KR100302754B1 - Power train of automatic transmission for vehicle - Google Patents

Power train of automatic transmission for vehicle Download PDF

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Publication number
KR100302754B1
KR100302754B1 KR1019950043372A KR19950043372A KR100302754B1 KR 100302754 B1 KR100302754 B1 KR 100302754B1 KR 1019950043372 A KR1019950043372 A KR 1019950043372A KR 19950043372 A KR19950043372 A KR 19950043372A KR 100302754 B1 KR100302754 B1 KR 100302754B1
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KR
South Korea
Prior art keywords
planetary gear
gear set
sun gear
gear
double pinion
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Application number
KR1019950043372A
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Korean (ko)
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KR970027940A (en
Inventor
박종술
Original Assignee
이계안
현대자동차주식회사
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Application filed by 이계안, 현대자동차주식회사 filed Critical 이계안
Priority to KR1019950043372A priority Critical patent/KR100302754B1/en
Priority to US08/752,441 priority patent/US5810689A/en
Priority to CA002191028A priority patent/CA2191028A1/en
Priority to EP96118775A priority patent/EP0775846B1/en
Priority to IN2028CA1996 priority patent/IN190503B/en
Priority to DE69609291T priority patent/DE69609291T2/en
Priority to AU71934/96A priority patent/AU715365B2/en
Priority to JP8329211A priority patent/JPH09291990A/en
Publication of KR970027940A publication Critical patent/KR970027940A/en
Application granted granted Critical
Publication of KR100302754B1 publication Critical patent/KR100302754B1/en

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Classifications

    • 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
    • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02039—Gearboxes for particular applications
    • F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
    • F16H2057/02047—Automatic transmissions
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H2057/087—Arrangement and support of friction devices in planetary gearings, e.g. support of clutch drums, stacked arrangements of friction devices
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means

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

Abstract

PURPOSE: A power train of an automatic transmission for a vehicle is provided to compact the structure of a transmission and to minimize the loss of power at a highest speed range. CONSTITUTION: A power train includes a first double pinion planetary gear set(6) having a sun gear(4) directly connected with an input shaft(2), a second double pinion planetary gear set(12) having a ring gear(10) directly connected to a ring gear(8) of the first planetary gear set. A carrier(14) of the first planetary gear set is connected with a sun gear(18) of the second planetary gear set via a first friction element(16). A carrier(20) of the second planetary gear set is connected with a transfer driver gear(22). A second friction element(24) is installed between the ring gear of the second planetary gear set and a transmission housing(26). A third friction element(28) fixes the sun gear of the second planetary gear set. A fourth friction element(30) selectively transfer power to the ring gears. A fifth friction element(34) is installed on a sun gear shaft(32) to transfer the power of the input shaft to the sun gear of the second planetary gear set in the reverse range. One of three elements of the planetary gear set is selected as an input and another element is selected as a reaction force element depending on the operation of the friction elements.

Description

차량용 자동변속기의 파워 트레인Power train of car automatic transmission

제1도는 본 발명의 제1실시예에 따른 변속장치의 파워 트레인을 나타내는 도면.1 shows a power train of a transmission according to a first embodiment of the present invention.

제2도는 본 발명에 의한 변속장치의 변속단별 마찰요소 작동표.2 is a frictional element operation table for each shift stage of the transmission according to the present invention.

제3도는 본 발명의 제2실시예에 따른 변속장치의 파워 트레인을 나타내는 도면이다.3 is a view showing a power train of a transmission according to a second embodiment of the present invention.

본 발명은 차량용 자동변속장치에 관한 것으로서, 보다 상세하게는 2개의 더블 피니온 유성기어셋트가 조합된 복합 유성기어장치를 사용하는 변속기에서 최고 변속단에서 유성기어장치의 모든 요소가 출력 속도 이하에서 회전할 수 있도록 하여 비작용 요소가 회전하므로서 발생하는 동력 손실을 최소화할 수 있는 자동변속기의 파워 트레인에 관한 것이다.BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an automatic transmission for a vehicle, and more particularly, in the transmission using a composite planetary gear unit in which two double pinion planetary gear sets are combined, all elements of the planetary gear unit at the top gear stage are below the output speed. The present invention relates to a power train of an automatic transmission that can be rotated to minimize power loss caused by rotation of non-active elements.

