KR20230084895A - Stepless automatic speed changing apparatus - Google Patents

Abstract

The present invention relates to a stepless automatic transmission apparatus which is able to receive a proper transmission ratio in accordance with the speed of a moving means by using a pair of planetary gear modules and differential gears, reduce the size of a transmission, and obtain economic effects. With the differential gear module in the center, a first planetary gear module is arranged on one side of the differential gear module, and a second planetary gear module is arranged on the other side of the differential gear module. An input shaft is axially engaged with the first planetary gear module and the second planetary gear module. The power for driving an output member engaged with the second planetary gear module is transmitted through the second planetary gear module through an input shaft. The power for transmission in accordance with the driving of the output member is transmitted through the first planetary gear module, the differential gear module, and the second planetary gear module through an input shaft. The differential gear module is operated by considering the rotation of the output member and a load applied to the output member.

Description

Stepless automatic speed changing apparatus}

The present invention relates to a continuously variable automatic transmission, and more particularly, to a continuously variable automatic transmission capable of receiving an appropriate transmission ratio according to the speed of a means of transportation by using a planetary gear module and a differential gear module.

In general, a transmission refers to a transmission device that converts power generated from various engines into required rotational force according to speed and transmits it, and one of various transmission methods includes a transmission method using a planetary gear device.

The planetary gear device includes a sun gear fixed to the driving shaft of the transmission main shaft to transmit rotational force, a ring gear connected to the driven shaft of the transmission main shaft to transmit driving force to the propulsion shaft, and a carrier supported between the sun gear and the ring gear. It is made up of planetary gears. The output of the carrier in this planetary gear device is determined by the number of rotations of the sun gear and the number of rotations of the ring gear.

For example, if the sun gear is rotated counterclockwise while the ring gear is fixed and does not rotate, the carrier is decelerated at 1:K in the counterclockwise direction. Also, when the sun gear is rotated counterclockwise while the ring gear is rotatable, the carrier rotates 1:1 with the sun gear in the counterclockwise direction. In addition, when the sun gear is rotated counterclockwise while the ring gear is rotated clockwise, more deceleration than 1:K is achieved.

When using a pair of planetary gears as described above, only two transmission ratios such as 1:1 or 1:K can be obtained, and conventional transmissions obtain various transmission ratios by combining several pairs of planetary gears. . However, it is practically difficult to combine several pairs of planetary gear units due to economic (cost-effectiveness) and physical (increasing the size of the transmission) limitations.

Republic of Korea Patent Registration No. 10-0294461 'Reduction gear consisting of planetary gear and differential gear set'

The present invention is to solve the above problems, and by using a pair of planetary gear modules and differential gear modules, an appropriate transmission ratio according to the speed of a means of transportation can be provided, thereby reducing the size of the transmission and obtaining economic effects. The purpose is to provide a stepless automatic transmission device.

In order to achieve the above object, the present invention continuously variable automatic transmission includes a first planetary gear module on one side of the differential gear module and a second planetary gear module on the other side of the differential gear module. Is provided, the input shaft is shaft-coupled to the first planetary gear module and the second planetary gear module, and the power transmission for driving the output member coupled to the second planetary gear module is the second planetary gear module through the input shaft. Transmission of power for shifting according to the driving of the output member is performed through an input shaft through a first planetary gear module, a differential gear module, and a second planetary gear module, and the operation of the differential gear module is output The rotation of the member and the load applied to the output member are considered.

In addition, the first planetary gear module includes a first sun gear integrally rotated with the input shaft, a first ring gear provided surrounding the first sun gear, and a first sun gear between the first sun gear and the first ring gear. A plurality of first planetary gears engaged with the sun gear and the first ring gear and rotatably provided, wherein the differential gear module includes second bevel gears and third bevel gears provided facing each other and through which an input shaft passes; It includes a first bevel gear meshed with a second bevel gear and a third bevel gear and rotatably shaft-fixed, wherein the second planetary gear module includes a second sun gear that rotates together with an input shaft, and the second sun gear. A second ring gear surrounded by a second ring gear and a plurality of second planetary gears rotatably provided and engaged with the second sun gear and the second ring gear between the second sun gear and the second ring gear, Each of the first planetary gears is rotatably provided on a plurality of first fixed shafts, one end of which is fixed to a second bevel gear adjacent to one side, and the first bevel gear is interlocked with the rotation of the output member to form an output member. The third bevel gear rotates integrally with the second ring gear, while the plurality of second planetary gears are adjacent to one side of the second planetary gear module. It may be rotatably provided on each of a plurality of second fixed shafts having one end fixed to the output member provided.

