KR20050006742A - planetary gear set, clutches and brakes for a continuously variable transmission - Google Patents

planetary gear set, clutches and brakes for a continuously variable transmission Download PDF

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Publication number
KR20050006742A
KR20050006742A KR1020030046676A KR20030046676A KR20050006742A KR 20050006742 A KR20050006742 A KR 20050006742A KR 1020030046676 A KR1020030046676 A KR 1020030046676A KR 20030046676 A KR20030046676 A KR 20030046676A KR 20050006742 A KR20050006742 A KR 20050006742A
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South Korea
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clutch
sun gear
stepped pinion
continuously variable
variable transmission
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KR1020030046676A
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Korean (ko)
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KR100535086B1 (en
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고정한
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현대자동차주식회사
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Structure Of Transmissions (AREA)

Abstract

PURPOSE: A planetary gear device and an operation mechanism for a continuously variable transmission are provided to achieve a kick down function by rapidly lowering a transmission gear ratio in desired time in hardware. CONSTITUTION: A planetary gear device and an operation mechanism for a continuously variable transmission comprises a stepped pinion(PN) in which a large diameter part and a small diameter part are integrally formed on a concentric shaft; a ring gear(R) engaged with the stepped pinion and connected to an output shaft; a first sun gear(S1) engaged with the large diameter part of the stepped pinion; a second sun gear(S2) engaged with the small diameter part of the stepped pinion; a first clutch(C1) and a third clutch(C3) changing the power transmission state of an input shaft and the first sun gear; a one-way clutch(F1) installed between the first clutch and the first sun gear; a second clutch(C2) changing the power transmission state of an input shaft of the second sun gear; a first brake(B1) fixing a carrier of the stepped pinion; and a fourth clutch(C4) changing a state of connecting the carrier of the stepped pinion to the ring gear.

Description

무단변속기용 유성기어장치 및 작동기구{planetary gear set, clutches and brakes for a continuously variable transmission}Planetary gear sets, clutches and brakes for a continuously variable transmission}

본 발명은 무단변속기에 사용되는 유성기어장치 및 그 작동기구에 관한 것으로서, 보다 상세하게는 벨트식 무단변속기에서 종래의 유단 자동변속기에서 구현하던 킥다운 (kick down) 작동을 가능하도록 하는 기술에 관한 것이다.The present invention relates to a planetary gear device used in a continuously variable transmission and an operation mechanism thereof, and more particularly, to a technique for enabling a kick down operation implemented in a conventional stepped automatic transmission in a belt continuously variable transmission. will be.

벨트식 무단변속기는 구동풀리와 종동풀리가 벨트에 의해 연결되어 구동풀리와 종동풀리의 직경 변화에 따라 원하는 변속비를 연속적으로 얻을 수 있도록 하는데, 상기 구동풀리로 입력되는 회전력은 통상 엔진으로부터 토크컨버터를 통하여 공급되고, 상기 토크컨버터와 구동풀리의 사이에는 전후진 변화를 가능케 하기 위한 유성기어장치가 구비되어 있다.The belt continuously variable transmission allows the drive pulley and the driven pulley to be connected by a belt so that the desired transmission ratio can be continuously obtained according to the change of the diameter of the drive pulley and the driven pulley. The rotational force input to the drive pulley is normally used to obtain a torque converter from the engine. It is supplied through, the planetary gear device is provided between the torque converter and the drive pulley to enable the forward and backward change.

상기와 같은 구성을 가지고 있는 무단변속기에서는 운전자가 급가속을 하고자 할 때, 원하는 변속비를 형성하도록 상기 구동풀리와 종동풀리의 직경을 원하는 시간 내에 급격히 변화시키는 것이 매우 어렵다. 즉, 종래의 유단 자동변속기에서 순간적으로 기어비를 변화시켜서 구현하던 킥다운 기능을 제공할 수 없는 상태이다.In the continuously variable transmission having the configuration described above, when the driver intends to accelerate, it is very difficult to rapidly change the diameters of the driving pulley and the driven pulley within a desired time so as to form a desired speed ratio. In other words, in the conventional stepped automatic transmission, it is not possible to provide the kickdown function implemented by changing the gear ratio instantaneously.

