KR100757251B1 - Power transmission structure for cars by planetary gear and clutch - Google Patents

Power transmission structure for cars by planetary gear and clutch Download PDF

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Publication number
KR100757251B1
KR100757251B1 KR1020060078645A KR20060078645A KR100757251B1 KR 100757251 B1 KR100757251 B1 KR 100757251B1 KR 1020060078645 A KR1020060078645 A KR 1020060078645A KR 20060078645 A KR20060078645 A KR 20060078645A KR 100757251 B1 KR100757251 B1 KR 100757251B1
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South Korea
Prior art keywords
clutch
gear
planetary gear
transmission
power
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KR1020060078645A
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Korean (ko)
Inventor
이경훈
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현대자동차주식회사
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/02—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of clutch
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
    • B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing

Abstract

A power transmission structure for a vehicle using a planetary gear and a clutch is provided to reduce power applied to the clutch and to reduce capacity and a size of the clutch by connecting a crank shaft of an engine, an input shaft, and a clutch disk with a sun gear, a carrier, and a ring gear respectively. A crank shaft(12) of an engine(10), an input shaft(42) of a transmission(40), and a clutch disk(24) are connected to a simple planetary gear(30). The simple planetary gear contains a sun gear(32), a pinion gear(36), a ring gear(34), and a carrier(38). The sun gear is connected to the crank shaft. The pinion gear is tooth-geared on an outer periphery of the sun gear to be rotated. The ring gear is tooth-engaged to the outside of the pinion gear and connected to the clutch disk. The carrier is coupled to the ring gear and connected to the input shaft. The simple planetary gear is placed in the transmission, and installed with an oil seal(52) and a bearing(54) supporting the rotation of the crank shaft.

Description

유성기어와 클러치를 이용한 차량의 동력전달구조{Power Transmission Structure for Cars by Planetary Gear and Clutch}Power Transmission Structure for Cars by Planetary Gear and Clutch}

도 1은 종래 엔진에서 변속기로 동력전달 과정을 도시한 도면,1 is a view showing a power transmission process from a conventional engine to a transmission;

도 2는 종래 동력전달 과정에서 열손실이 없다는 가정하에서 클러치를 통해 전달되는 파워를 표시한 도면,2 is a view showing the power transmitted through the clutch under the assumption that there is no heat loss in the conventional power transmission process,

도 3은 본 발명에 따른 동력전달구조를 나타낸 도면,3 is a view showing a power transmission structure according to the present invention;

도 4는 도 3에서 클러치를 발로 밟고 변속이 이루어지는 경우 유성기어의 회전수를 나타내는 그래프,4 is a graph showing the number of revolutions of the planetary gear when shifting is performed by stepping on the clutch in FIG. 3;

도 5는 도 3에서 클러치에서 발을 뗀 경우 유성기어의 회전수를 나타내는 그래프,5 is a graph showing the rotational speed of the planetary gear when the foot is removed from the clutch in FIG.

도 6은 도 3에서 열손실이 없다는 가정하에서 클러치와 유성기어를 통해 전달되는 파워를 표시한 도면.6 is a view showing the power transmitted through the clutch and the planetary gear under the assumption that there is no heat loss in FIG.

<도면의 주요부분에 대한 부호의 설명><Description of the symbols for the main parts of the drawings>

10: 엔진 12: 크랭크축10: engine 12: crankshaft

20: 클러치 22: 클러치 커버20: clutch 22: clutch cover

24: 클러치 디스크 30: 단순유성기어24: Clutch Disc 30: Simple Planetary Gear

32: 선기어 34: 링기어32: sun gear 34: ring gear

36: 피니언기어 38: 캐리어36: pinion gear 38: carrier

40: 변속기 42: 입력축40: transmission 42: input shaft

44: 출력축 45,46,47: 동기장치44: output shaft 45,46,47: synchronizer

48: 차동축48: differential shaft

본 발명은 유성기어와 클러치를 이용한 차량의 동력전달구조에 관한 것으로서, 더욱 상세하게는 엔진의 크랭크축, 입력축, 클러치 디스크를 단순유성기어의 선기어, 캐리어, 링기어로 각각 연결하여 클러치의 마찰에 의해 동력이 전달될 때 클러치가 담당하는 파워를 줄일 수 있는 동력전달구조에 관한 것이다.The present invention relates to a power transmission structure of a vehicle using a planetary gear and a clutch. More specifically, the engine crank shaft, the input shaft, and the clutch disk are connected to the sun gear, the carrier, and the ring gear of the simple planetary gear to prevent friction of the clutch. It relates to a power transmission structure that can reduce the power that the clutch is in charge when power is transmitted by.

일반적으로 차량의 경우 엔진에서 발생한 구동력은 변속기에서 주행 상태에 따라 적절한 토크로 변속된 다음 추진축을 통해 구동바퀴로 전달되어 주행이 이루어짐으로써 동력전달이 이루어진다.In general, in the case of a vehicle, the driving force generated by the engine is shifted to an appropriate torque in accordance with the driving state in the transmission, and then transmitted to the driving wheel through the propulsion shaft, thereby driving the power.

종래 기술에 따른 차량의 동력전달은 도 1에 도시된 바와 같이, 엔진(1)의 구동력을 단속하는 클러치(2)와, 차실에 장착된 변속레버(미도시)의 조작에 따라 상기 클러치(2)를 통해 전달받은 엔진(1)의 구동력을 증감시키고, 후진변속 작용을 행하는 변속기(3)와, 상기 변속기(3)로부터 출력된 동력을 전달받아 좌우 구동바퀴에 각각 분배하는 차동장치(미도시) 등으로 이루어진다.Power transmission of the vehicle according to the prior art, as shown in Figure 1, the clutch 2 for controlling the driving force of the engine 1, and the clutch (2) in accordance with the operation of the shift lever (not shown) mounted to the vehicle cabin Differential device for increasing and decreasing the driving force of the engine 1 received through the transmission, and transmitting the power output from the transmission 3 and the power output from the transmission 3 to each of the left and right driving wheels (not shown). ) And so on.