In addition, the output member has a cylindrical shape with one end open and has a first planetary gear module, a differential gear module, a second planetary gear module, and an interlocking ring inside, and one end of the second fixed shaft is fixed to the other end, A fixing ring is provided on the inner surface of the output member to be spaced apart from the interlocking ring at a position corresponding to the interlocking ring, and mutual attraction is applied between the fixing ring and the interlocking ring so that the interlocking ring rotates together when the output member rotates. can

In addition, the first sun gear and the second sun gear may be coupled to the input shaft through a one-way bearing capable of only rotating in one direction.

In addition, a chainring rotated according to the rotation of the power generating member, a sprocket provided to rotate along with the input shaft on the other side of the first planetary gear module, and coupled to the chainring and the sprocket to transfer the rotational force of the chainring to the sprocket. A power transmission module including a chain to transmit; may be further included.

According to the present invention, in using a pair of planetary gear modules and differential gear modules, an appropriate transmission ratio according to the speed of a moving means can be provided by adjusting the amount of rotation of the ring gear constituting each planetary gear module. . This can significantly reduce the size compared to transmissions using several pairs of planetary gear modules, and can also reduce the cost and time required to manufacture them, so that economic effects can be obtained.

1 is a perspective view showing a first planetary gear module, a differential gear module, a second planetary gear module, and an interlocking ring applied to the continuously variable automatic transmission of the present invention;
2 is a perspective view showing a first planetary gear module, a differential gear module, and a second planetary gear module applied to the continuously variable automatic transmission of the present invention;
3 is a front view showing a state in which a first planetary gear module, a differential gear module, and a second planetary gear module applied to the continuously variable automatic transmission of the present invention are provided in an output member;
4 is a side view showing the structure of a fixed ring and an interlocking ring applied to the continuously variable automatic transmission of the present invention;
5 is an exploded perspective view showing a structure according to an embodiment of the continuously variable automatic transmission of the present invention;
6 is a combined perspective view showing a structure according to an embodiment of the continuously variable automatic transmission of the present invention;
7 is an exemplary view showing an example in which a structure according to an embodiment of a continuously variable automatic transmission according to the present invention is applied;
8 is a view showing that the final output of the output member is automatically shifted in the example to which the present invention is applied as shown in FIG. 7;

In the present invention, by using a pair of planetary gear modules and differential gear modules, an appropriate transmission ratio according to the speed of the means of transportation can be provided, so that the size of the transmission can be reduced and economic effects can be obtained. A first planetary gear module is provided on one side of the differential gear module, a second planetary gear module is provided on the other side of the differential gear module, and an input shaft is axially coupled to the first planetary gear module and the second planetary gear module, Power transmission for driving the output member coupled to the second planetary gear module is performed through the second planetary gear module through an input shaft, and power transmission for gear shift according to driving of the output member is controlled through an input shaft. 1 is made through a planetary gear module, a differential gear module, and a second planetary gear module, and the operation of the differential gear module is a continuously variable automatic transmission, characterized in that the rotation of the output member and the load applied to the output member are considered. suggests

The scope of the present invention is not limited to the embodiments described below, and can be variously modified and implemented by those skilled in the art within the scope of not departing from the technical gist of the present invention.

Hereinafter, the continuously variable automatic transmission according to the present invention will be described in detail with reference to FIGS. 1 to 8 attached. And in the drawings, for convenience, the teeth of the gear are indicated by hatching or omitted.

As shown in FIGS. 1 to 5, the continuously variable automatic transmission of the present invention includes a first planetary gear module 100, a differential gear module 200 and a second planetary gear module 300, and the first planetary gear An input shaft 410 is provided to pass through parts constituting each of the module 100, the differential gear module 200, and the second planetary gear module 300 or to transmit rotational force.