따라서, 운전자는 무단변속기가 장착된 차량에서 만족할만한 가속감을 얻기가 어려운 실정이다.Therefore, it is difficult for a driver to obtain a satisfactory acceleration feeling in a vehicle equipped with a continuously variable transmission.

이에 본 발명은 상기한 바와 같은 문제점을 해결하기 위하여 안출된 것으로서, 무단변속기에서도 하드웨어적으로 변속비를 원하는 시간 내에 급격히 낮추어 킥다운 기능을 구현할 수 있도록 한 무단변속기용 유성기어장치 및 작동기구를 제공함에 그 목적이 있다.Accordingly, the present invention has been made to solve the problems described above, to provide a planetary gear device and operation mechanism for a continuously variable transmission to implement a kick-down function by sharply lowering the transmission ratio in a desired time even in a continuously variable transmission. The purpose is.

도 1은 본 발명에 따른 무단변속기용 유성기어장치 및 작동기구를 도시한 다이어그램,1 is a diagram showing a planetary gear device and operating mechanism for a continuously variable transmission according to the present invention;

도 2는 도 1의 유성기어장치에 대한 레버 다이어그램이다.FIG. 2 is a lever diagram of the planetary gear device of FIG. 1.

<도면의 주요 부분에 대한 부호의 간단한 설명><Brief description of symbols for the main parts of the drawings>

PN; 단차피니언 R; 링기어PN; Stepped pinion R; Ring gear

C1; 제1클러치 C3; 제3클러치C1; First clutch C3; 3rd clutch

F1; 원웨이클러치 C2; 제2클러치F1; One-way clutch C2; Second clutch

B1; 제1브레이크 C4; 제4클러치B1; First brake C4; 4th clutch

S1; 제1선기어 S2; 제2선기어S1; First sun gear S2; 2nd Sun Gear

상기한 바와 같은 목적을 달성하기 위한 본 발명 무단변속기용 유성기어장치 및 작동기구는 서로 크고 작은 직경을 가진 큰직경부와 작은직경부가 동심축을 이루며 일체로 형성된 단차피니언과;The present invention provides a planetary gear device and an actuating mechanism for a continuously variable transmission for achieving the object as described above;

상기 단차피니언에 치합되고 출력축에 연결된 링기어와;A ring gear meshed with the stepped pinion and connected to the output shaft;

상기 단차피니언의 큰직경부에 치합되는 제1선기어와;A first sun gear meshed with a large diameter portion of the stepped pinion;

상기 단차피니언의 작은직경부에 치합되는 제2선기어와;A second sun gear meshed with a small diameter portion of the stepped pinion;

상기 제1선기어와 입력축의 동력전달상태를 전환하는 제1클러치 및 제3클러치와;A first clutch and a third clutch for switching a power transmission state between the first sun gear and the input shaft;

상기 제1클러치와 제1선기어 사이에 설치된 원웨이클러치와;A one-way clutch installed between the first clutch and the first sun gear;

상기 제2선기어와 입력축의 동력전달상태를 전환하는 제2클러치와;A second clutch for switching a power transmission state between the second sun gear and the input shaft;

상기 단차피니언의 캐리어를 고정하는 제1브레이크와;A first brake fixing the carrier of the stepped pinion;

상기 단차피니언의 캐리어를 상기 링기어에 연결시키는 상태를 전환하는 제4클러치를 포함하여 구성된 것을 특징으로 한다.And a fourth clutch for switching a state of connecting the carrier of the stepped pinion to the ring gear.

이하, 첨부된 도면을 참조하여 본 발명의 바람직한 실시예를 설명하면 다음과 같다.Hereinafter, exemplary embodiments of the present invention will be described with reference to the accompanying drawings.

