wedge grooves of the pair of main first keys disposed with the auxiliary first key interposed therebetween is alternately shifted laterally with respect to the moving direction of the power transmission member.

And each of the wedge grooves of the pair of main second keys arranged with the auxiliary second key interposed therebetween and alternately shifted transversely with respect to the moving direction of the power transmission member.