As shown in FIGS. 1 to 3 , the first planetary gear module 100 includes a first sun gear 110 , a first ring gear 120 and a plurality of first planetary gears 130 . The first sun gear 110 and the first planetary gear 130 may be composed of spur gears, and the first ring gear 120 may be composed of a ring gear having teeth formed along an inner circumference.

Specifically, the first sun gear 110 is integrally rotated with the input shaft 410, so that the rotation amount of the first sun gear 110 is the same as that of the input shaft 410. However, the first sun gear 110 is coupled to the input shaft 410 through a one-way bearing capable of only rotating in one direction so that the first sun gear 110 does not rotate when the input shaft 410 rotates in the reverse direction. desirable. The first ring gear 120 is provided so that the input shaft 410 passes through the center thereof, and surrounds the outer periphery of the first sun gear 110 .

The plurality of first planetary gears 130 are meshed with the first sun gear 110 and the first ring gear 120 between the first sun gear 110 and the first ring gear 120, respectively, and are rotatably are provided For example, the plurality of first planetary gears 130 may be composed of three as shown in the drawing, but are not necessarily limited thereto. The plurality of first planetary gears 130 may be provided such that the first fixed shaft 131 penetrates in a direction parallel to the input shaft 410 so that each of the first planetary gears 130 can rotate. In addition, at least one end of the plurality of first fixed shafts 131 is fixed in the same configuration so that the plurality of first planetary gears 130 can revolve around the first sun gear 110 while maintaining a constant distance therebetween. form a structure The plurality of first planetary gears 130 in the present invention constitutes the differential gear module 200 and has one end fixed to the second bevel gear 220 adjacent to one side of the first planetary gear module 100. It is rotatably provided on each of the first fixing shafts 131 of the dog.

As shown in FIGS. 1 to 4 , the differential gear module 200 includes a first bevel gear 210, a second bevel gear 220, and a third bevel gear 230, and the first planetary gear module It is provided on one side of (100). First, the second bevel gear 220 is provided on one side adjacent to the above-described first planetary gear module 100, and the input shaft 410 passes therethrough, regardless of the rotation of the input shaft 410 around the input shaft 410. can be rotated The third bevel gear 230 is provided facing one side spaced apart from the second bevel gear 220, and the input shaft 410 penetrates and rotates around the input shaft 410 regardless of the rotation of the input shaft 410. possible. The first bevel gear 210 is engaged with the second bevel gear 220 and the third bevel gear 230 and is shaft-fixed to another configuration so as to be able to rotate, and the first bevel gear 210 in the present invention will be described later. It is rotatably fixed to the interlocking ring 430 to be shafted. One such first bevel gear 210 may be provided, as well as a plurality of symmetrically provided as shown in the drawing, for example, four first bevel gears 210 are on the same plane. can be placed. At this time, the plurality of first bevel gears 210 are all rotatably shaft-fixed to the interlocking ring 430, and the interlocking ring 430 is rotated in conjunction with the rotation of the output member 420, the output member 420 ) may revolve around the input shaft 410 in the same direction as the rotation.

As shown in FIGS. 1 to 3 , the second planetary gear module 300 includes a second sun gear 310, a second ring gear 320, and a plurality of second planetary gears 330, 1 may be configured the same as the planetary gear module 100. The second sun gear 310 and the second planetary gear 330 may be composed of spur gears, and the second ring gear 320 may be composed of a ring gear having gear teeth formed along an inner periphery.

Specifically, the second sun gear 310 is provided to rotate integrally with the input shaft 410, so that the rotation amount of the second sun gear 310 is the same as that of the input shaft 410. However, the second sun gear 310 is coupled to the input shaft 410 through a one-way bearing capable of only rotating in one direction so that the second sun gear 310 does not rotate when the input shaft 410 rotates in the reverse direction. desirable. The second ring gear 320 is provided so that the input shaft 410 passes through the center thereof, and surrounds the outer periphery of the second sun gear 310 . The second ring gear 320 is configured to rotate integrally with the third bevel gear 230 . At this time, the third bevel gear 230 and the second ring gear 320 may have a gear ratio of 1:1, so that the amount of rotation of the second ring gear 320 is the same as that of the third bevel gear 230. has rotation. For example, a power transmission plate 510 may be further provided between the third bevel gear 230 and the second ring gear 320, and the power transmission plate 510 is hollow so that the input shaft 410 passes therethrough. A through-shaped disc shape may be achieved, and the third bevel gear 230 may be integrally coupled to one side and the second ring gear 320 may be integrally coupled to the other side.