일반적으로 차량용 자동변속장치는, 차량의 주행속도와 부하의 변동에 따라 변속비를 자동적으로 제어하는 트랜스밋션 제어 유닛을 구비하고 있다.BACKGROUND ART In general, an automatic transmission for a vehicle includes a transmission control unit that automatically controls a transmission ratio in accordance with a change in a traveling speed and a load of a vehicle.

상기한 트랜스밋션 제어 유닛은 기어 트레인에 설치된 다수개의 마찰요소들을 작동 또는 비작동 상태로 제어하여 유성기어의 3요소(선기어, 링기어, 유성 캐리어)중 어느 요소를 입력요소로 선택하고, 어느 요소를 반력요소로 선택하여 출력단 회전수를 조절하게 된다.The transmission control unit controls a plurality of friction elements installed in the gear train in an active or non-operating state to select which of the three elements of the planetary gear (sun gear, ring gear, planet carrier) as an input element, and which element Select as the reaction force element to adjust the output speed.

실질적으로 전진 4속과 후진 1속의 변속비를 출력할 수 있는 파워 트레인을 설계하기 위해서는 1개의 복합 유성기어장치와, 최소한 5개의 마찰요소를 사용하여야 한다.In order to design a power train that can output a gear ratio of four forward speeds and one reverse speed, one compound planetary gear unit and at least five friction elements must be used.

이러한 마찰요소들 중에서 클러치 요소의 회전 반경은 입력축과 연결되기 위하여 출력요소의 회전 반경보다 작아야 하며, 또 반력요소의 회전 반경보다도 작아야 하는 구조적 제약 조건을 갖는다.Among these friction elements, the rotation radius of the clutch element must be smaller than the rotation radius of the output element in order to be connected to the input shaft, and has a structural constraint that the rotation radius of the reaction element must be smaller than the rotation radius of the reaction force element.

복합 유성기어 자치를 사용하는 변속장치는 어느 하나의 유성기어셋트의 요소들이 다른 하나의 유성기어셋트의 요소들과 결합되는 구조를 갖는다.The transmission using the composite planetary gear autonomous has a structure in which elements of one planetary gearset are combined with elements of another planetary gearset.

그러나 이러한 구조의 복합 유성기어장치를 사용하는 파워 트레인에 있어서, 최고 변속단에서 입력보다 빠른 속도로 회전하는 요소가 있으므로 동력 손실이 있으며, 복합 유성기어장치에서 어느 하나의 유성기어셋트에서는 비작동 요소에서 슬립이 발생하게 되므로 그에 따른 동력 손실이 발생하여 연비 측면에서 나쁜 영향을 주고 있다.However, in the power train using the composite planetary gear system of such a structure, there is a power loss because there is an element that rotates at a higher speed than the input at the top shift stage, and the non-operating element in any one planetary gear set in the composite planetary gear system. Since the slip occurs in the power loss caused by it has a bad effect in terms of fuel economy.

본 발명은 상기한 바와 같은 종래 기술의 문제점을 해소하기 위하여 발명된 것으로서, 본 발명의 목적은 변속기를 컴팩트하게 제공할 수 있으며, 특히 최고 변속단에서 동력 손실을 최소화할 수 있는 차량용 자동변속기의 파워 트레인을 제공하는데 있다.The present invention has been invented to solve the problems of the prior art as described above, an object of the present invention is to provide a compact transmission, in particular the power of the automatic transmission for a vehicle that can minimize the power loss at the highest transmission stage To provide the train.