도 1은 본 발명에 따른 무단변속기용 유성기어장치 및 작동기구를 도시한 다이어그램으로서, 서로 크고 작은 직경을 가진 큰직경부와 작은직경부가 동심축을 이루며 일체로 형성된 단차피니언(PN)과, 상기 단차피니언(PN)에 치합되고 출력축에 연결된 링기어(R)와, 상기 단차피니언(PN)의 큰직경부에 치합되는 제1선기어(S1)와, 상기 단차피니언(PN)의 작은직경부에 치합되는 제2선기어(S2)와, 상기 제1선기어(S1)와 입력축의 동력전달상태를 전환하는 제1클러치(C1) 및 제3클러치(C3)와, 상기 제1클러치(C1)와 제1선기어(S1) 사이에 설치된 원웨이클러치(F1)와, 상기 제2선기어(S2)와 입력축의 동력전달상태를 전환하는 제2클러치(C2)와, 상기 단차피니언(PN)의 캐리어를 고정하는 제1브레이크(B1)와, 상기 단차피니언(PN)의 캐리어를 상기 링기어(R)에 연결시키는 상태를 전환하는 제4클러치(C4)가 도시되어 있다.1 is a diagram illustrating a planetary gear device and an actuating mechanism for a continuously variable transmission according to the present invention. A stepped pinion (PN) integrally formed with a large diameter portion and a small diameter portion having a large diameter and a small diameter concentric with each other, and the step Ring gear (R) meshed with pinion (PN) and connected to output shaft, first sun gear (S1) meshed with large diameter part of stepped pinion (PN), and small diameter part of stepped pinion (PN) The second sun gear S2, the first clutch C1 and the third clutch C3 for switching the power transmission state between the first sun gear S1 and the input shaft, and the first clutch C1 and the first clutch. The one-way clutch F1 provided between the sun gear S1, the second clutch C2 for switching the power transmission state between the second sun gear S2 and the input shaft, and the carrier of the stepped pinion PN are fixed. Before the state of connecting the first brake (B1) and the carrier of the stepped pinion (PN) to the ring gear (R) A fourth clutch (C4), which is shown.

상기 링기어(R)는 상기 단차피니언(PN)의 큰직경부에 치합되어 있고, 상기 링기어(R)는 출력축을 통하여 벨트식 무단변속기의 구동풀리에 연결되며, 상기 입력축은 토크컨버터의 터빈에 연결되어 엔진으로부터의 동력을 전달받도록 구성한다.The ring gear (R) is engaged with the large diameter portion of the stepped pinion (PN), the ring gear (R) is connected to the drive pulley of the belt-type continuously variable transmission through the output shaft, the input shaft is a turbine of the torque converter Is configured to receive power from the engine.

한편, 상기 원웨이클러치(F1)는 상기 입력축의 동력을 제1선기어(S1)로 전달하는 상태로 설치한다.On the other hand, the one-way clutch (F1) is installed in a state that transmits the power of the input shaft to the first sun gear (S1).

즉, 종래에는 무단변속기에 사용되는 유성기어장치가 단순히 전진과 후진 상태만을 선택하도록 하는 기능을 제공하였던 것에 비하여, 본 발명의 유성기어장치 및 작동기구는 상기 제1선기어(S1)와 제2선기어(S2)가 상기 단차피니언(PN)과 형성하는 기어비를 이용하여 전진 2단과 후진을 선택할 수 있는 메커니즘을 제공함으로써, 킥다운이 필요한 시점에 상기 전진 2단의 변속비를 전환하여 원하는 짧은 시간 내에 저단의 변속비를 얻어내도록 한 것이다.That is, the planetary gear device and the operating mechanism of the present invention are the first sun gear (S1) and the second sun gear, whereas the planetary gear device used in the continuously variable transmission provides a function of simply selecting forward and backward states. (S2) provides a mechanism to select the second forward and the second forward by using the gear ratio formed with the stepped pinion (PN), by switching the speed ratio of the two forward speed when the kickdown is required, the low stage within the desired short time The gear ratio of

상기한 바와 같은 유성기어장치에서 상기 전진2단 변속비를 도 2에 도시된 레버 다이어그램을 참조하여 비교하여 보면 다음과 같다.In the planetary gear device as described above, the forward two speed ratios are compared with reference to the lever diagram shown in FIG. 2.