The plurality of second planetary gears 330 are meshed with the second sun gear 310 and the second ring gear 320 between the second sun gear 310 and the second ring gear 320, respectively, and are rotatably are provided For example, the plurality of second planetary gears 330 may be composed of three as shown in the drawing, but are not necessarily limited thereto. The plurality of second planetary gears 330 may be provided so that the second fixed shaft 331 penetrates in a direction parallel to the input shaft 410 so that each rotates. In addition, at least one end of the plurality of second fixed shafts 331 is fixed in the same configuration so that the plurality of second planetary gears 330 can revolve around the second sun gear 310 while maintaining a constant distance therebetween. form a structure As shown in FIG. 3, the plurality of second planetary gears 330 in the present invention have one end fixed to the output member 420 provided adjacent to one side of the second planetary gear module 300. It is rotatably provided to each of the second fixing shafts 331 .

In the output member 420, for example, a disc-shaped portion may be provided adjacent to one side of the second planetary gear module 300, and at least a part of the edge may extend toward the other side. As a specific example, the output member 420 may be horizontally arranged in a tubular shape with one end open, as shown in FIGS. 3, 5, and 6, and the first planetary gear module 100, the differential gear module 200, the second planetary gear module 300, and the interlocking ring 440 may be provided therein. One end of the plurality of second fixed shafts 331 may be fixed to the other end of the output member 420, and wheels for actual driving may be provided on the outer side of the sidewall connecting one end and the other end, as shown in FIG. can

In addition, a fixing ring 430 spaced apart from the interlocking ring 440 may be provided on the inner side of the sidewall of the output member 420 (the inner surface of the output member 420) at a position corresponding to the interlocking ring 440. . Specifically, the interlocking ring 440 is formed in a ring shape surrounding a point where the first bevel gear 210 is provided in the differential gear module 200, and interlocking magnets 441 may be provided along the outer periphery. . The stationary ring 430 is formed in a ring shape surrounding the stationary ring 430, and a stationary magnet 431 may be provided along the inner periphery. The fixed ring 430 and the interlocking ring 440 are disposed somewhat apart, and mutual attraction is acted upon due to magnetic force between the interlocking magnet 441 and the stationary magnet 431 . Therefore, when the output member 420 rotates, the fixed ring 430 rotates integrally with the output member 420, and the interlocking ring 440 rotates due to the attractive force with the fixed ring 430, The first bevel gear 210 rotatably shaft-fixed to the interlocking ring 440 is processed around the input shaft 410.

And, as shown in FIGS. 5 and 6, the present invention may further include a wheel plate 520 forming a disc shape to block the open end of the output member 420, and the wheel plate 520 has an input shaft 410 at the center. ) may be provided so as to penetrate and be independent of the rotation of the input shaft 410. The other end of the first fixed shaft 131, which allows the first planetary gear 130 to rotate, may be fixed to the wheel plate 520.

In the present invention as described above, power transmission for driving the output member 420 is performed through the second planetary gear module 300 through the input shaft 410, and shifts according to the drive of the output member 420. Power transmission for is made through the first planetary gear module 100, the differential gear module 200, and the second planetary gear module 300 through the input shaft 410. At this time, the operation of the differential gear module 200 is performed in consideration of the rotation of the output member 420 and the load applied to the output member 420 .

On the other hand, the present invention is a configuration for providing rotational force to the input shaft 410, and may further include a power generating member 600 and a power transmission module 700 as shown in FIGS. 5 to 7 . The power generating member 600 may generate rotational force through electricity, such as a motor, or may generate rotational force through a user's manipulation, such as a bicycle pedal. The power transmission module 700 may transfer the rotational force generated from the power generating member 600 to the input shaft 410 as it is or transmit it after being decelerated or accelerated.