상기한 바와 같은 본 발명의 목적을 실현하기 위하여, 토오크 컨버터를 통하여 엔진의 회전 동력을 전달받는 입력축과, 상기한 입력축과 직결되는 선기어를 보유하고 있으며 클러치 수단을 통하여 입력축의 회전 동력을 전달받는 링기어를 보유하는 첫번째 더블 피니온 유성기어셋트와, 상기한 링기어와 직결되는 링기어를 보유하고 있으며 첫번째 더블 피니온 유성기어셋트의 유성 캐리어와 클러치 수단을 통하여 연결되는 선기어를 보유하는 두번째 더블 피니온 유성기어셋트와, 상기한 첫번째 및 두번째 링기어들을 반력요소로 선택하는 브레이크 수단과, 상기한 두번째 더블 피니온 유성기어셋트의 선기어를 반력요소로 선택하는 또 다른 브레이크 수단을 포함하는 차량용 자동변속기의 파워 트레인을 제공한다.In order to realize the object of the present invention as described above, a ring having an input shaft to receive the rotational power of the engine through the torque converter, and a sun gear directly connected to the input shaft and a transmission of the rotational power of the input shaft through the clutch means The first double pinion planetary gearset with gears, and the second double pinion with ring gears directly connected to the above-mentioned ring gear, and the sun gear connected via the planetary carrier and clutch means of the first double pinion planetary gearset. A vehicle automatic transmission comprising an on planetary gear set, brake means for selecting the first and second ring gears as a reaction element, and another brake means for selecting the sun gear of the second double pinion planetary gear set as a reaction element. To provide a power train.

상기한 첫번째 더블 피니온 유성기어셋트의 선기어와 두번째 더블 피니온 유성기어셋트의 선기어는 클러치 수단으로 연결되어 입력축의 회전 동력이 후진 레인지에서 두번째 더블 피니온 유성기어셋트의 선기어로 전달될 수 있는 차량용 자동변속기의 파워 트레인을 제공한다.The sun gear of the first double pinion planetary gear set and the sun gear of the second double pinion planetary gear set are connected by clutch means so that the rotational power of the input shaft can be transmitted to the sun gear of the second double pinion planetary gear set in the reverse range. Provides power train for automatic transmission.

상기한 입력축과 첫번째 더블 피니온 유성기어셋트의 링기어는 클러치 수단에 의해 연결되는 차량용 자동변속기의 파워 트레인을 제공한다.The input shaft and the ring gear of the first double pinion planetary gear set provide the power train of the vehicle automatic transmission connected by the clutch means.

또한 상기한 클러치 수단은 첫번째 더블 피니온 유성기어셋트의 유성 캐리어와 링기어 사이에 설치되는 차량용 자동변속기의 파워 트레인을 제공한다.The clutch means also provides a power train of an automatic transmission for a vehicle installed between the planetary carrier and the ring gear of the first double pinion planetary gear set.

이하 본 발명의 바람직한 실시예를 첨부한 도면을 참조하여 더욱 상세히 설명한다.Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings.

제1도는 본 발명의 제1실시예에 따른 변속장치의 파워 트레인을 나타내는 도면으로서, 엔진(E)으로부터 토오크 컨버터(T)를 통하여 변속부의 입력축(2)으로 회전 동력을 전달할 수 있도록 구성하고 있다.1 is a view showing a power train of a transmission apparatus according to a first embodiment of the present invention, and is configured to transmit rotational power from the engine E to the input shaft 2 of the transmission portion through the torque converter T. .

상기한 입력축(2)의 일측으로는 이 축과 직결된 선기어(4)를 보유하는 첫번째 더블 피니온 유성기어셋트(6)와, 이 유성기어셋트의 링기어(8)와 직결되는 링기어(10)를 보유하는 두번째 더블 피니온 유성기어셋트(12)로 이루어지는 복합 유성기어장치가 배치되어 있다.One side of the input shaft 2 has a first double pinion planetary gear set 6 having a sun gear 4 directly connected to the shaft, and a ring gear directly connected to the ring gear 8 of the planetary gear set. There is arranged a composite planetary gear device consisting of a second double pinion planetary gear set 12 having 10).