도 2의 레버 다이어그램은 R과 c1 사이는 제1선기어의 잇수, c1과 S1 사이는 링기어(R)의 잇수, R과 c2 사이는 제2선기어의 잇수, c2와 S2사이는 링기어(R)의잇수를 정량적이 아닌 정성적으로 표현하고 있는데, 출력축과 직결된 링기어(R)의 회전속도를 동일한 상태로 놓고, 이와 같은 동일한 출력속도를 내기 위한 제1선기어(S1)의 속도와 제2선기어(S2)의 속도를 비교하고 있는 것이다.The lever diagram of FIG. 2 shows the number of teeth of the first sun gear between R and c1, the number of teeth of the ring gear R between c1 and S1, the number of teeth of the second sun gear between R and c2, and the ring gear R between c2 and S2. The number of teeth is expressed qualitatively, not quantitatively.The rotation speed of the ring gear (R) directly connected to the output shaft is set to the same state, and the speed and the first speed of the first sun gear (S1) The speed of the two-wire gear S2 is being compared.

이 레버 다이어그램으로부터 동일한 출력축 회전속도를 얻기 위한 제1선기어(S1)와 제2선기어(S2)의 회전속도가 다르며, 동일한 출력축 회전속도를 얻기 위해서는 상기 단차피니언(PN)의 큰직경부에 치합되는 제1선기어(S1)가 더 빠른 속도로 회전해야 함을 알 수 있다.From this lever diagram, the rotation speeds of the first sun gear S1 and the second sun gear S2 are different to obtain the same output shaft rotational speed, and in order to obtain the same output shaft rotational speed, they are fitted to the larger diameter portion of the stepped pinion PN. It can be seen that the first sun gear S1 should rotate at a higher speed.

따라서, 실제 무단변속기에서는 상기 제2선기어(S2)를 입력으로 하는 상태를 기본적인 주행상태로 하고, 킥다운이 요구되는 경우에는 입력을 제1선기어(S1)로 바꾸어줌으로써 순간적으로 낮은 변속비를 얻어내어 원하는 급가속의 특성을 얻어낼 수 있는 것이다.Therefore, in the continuously variable transmission, the state in which the second sun gear S2 is input as the basic driving state is changed, and when the kickdown is required, the input is changed to the first sun gear S1 to obtain a low speed ratio instantaneously. It is possible to obtain the desired acceleration characteristics.

참고적으로 상기 유성기어장치와 작동기구에 의해 구현되는 나머지 상태들을 다음의 표 1을 통해 설명한다.For reference, the remaining states implemented by the planetary gear device and the operating mechanism will be described with the following Table 1.

C1C1 C2C2 C3C3 C4C4 B1B1 F1F1 엔진브레이크Engine brake RR ●● ●● ○○ D1D1 ●● ●● ▲▲ ×× D2D2 ○○ ●● ●● △△ ○○ LL ●● ●● △△ ○○

후진변속단을 만들기 위해서는 제3클러치(C3)와 제4클러치(C4)를 작동시킨다. 따라서 입력축으로 들어온 회전력은 제1선기어(S1)로 전달되고, 상기 제4클러치(C4)에 의해 링기어(R)와 캐리어가 일체로 되어 상기 단차피니언(PN)은자전이 불가능하여 상기 제1선기어(S1)의 회전력에 의해 상기 단차피니언(PN) 캐리어 및 링기어(R)가 일체로 입력축 회전방향과 동일한 방향으로 회전되어 후진 변속단을 형성하게 된다.In order to make the reverse shift stage, the third clutch C3 and the fourth clutch C4 are operated. Therefore, the rotational force entered into the input shaft is transmitted to the first sun gear S1, and the ring gear R and the carrier are integrated by the fourth clutch C4, so that the stepped pinion PN cannot be rotated so that the first sun gear The stepped pinion (PN) carrier and the ring gear (R) are integrally rotated in the same direction as the input shaft rotation direction by the rotational force of S1 to form a reverse shift stage.