As a specific example, the power transmission module 700 may include a chainring 710, a sprocket 720, and a chain 730 like a bicycle. The chainring 710 is axially rotated according to the rotation of the power generating member 600, and the sprocket 720 may be provided to rotate together with the input shaft 410 on the other side of the first planetary gear module 100. At this time, the chain 730 is coupled to the chainring 710 and the sprocket 720 while surrounding the chainring 710 and the sprocket 720 at once, so that the rotational force of the chainring 710 can be transmitted to the sprocket 720. there is. However, it is preferable that the input shaft 410 is coupled to the sprocket 720 through a one-way bearing capable of only rotating in one direction so that the input shaft 410 does not rotate reversely when the sprocket 720 rotates backward.

The detailed description of the operation of the continuously variable automatic transmission according to the present invention as described above is as follows. In each of the first planetary gear module 100 and the second planetary gear module 300, the second bevel gear 220 and the output member 420 serve as carriers. The planetary gear module, such as the first planetary gear module 100 and the second planetary gear module 300, can organically change the output of the carrier by changing the rotation amount of the ring gear, and the following [Equation 1] applies.

: 링기어 회전량,

: 태양기어 회전량,

: 캐리어 회전량,

: 유성기어모듈의 감속비)(

: ring gear rotation amount,

: sun gear rotation amount,

: carrier rotation amount,

: Reduction ratio of planetary gear module)

In the differential gear module 200, the amount of rotation of the third bevel gear 330 is determined according to the amount of rotation of the first bevel gear 310 and the second bevel gear 320. is applied.

: 제1 베벨기어의 회전량,

: 제2 베벨기어의 회전량,

: 제3 베벨기어의 회전량)(

: Rotation amount of the first bevel gear,

: Rotation amount of the second bevel gear,

: Amount of rotation of the 3rd bevel gear)

의 범위는

과

에 의해 -

~ 무한대까지 가능하다.As confirmed in [Equation 2] above,

the range of

class

by -

~ up to infinity

When the final output through the output member 420 is derived using [Equation 1] and [Equation 2], it is as follows. At this time, the description will be made on the premise that the reduction ratio of the first planetary gear module and the reduction ratio of the second planetary gear module are the same.

1) Output of the output member 420 serving as a carrier in the second planetary gear module 300

이면, 제2 태양기어(310)로

회전량이 전달되어, 제2 태양기어(310)는 반시계방향으로

만큼 회전하게 된다. 그리고 제2 링기어(320)은 제3 베벨기어(230)와 일체로 회전되는바, 제2 링기어(320)의 회전량(

)은, 제3 베벨기어(230)의 회전량(

)이 적용될 수 있다. 따라서, 제2 태양기어(310)로 전달된 회전량(

)과 제2 링기어의 회전량(

)에 따라 캐리어 역할을 하는 출력부재(420)의 출력량(

)이 결정되며, 출력부재(420)의 출력량(

)은 아래의 [수학식 3]과 같이 나타낼 수 있다.The amount of rotation of the input shaft

On the other side, to the second sun gear 310

The amount of rotation is transmitted, and the second sun gear 310 rotates counterclockwise.

rotate as much as And since the second ring gear 320 is integrally rotated with the third bevel gear 230, the amount of rotation of the second ring gear 320 (

) is the amount of rotation of the third bevel gear 230 (

) can be applied. Therefore, the amount of rotation transmitted to the second sun gear 310 (

) and the amount of rotation of the second ring gear (

), the output amount of the output member 420 serving as a carrier (

) is determined, and the output amount of the output member 420 (

) can be expressed as in [Equation 3] below.

: 제3 베벨기어 회전량,

: 제2 태양기어 회전량,

: 출력부재 회전량,

: 제2 유성기어모듈의 감속비)(

: 3rd bevel gear rotation amount,

: 2nd sun gear rotation amount,

: Output member rotation amount,

: Reduction ratio of the second planetary gear module)

The output member 420 transmits power to the wheels and rotates together with the second ring gear 320 until the second sun gear 310 rotates next.