상기한 첫번째 더블 피니온 유성기어셋트(6)의 유성 캐리어(14)는 클러치 수단으로 제1마찰요소(16)를 통하여 두번째 더블 피니온 유성기어셋트(12)의 선기어(18)와 연결되어 동력을 전달할 수 있도록 구성된다.The planetary carrier 14 of the first double pinion planetary gearset 6 is connected to the sun gear 18 of the second double pinion planetary gearset 12 via a first friction element 16 by clutch means. It is configured to deliver.

상기한 두번째 더블 피니온 유성기어셋트(12)의 유성 캐리어(20)는 트랜스퍼 드라이브 기어(22)와 연결되어 출력수단으로 사용될 수 있는 구성을 갖는다.The planetary carrier 20 of the second double pinion planetary gear set 12 is connected to the transfer drive gear 22 and has a configuration that can be used as an output means.

상기한 두번째 더블 피니온 유성기어셋트(12)의 링기어(10)는 상기한 제1마찰요소(16)가 작동시 반력요소로 선택될 수 있도록 브레이크 수단인 제2마찰요소(24)를 변속기 하우징(26)과의 사이에 설치하고 있다.The ring gear 10 of the second double pinion planetary gear set 12 transmits the second friction element 24 as brake means so that the first friction element 16 can be selected as a reaction force element during operation. It is provided between the housing 26.

그리고 선기어(18)가 상기한 클러치 수단이 작용할 때 반력요소로 작용할 수 있도록 브레이크 수단인 제3마찰요소(28)에 의해 고정될 수 있도록 하고 있다.And the sun gear 18 is to be fixed by the third friction element 28, which is a brake means to act as a reaction force element when the clutch means described above.

상기한 입력축(2)과 상기한 첫번째 및 두번째 더블 피니온 유성기어셋트(6,12)의 링기어(8)(10)들은 클러치 수단인 제4마찰요소(30)에 의해 선택적으로 동력을 전달받을 수 있도록 구성된다.The input shaft 2 and the ring gears 8 and 10 of the first and second double pinion planetary gear sets 6 and 12 are selectively transmitted by a fourth friction element 30 which is a clutch means. It is configured to receive.

한편 후진 레인지(R)에서 클러치 수단으로 입력축(2)의 동력을 두번째 더블 피니온 유성기어셋트(12)의 선기어(18)로 전달하기 위하여 선기어축(32)에 제5마찰요소(34)를 설치하고 있다.On the other hand, the fifth friction element 34 is applied to the sun gear shaft 32 in order to transmit the power of the input shaft 2 to the sun gear 18 of the second double pinion planetary gear set 12 by the clutch means in the reverse range R. I install it.

이와 같이 이루어지는 본 발명의 변속장치는, 트랜스밋션 제어 유닛에 의해 작동과 비작동이 선택되는 마찰요소들의 작동 유무에 따라 유성기어셋트의 3요소중 어느 하나의 요소를 입력으로, 그리고 다른 하나의 요소를 반력요소로 선택하여 다음과 같은 전진 4속과 후진 1속의 변속비를 출력하게 된다.According to the present invention, the transmission includes the one of the three elements of the planetary gear set as an input and the other element depending on whether or not the friction elements are selected to be operated or deactivated by the transmission control unit. Is selected as the reaction force element to output the following transmission ratios of 4 forward speed and 1 reverse speed.

트랜스밋션 제어 유닛에 의해 작동과 비작동이 선택되는 마찰요소들에 관련하는 레인지별 작동표가 제2도에 나타나 있다.The range-specific operating table relating to the friction elements for which operation and non-operation are selected by the transmission control unit is shown in FIG.

전진(D) 레인지로 셀렉터 레버가 선택되면, 트랜스밋션 제어 유닛은 파워 트레인이 1속의 변속비를 출력할 수 잇도록 클러치 수단으로 제1마찰요소(16)를 작동시키고, 브레이크 수단으로 제2마찰요소(24)를 작동시키게 된다.When the selector lever is selected in the forward (D) range, the transmission control unit operates the first friction element 16 by the clutch means so that the power train can output the speed ratio of 1 speed, and the second friction element by the brake means. (24) will be activated.