D2는 상기 제2선기어(S2)를 입력으로 하는 기본적인 주행상태를 위한 변속단으로서, 제2클러치(C2)와 제1브레이크(B1)를 작동시킨다. 따라서, 입력축으로부터 상기 제2선기어(S2)로 입력된 회전력은 상기 제1브레이크(B1)에 의해 캐리어가 고정되었으므로 상기 단차피니언(PN)의 작은직경부를 회전시키고, 그에 따라 링기어(R)가 입력축 회전 방향에 반대방향으로 회전하여 D2 변속단을 형성하게 된다.D2 is a shift stage for a basic driving state using the second sun gear S2 as an input, and operates the second clutch C2 and the first brake B1. Therefore, since the carrier is fixed to the second sun gear S2 from the input shaft by the first brake B1, the small diameter portion of the stepped pinion PN is rotated, so that the ring gear R is rotated. The D2 shift stage is formed by rotating in the direction opposite to the input shaft rotation direction.

D1은 상기 D2를 기본적인 주행상태로 하다가 운전자의 급가속 요구가 있으면, 이를 반영하여 킥다운 기능을 수행하기 위해서 상기한 바와 같이 변속비를 짧은 시간내에 하드웨어적으로 변화시키기 위해 마련된 변속단으로서, 제1클러치(C1)와 제1브레이크(B1)를 작동시키며, 이때 상기 원웨이클러치(F1)가 입력축으로부터의 회전력을 제1선기어(S1)로 전달하게 되어 있다.D1 is a shift stage provided to change the transmission ratio in hardware within a short time as described above in order to perform the kick-down function by reflecting the driver's rapid acceleration request while making D2 the basic driving state. The clutch C1 and the first brake B1 are operated. At this time, the one-way clutch F1 transmits the rotational force from the input shaft to the first sun gear S1.

상기 제1클러치(C1)를 통과한 회전력은 상기 원웨이클러치(F1)를 통해 제1선기어(S1)를 구동하고, 상기 캐리어가 고정되어 있으므로, 상기 단차피니언(PN)의 큰직경부에 제1선기어(S1)로부터의 회전력이 전달되어 상기 링기어(R)로 전달되므로, 상기 링기어(R)는 상기 입력축과 반대방향으로 회전하여 D1 변속단을 형성하게 되며, 이 D1 변속단은 상기한 바와 같이 상기 제1선기어(S1)가 단차피니언(PN)의 큰직경부와 치합됨으로써, 제2선기어(S2)가 단차피니언(PN)의 작은직경부와 치합된경우에 비하여 낮은 변속비를 형성하게 된다.The rotational force passing through the first clutch C1 drives the first sun gear S1 through the one-way clutch F1, and the carrier is fixed, so that the rotational force passing through the first clutch C1 is applied to the large diameter portion of the stepped pinion PN. Since the rotational force from the first sun gear S1 is transmitted to the ring gear R, the ring gear R rotates in a direction opposite to the input shaft to form a D1 shift stage. As described above, since the first sun gear S1 is engaged with the large diameter portion of the stepped pinion PN, the second sun gear S2 is lower than the small diameter portion of the stepped pinion PN. Done.

한편, 상기 제1클러치(C1)에 원웨이클러치(F1)를 직렬로 함께 사용한 이유는 상기 D1 변속단에서 D2 변속단으로 전환할 때 제1클러치(C1)를 잡고 있는 상태에서도 제2클러치(C2)를 잡아 D2 변속단으로 변속할 수 있도록 하는 소위 비동기 변속을 가능하도록 하여 제어가 용이하게 하기 위한 것이다.On the other hand, the reason why the one-way clutch F1 is used in series with the first clutch C1 is that the second clutch (1) is held even when the first clutch C1 is held when switching from the D1 shift stage to the D2 shift stage. It is to facilitate the control by enabling a so-called asynchronous shift that allows the shift to the shift stage D2 by holding C2).

한편, 상기 제1클러치(C1)와 병렬로 제3클러치(C3)를 사용하고 있는 이유는 엔진브레이크의 기능을 확보하기 위한 것으로서, 상기 표 1에 도시된 바와 같이 상기 제3클러치(C3)는 R과 L단에서 엔진브레이크가 가능하도록 하고 있다.The reason why the third clutch C3 is used in parallel with the first clutch C1 is to secure the function of the engine brake. As shown in Table 1, the third clutch C3 is Engine brakes are available at the R and L stages.