2) Rotation amount of the third bevel gear 230 through the first planetary gear module 100

이면, 제1 태양기어(110)로

회전량이 전달되고, 제1 유성기어(130)에 의해

로 감속되어, 캐리어 역할을 하는 제2 베벨기어(220)를 반시계방향으로

만큼 회전시킨다. 이를 상기 [수학식 2]에 적용하면 아래의 [수학식 4]와 같이 나타낼 수 있다.As shown in [Equation 2], the amount of rotation of the third bevel gear 230 is determined according to the amount of rotation of the first bevel gear 210 and the second bevel gear 220. At this time, the amount of rotation of the second bevel gear 220 is determined by the first planetary gear module 100 . That is, the amount of rotation of the input shaft

On the other side, to the first sun gear 110

The amount of rotation is transmitted, and by the first planetary gear 130

is decelerated, and rotate the second bevel gear 220, which serves as a carrier, in a counterclockwise direction.

rotate as much as If this is applied to [Equation 2] above, it can be expressed as [Equation 4] below.

: 제1 베벨기어의 회전량,

: 제3 베벨기어의 회전량,

: 제2 베벨기어의 회전량)(

: Rotation amount of the first bevel gear,

: The amount of rotation of the third bevel gear,

: Amount of rotation of the second bevel gear)

를 상기 [수학식 3]에 적용하면, 아래와 같은 [수학식 5]가 도출된다.Therefore, derived from [Equation 4] above

When is applied to the above [Equation 3], the following [Equation 5] is derived.

)가 1일 때, 스프라켓(720)의 회전수(

)는 설계에 따라 다양한 기어비로 설계가 가능하다. 구체적으로,

=1:5로 설계할 경우,

이며, 출력부재(420)의 최종 출력(

)은, 바퀴 회전수(

)에 비례함을 확인할 수 있다. 따라서, 체인링(710)의 1 회전할 때에 발생되는 출력부재(420)의 최종 출력(

)은 아래의 [표 1] 및 도 8에 도시된 바와 같이 바퀴 회전수에 따라 자동으로 변속이 가능해진다. For example, when the power generating member 600 is composed of a pedal and the power transmission member 700 is composed of a chainring 710, a sprocket 720 and a chain 730, the number of revolutions of the chainring 710 (

) is 1, the number of revolutions of the sprocket 720 (

) can be designed with various gear ratios depending on the design. Specifically,

= 1:5 design,

And, the final output of the output member 420 (

) is the number of wheel revolutions (

), it can be seen that it is proportional to Therefore, the final output of the output member 420 generated when the chainring 710 rotates once (

) is automatically shifted according to the number of wheel revolutions, as shown in [Table 1] and FIG. 8 below.

resistance

0 0 0 0 One 0.56 0.1 0.50 One 1.22 0.1 1.10 One 2.02 0.1 1.82 One 2.98 0.1 2.68 One 4.13 0.1 3.72 0 3.72 0.1 3.35 0 3.35 0.1 3.01 0 3.01 0.1 2.71 0 2.71 0.1 2.44 0 2.44 0.1 2.20 One 3.49 0.5 1.74 One 2.88 0.5 1.44 One 2.47 0.5 1.24 One 2.21 0.5 1.10 One 2.03 0.5 1.01 One 1.91 0.3 1.33 One 2.33 0.3 1.63 One 2.73 0.3 1.91 One 3.11 0.5 1.55 One 2.63 0.5 1.31 One 2.31 0.1 2.08 One 3.32 0.1 2.99 0 2.99 0.1 2.69 0 2.69 0.1 2.42 0 2.42 0.1 2.18

As described above, the continuously variable automatic transmission of the present invention uses a pair of planetary gear modules 100 and 300 and a differential gear module 200, and the rotation of the ring gears 120 and 320 constituting each planetary gear module 100 and 300 By adjusting the total amount, an appropriate transmission ratio according to the speed of the means of transportation (bicycle, etc.) can be provided. Therefore, compared to transmissions using several pairs of planetary gear modules, the size can be significantly reduced, and the cost and time required to manufacture them can be reduced, and thus economic effects can be obtained.