이러한 제어에 의해 입력축(2)의 회전 동력은 직결된 첫번째 더블 피니온 유성기어셋트(6)의 선기어(4)로 전달되면서 유성 캐리어(14)를 입력과 반대방향으로 회전시키게 된다.By this control, the rotational power of the input shaft 2 is transmitted to the sun gear 4 of the first double pinion planetary gear set 6 directly connected to rotate the planet carrier 14 in the opposite direction to the input.

이러한 유성 캐리어(14)의 동력은 제1마찰요소(16)를 통하여 두번째 더블 피니온 유성기어셋트(12)의 선기어(18)로 전달되는데, 이때 링기어(10)가 반력요소로 작용하고 있으므로 유성 캐리어(20)는 입력축(2)과 동일한 방향으로 회전하면서 본 실시예가 감속할 수 있는 가장 큰 감속비인 1속의 변속비를 트랜스퍼 드라이브 기어(22)로 전달하게 된다.The power of the planet carrier 14 is transmitted to the sun gear 18 of the second double pinion planetary gear set 12 through the first friction element 16, since the ring gear 10 acts as a reaction force element. The planet carrier 20 transmits the gear ratio of 1 speed, which is the largest reduction ratio that the present embodiment can decelerate while rotating in the same direction as the input shaft 2, to the transfer drive gear 22.

이러한 1속 제어 상태에서 차속이 증가하게 되면, 트랜스밋션 제어 유닛은 클러치 수단을 그대로 작동시키는 상태에서 브레이크 수단을 제2마찰요소에서 제3마찰요소(28)로 바꾸게 된다.When the vehicle speed increases in such a first speed control state, the transmission control unit changes the brake means from the second friction element to the third friction element 28 while the clutch means is operated as it is.

따라서 입력축(2)의 동력 전달은 선기어(4)로 전달되지만, 첫번째 및 두번째 더블 피니온 유성기어셋트(12)의 링기어(8)(10)가 회전하는 상태이므로 유성 캐리어(20)는 링기어의 회전분 만큼 더 회전속도가 빨라지면서 2속의 변속비를 트랜스퍼 드라이브 기어(22)로 전달하게 된다.Therefore, power transmission of the input shaft (2) is transmitted to the sun gear (4), but since the ring gear (8) 10 of the first and second double pinion planetary gear set 12 is rotated, the planet carrier (20) is a ring As the rotation speed is increased by the rotational speed of the gear, the speed ratio of the second speed is transmitted to the transfer drive gear 22.

이러한 2속 제어 상태에서 차속이 증가하게 되면, 트랜스밋션 제어 유닛은 모든 브레이크 수단의 작용을 중단시키면서 새로이 클러치 수단으로 제4마찰요소(30)를 작동시키게 된다.When the vehicle speed is increased in this two-speed control state, the transmission control unit newly operates the fourth friction element 30 by the clutch means while stopping the action of all the brake means.

따라서 복합 유성기어장치는 2개의 입력요소를 갖게 되므로 입력과 출력이 동일한 1:1의 변속비를 출력하게 된다.Therefore, the compound planetary gear device has two input elements, and thus outputs a 1: 1 ratio of the same input and output.

이러한 3속 제어 상태에서 차속이 더욱 빨라지게 되면, 트랜스밋션 제어 유닛은 1,2,3속에서 작용하던 제1마찰요소(15)의 작동을 중단시키면서 브레이크 수단으로 제3마찰요소(28)를 작동시키게 된다.When the vehicle speed becomes faster in this three-speed control state, the transmission control unit stops the operation of the first friction element 15 acting at the first, second and third speeds, and applies the third friction element 28 to the brake means. It works.

따라서 두번째 더블 피니온 유성기어셋트(12)의 선기어(18)가 고정되므로 링기어(10)로 입력되는 입력축(2)의 회전 동력은 입력보다 빠르게 회전하는 4속의 변속비를 유성 캐리어(20)를 통하여 트랜스퍼 드라이브 기어(22)로 전달하게 된다.Therefore, since the sun gear 18 of the second double pinion planetary gear set 12 is fixed, the rotational power of the input shaft 2 input to the ring gear 10 has a four-speed transmission ratio that rotates faster than the input, thus providing the planetary carrier 20. It is transmitted to the transfer drive gear 22 through.