L단을 보면, D1 변속단의 상태에서 제1클러치(C1) 대신 제3클러치(C3)가 입력축의 회전력을 제1선기어(S1)에 전달하도록 하고 있는바, 이와 같은 제3클러치(C3)와 제1선기어(S1) 사이에는 원웨이클러치(F1)가 없으므로 엔진브레이크가 가능한 것이다.In the L stage, the third clutch C3 transmits the rotational force of the input shaft to the first sun gear S1 in place of the first clutch C1 in the state of the D1 shift stage, such a third clutch C3. There is no one-way clutch F1 between the first sun gear S1 and the engine brake is possible.

아울러, 상기 표 1을 보면 상기 원웨이클러치(F1)를 사용하고 있는 D1 변속단 이외에는 모두 출력축으로부터 입력축으로의 동력전달이 가능한 상태를 취하여 엔진브레이크가 가능함을 알 수 있다.In addition, it can be seen from Table 1 that the engine brake is possible by taking a state in which power transmission from the output shaft to the input shaft is possible except for the D1 shift stage using the one-way clutch F1.

이상과 같이 본 발명에 의하면, 무단변속기에서 하드웨어적으로 변속비를 원하는 시간 내에 급격히 낮추어 실질적인 킥다운 기능을 구현할 수 있도록 함으로써, 운전자가 원하는 가속감을 얻을 수 있도록 하여 상품성을 크게 향상시킨다.As described above, according to the present invention, the speed ratio can be drastically lowered within a desired time in a continuously variable transmission to implement a practical kickdown function, so that the driver can obtain a desired feeling of acceleration and greatly improve the merchandise.

Claims (2)

서로 크고 작은 직경을 가진 큰직경부와 작은직경부가 동심축을 이루며 일체로 형성된 단차피니언과;A stepped pinion integrally formed with a large diameter portion and a small diameter portion having a large diameter and a small diameter concentric with each other; 상기 단차피니언에 치합되고 출력축에 연결된 링기어와;A ring gear meshed with the stepped pinion and connected to the output shaft; 상기 단차피니언의 큰직경부에 치합되는 제1선기어와;A first sun gear meshed with a large diameter portion of the stepped pinion; 상기 단차피니언의 작은직경부에 치합되는 제2선기어와;A second sun gear meshed with a small diameter portion of the stepped pinion; 상기 제1선기어와 입력축의 동력전달상태를 전환하는 제1클러치 및 제3클러치와;A first clutch and a third clutch for switching a power transmission state between the first sun gear and the input shaft; 상기 제1클러치와 제1선기어 사이에 설치된 원웨이클러치와;A one-way clutch installed between the first clutch and the first sun gear; 상기 제2선기어와 입력축의 동력전달상태를 전환하는 제2클러치와;A second clutch for switching a power transmission state between the second sun gear and the input shaft; 상기 단차피니언의 캐리어를 고정하는 제1브레이크와;A first brake fixing the carrier of the stepped pinion; 상기 단차피니언의 캐리어를 상기 링기어에 연결시키는 상태를 전환하는 제4클러치;A fourth clutch for switching a state of connecting the carrier of the stepped pinion to the ring gear; 를 포함하여 구성된 것을 특징으로 하는 무단변속기용 유성기어장치 및 작동기구.Planetary gear device and actuating mechanism for continuously variable transmission, characterized in that comprises a. 제1항에 있어서,The method of claim 1, 상기 원웨이클러치는 상기 입력축의 동력을 제1선기어로 전달하는 상태로 설치된 것The one-way clutch is installed in a state of transmitting power of the input shaft to the first sun gear. 을 특징으로 하는 무단변속기용 유성기어장치 및 작동기구.Planetary gear device and actuating mechanism for continuously variable transmission.
KR10-2003-0046676A 2003-07-10 2003-07-10 planetary gear set for a continuously variable transmission KR100535086B1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113803425A (en) * 2021-08-27 2021-12-17 江麓机电集团有限公司 Large-step-ratio planetary speed change mechanism

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113803425A (en) * 2021-08-27 2021-12-17 江麓机电集团有限公司 Large-step-ratio planetary speed change mechanism
CN113803425B (en) * 2021-08-27 2023-12-19 江麓机电集团有限公司 Planetary speed change mechanism with large order ratio

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