100: first planetary gear module 110: first sun gear
120: first ring gear 130: first planetary gear
131: first fixed axis
200: differential gear module 210: first bevel gear
220: second bevel gear 230: third bevel gear
300: second planetary gear module 310: second sun gear
320: second ring gear 330: second planetary gear
331: second fixed shaft
410: input shaft 420: output member
430: fixed ring 431: fixed magnet
440: interlocking ring 441: interlocking magnet
510: power transmission plate 520: wheel plate
600: power generating member
700: power transmission module 710: chainring
720: sprocket 730: chain

Claims (5)

Centered on the differential gear module 200, the first planetary gear module 100 is provided on one side of the differential gear module 200, and the second planetary gear module 300 is provided on the other side of the differential gear module 200. Is provided, the input shaft 410 is shaft-coupled to the first planetary gear module 100 and the second planetary gear module 300,
Transmission of power for driving the output member 420 coupled to the second planetary gear module 300 is achieved through the second planetary gear module 300 through the input shaft 410,
Power transmission for gear shift according to the drive of the output member 420 is made through the first planetary gear module 100, the differential gear module 200, and the second planetary gear module 300 through the input shaft 410. lose,
The operation of the differential gear module 200 is a continuously variable automatic transmission, characterized in that the rotation of the output member 420 and the load applied to the output member 420 are considered. According to claim 1,
The first planetary gear module 100 includes a first sun gear 110 integrally rotated with an input shaft 410, a first ring gear 120 provided surrounding the first sun gear 110, Between the first sun gear 110 and the first ring gear 120, a plurality of first planetary gears 130 meshed with and rotatably provided with the first sun gear 110 and the first ring gear 120 are provided. include,
The differential gear module 200 includes a second bevel gear 220 and a third bevel gear 230, the second bevel gear 220 and the third bevel gear ( 230) and a first bevel gear 210 rotatably shaft-fixed,
The second planetary gear module 300 includes a second sun gear 310 rotating together with an input shaft 410, a second ring gear 320 provided surrounding the second sun gear 310, and the second planetary gear module 300. 2 Includes a plurality of second planetary gears 330 rotatably provided and engaged with the second sun gear 310 and the second ring gear 320 between the sun gear 310 and the second ring gear 320 but
The plurality of first planetary gears 130 are rotatably provided on a plurality of first fixed shafts 131 having one end fixed to the second bevel gear 220 adjacent to one side, respectively,
The first bevel gear 210 is shaft-fixed to an interlocking ring 440 that rotates in the same direction as the output member 420 in conjunction with the rotation of the output member 420,
While the third bevel gear 230 rotates integrally with the second ring gear 320,
The plurality of second planetary gears 330 each rotate on a plurality of second fixed shafts 331 having one end fixed to the output member 420 provided adjacent to one side of the second planetary gear module 300. A continuously variable automatic transmission, characterized in that it is provided as possible. According to claim 2,
The output member 420 has a cylindrical shape with one end open, and includes a first planetary gear module 100, a differential gear module 200, a second planetary gear module 300, and an interlocking ring 440 therein. And, one end of the second fixing shaft 331 is fixed to the other end,
On the inner surface of the output member 420, a fixing ring 430 is provided to be spaced apart from the interlocking ring 440 at a position corresponding to the interlocking ring 440,
The fixed ring 430 and the interlocking ring 440 are operated by mutual attraction, so that the interlocking ring 440 rotates together when the output member 420 rotates. According to claim 2,
The continuously variable automatic transmission, characterized in that the first sun gear (110) and the second sun gear (310) are coupled to the input shaft (410) through a one-way bearing capable of only rotating in one direction. According to claim 2,
A chainring 710 that is axially rotated according to the rotation of the power generating member 600,
A sprocket 720 provided to rotate together with the input shaft 410 on the other side of the first planetary gear module 100;
A power transmission module 700 including a chain 730 coupled to the chainring 710 and the sprocket 720 to transmit rotational force of the chainring 710 to the sprocket 720; characterized in that it further comprises stepless automatic transmission.

Images