이때 첫번째 더블 피니온 유성기어셋트(6)도 입력요소가 2개가 되기 때문에 셋트 전체가 일체로 회전하는 상태가 되므로 비작동 요소에 의한 마찰 손실을 줄일 수 있다.At this time, since the first double pinion planetary gear set 6 also has two input elements, the entire set is rotated integrally, thereby reducing frictional losses caused by non-operating elements.

한편 셀렉터 레버가 후진(R) 레인지로 선택되면, 트랜스밋션 제어 유닛은 클러치 수단으로 제5마찰요소(34)를 작동시키면서 브레이크 수단으로 제2마찰요소(24)를 작동시키게 된다.On the other hand, when the selector lever is selected as the reverse (R) range, the transmission control unit operates the second friction element 24 by the brake means while operating the fifth friction element 34 by the clutch means.

이러한 제어에 의해 입력축(2)의 회전 동력은 두번째 더블 피니온 유성기어셋트(12)의 선기어(18)로 전달되는데, 이때 링기어(10)가 고정된 상태이므로 유성 캐리어(20)는 입력과 반대방향으로 회전하면서 후진 감속비를 트랜스퍼 드라이브 기어(22)로 전달하게 된다.By this control, the rotational power of the input shaft 2 is transmitted to the sun gear 18 of the second double pinion planetary gear set 12. In this case, since the ring gear 10 is fixed, the planet carrier 20 is connected to the input. The reverse gear ratio is transmitted to the transfer drive gear 22 while rotating in the opposite direction.

이상 설명한 바와 같이 본 실시예에 의한 변속장치는, 특히 4속단에서 첫번째 더블 피니온 유성기어셋트를 일체로 회전시킬 수 있도록 하고 있기 때문에 이곳에서 비작동 요소가 슬립을 하지 않게 되어 마찰 손실을 줄일 수 있다.As described above, the transmission according to the present embodiment, in particular, allows the first double pinion planetary gear set to be integrally rotated at the fourth speed, so that non-operating elements do not slip here, thereby reducing frictional losses. have.

그리고 부변속단을 사용하지 않고도 전진 4속과 후진 1속의 변속비를 출력할 수 있으므로 변속기를 컴팩트하게 설계할 수 있는 이점도 있다.In addition, since the transmission ratio of 4 forward speeds and 1 reverse speed can be output without using the subshift stage, there is an advantage in that the transmission can be compactly designed.

제3도는 본 발명의 다른 실시예에 의한 파워트레인을 나타내는 도면으로서, 특히 다른 점은 4속에서 클러치 수단으로 작용하는 제4마찰요소(30)를 첫번째 더블 피니온 유성기어셋트(6)의 유성 캐리어(14)와 링기어(8) 사이에 연결하여 이 유성기어셋트를 일체로 회전하도록 하는 것이다.3 is a view showing a power train according to another embodiment of the present invention, in particular, the fourth friction element 30 acting as a clutch means at four speeds is the planetary of the first double pinion planetary gear set 6. It is connected between the carrier 14 and the ring gear 8 to rotate the planetary gear set integrally.

따라서 상기한 실시예와 동일하게 4속단에서 비작동 요소의 슬립에 따른 동력 손실을 줄일 수 있다.Therefore, the power loss due to the slip of the non-operating element can be reduced in the fourth speed as in the above embodiment.

Claims (2)

제1선기어, 제1캐리어, 제1링기어로 구성되어 상기 제1선기어는 입력축과 직결되는 제1더블 피니언 유성기어셋트; 제2선기어, 제2캐리어, 제2링기어로 구성되어, 상기 제2링기어는 상기 제1링 기어와 직결되고, 제2캐리어가 상시 출력요소로 작용하는 제2더블 피니언 유성기어 셋트를 보유하는 자동변속기의 파워 트레인으로서, 상기 제2링기어를 가변적으로 고정하는 제1브레이크 및 상기 제2선기어를 가변적으로 고정하는 제2브레이크를 구비하고, 상기 제1캐리어와 상기 제2선기어를 가변 연결하는 제1클러치, 상기 입력축과 상기 제1링기어를 가변 연결하는 제2클러치, 및 상기 제1선기어와 상기 제2선기어를 가변 연결하는 제3클러치를 구비하는 것을 특징으로 하는 차량용 자동변속기의 파워 트레인.A first double pinion planetary gear set including a first sun gear, a first carrier, and a first ring gear, the first sun gear being directly connected to an input shaft; A second sun gear, a second carrier, and a second ring gear, the second ring gear is directly connected to the first ring gear, and has a second double pinion planetary gear set in which the second carrier acts as an output element at all times. A power train of an automatic transmission, comprising: a first brake for variably fixing the second ring gear and a second brake for variably fixing the second sun gear, and variably connecting the first carrier and the second sun gear. A first clutch, a second clutch for variably connecting the input shaft and the first ring gear, and a third clutch for variably connecting the first sun gear and the second sun gear. Train. 제1선기어, 제1캐리어, 제1링기어로 구성되어 상기 제1선기어는 입력축과 직결되는 제1더블 피니언 유성기어셋트; 제2선기어, 제2캐리어, 제2링기어로 구성되어, 상기 제2링기어는 상기 제1링기어와 직결되고, 제2캐리어가 상시 출력요소로 작용하는 제2더블 피니언 유성기어 셋트를 보유하는 자동변속기의 파워 트레인으로서, 상기 제2링기어를 가변적으로 고정하는 제1브레이크 및 상기 제2선기어를 가변적으로 고정하는 제2브레이크를 구비하고, 상기 제1캐리어와 상기 제2선기어를 가변 연결하는 제1클러치, 상기 제1링기어와 제1캐리어를 가변 연결하는 제2클러치, 및 상기 제1선기어와 상기 제2선기어를 가변 연결하는 제3클러치를 구비하는 것을 특징으로 하는 차량용 자동변속기의 파워 트레인.A first double pinion planetary gear set including a first sun gear, a first carrier, and a first ring gear, the first sun gear being directly connected to an input shaft; A second sun gear, a second carrier, and a second ring gear, the second ring gear is directly connected to the first ring gear, and has a second double pinion planetary gear set in which the second carrier acts as an output element at all times. A power train of an automatic transmission, comprising: a first brake for variably fixing the second ring gear and a second brake for variably fixing the second sun gear, and variably connecting the first carrier and the second sun gear. A first clutch, a second clutch for variably connecting the first ring gear and the first carrier, and a third clutch for variably connecting the first sun gear and the second sun gear. Power train.
KR1019950043372A 1995-11-23 1995-11-23 Power train of automatic transmission for vehicle KR100302754B1 (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
KR1019950043372A KR100302754B1 (en) 1995-11-23 1995-11-23 Power train of automatic transmission for vehicle
US08/752,441 US5810689A (en) 1995-11-23 1996-11-14 Transmission planetary gearing
CA002191028A CA2191028A1 (en) 1995-11-23 1996-11-22 Transmission planetary gearing
EP96118775A EP0775846B1 (en) 1995-11-23 1996-11-22 Transmission planetary gearing
IN2028CA1996 IN190503B (en) 1995-11-23 1996-11-22
DE69609291T DE69609291T2 (en) 1995-11-23 1996-11-22 Gears with planetary gear sets
AU71934/96A AU715365B2 (en) 1995-11-23 1996-11-22 Transmission planetary gearing
JP8329211A JPH09291990A (en) 1995-11-23 1996-11-25 Transmission device

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Application Number Priority Date Filing Date Title
KR1019950043372A KR100302754B1 (en) 1995-11-23 1995-11-23 Power train of automatic transmission for vehicle

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KR970027940A KR970027940A (en) 1997-06-24
KR100302754B1 true KR100302754B1 (en) 2001-12-28

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