상기 변속기(3)는 엔진(1)의 구동력을 전달받아 회전되는 입력축(4)과, 상기 입력축(4)과 평행하게 배치되고 차동장치로 변속된 엔진(1)의 구동력을 전달하는 출력축(5)과, 상기 입력축(4)과 출력축(5) 사이에 배치되어 변속시 상기 입력축(4)과 출력축(5)을 동기화시킴과 아울러 입력축(4)과 출력축(5)을 일정 기어비로 연결하는 동기장치(6,7,8)를 포함하여 구성된다.The transmission 3 has an input shaft 4 which is rotated by receiving the driving force of the engine 1 and an output shaft 5 which is disposed in parallel with the input shaft 4 and transmits the driving force of the engine 1 shifted by a differential device. And the input shaft 4 and the output shaft 5 to synchronize the input shaft 4 and the output shaft 5 at the time of shifting, and to connect the input shaft 4 and the output shaft 5 with a constant gear ratio. It comprises a device (6, 7, 8).

상기 클러치(2)는 클러치 커버(2a)와 클러치 디스크(2b)로 이루어지며, 클러치 디스크(2b)와 변속기(3)의 입력축(4)은 스플라인 결합하여 같이 회전한다.The clutch 2 consists of a clutch cover 2a and a clutch disc 2b, and the clutch disc 2b and the input shaft 4 of the transmission 3 are splined together to rotate together.

그리고 상기 변속기(3)의 입력축(4)에는 오일의 누유를 방지하는 오일 시일(9a)과, 회전을 지지하는 베어링(9b)이 구비된다.The input shaft 4 of the transmission 3 is provided with an oil seal 9a for preventing oil leakage and a bearing 9b for supporting rotation.

도 1에서 기호 Te는 엔진(1) 토크, We는 엔진(1) 회전수(클러치 커버(2a)의 회전수), Tt는 클러치(2) 연결시 변속기(3)로부터 엔진(1)에 작용하는 부하(≤클러치 용량(Cc)), Wt는 변속기 입력축(4)의 회전수(클러치 디스크(2b)의 회전수)를 나타낸다.In Fig. 1, the symbol Te denotes the engine 1 torque, We the engine 1 rotation speed (the rotation speed of the clutch cover 2a), and Tt acts on the engine 1 from the transmission 3 when the clutch 2 is connected. The load (≤ clutch capacity Cc) and Wt denote the rotational speed of the transmission input shaft 4 (the rotational speed of the clutch disc 2b).

상기 클러치 용량(Cc)은 아래의 수학식 1에 의해 구해진다.The clutch capacity Cc is obtained by the following equation.

Cc = 마찰계수 X 유효반경 X 단면적 X 면압이다.Cc = friction coefficient X effective radius X cross sectional area X surface pressure.

여기서 마찰계수는 클러치 디스크(2b)의 마찰계수, 유효반경은 클러치 디스크 마찰력이 작용하는 유효반경, 면압(clamping load)은 클러치 디스크(2b)에 작용하는 압력이다.Here, the friction coefficient is the friction coefficient of the clutch disc 2b, the effective radius is the effective radius to which the clutch disc frictional force acts, and the clamping load is the pressure acting on the clutch disc 2b.

상기한 구성에서 열손실이 없는 경우에 클러치(2)를 통해 전달되는 파워 관계식은 Te*We=Tt*Wt이다(도 2 참조).In the above configuration, when there is no heat loss, the power relation transmitted through the clutch 2 is Te * We = Tt * Wt (see FIG. 2).

그런데 배기 규제 및 차량 성능 향상을 위해 엔진(1) 용량이 증대됨에 따라 클러치 용량(Cc)을 증대되어야 한다.However, the clutch capacity Cc should be increased as the engine 1 capacity is increased for exhaust regulation and vehicle performance improvement.

상기 Cc를 증대시키기 위해서는 상기 수학식 1에 나타낸 바와 같이 면압을 올리거나 유효반경을 증대시켜야 한다.In order to increase the Cc, as shown in Equation 1, the surface pressure must be increased or the effective radius must be increased.

면압을 증대시킬 경우 클러치 페달의 답력이 증대되어 사용자의 불만을 유발할 수 있고, 유효반경을 증대시킬 경우 변속기의 축간거리가 충분하지 않으면 서로 간섭을 일으키므로 간섭을 피하기 위해 변속기 축간거리를 증대하여야 하며, 이는 중량 증대, 기어 관성(inertia) 증대, 변속감 부족 등을 유발하는 문제점이 있었다.Increasing the surface pressure increases the pedal pedal effort, which may cause user dissatisfaction.Increasing the effective radius may cause interference with each other if the transmission gearbox distance is not sufficient, so the transmission gearbox distance should be increased to avoid interference. This has a problem of increasing weight, increasing gear inertia, lack of shifting feeling, and the like.

본 발명은 상술한 문제점을 해결하기 위하여 안출된 것으로서, 엔진의 크랭크축, 입력축, 클러치 디스크를 단순유성기어의 선기어, 캐리어, 링기어로 각각 연결하여 클러치의 마찰에 의해 동력이 전달될 때 클러치가 담당하는 파워를 줄임으로써 클러치의 용량과 사이즈를 줄일 수 있는 유성기어와 클러치를 이용한 차량의 동력전달구조를 제공하는데 그 목적이 있다.The present invention has been made to solve the above problems, the clutch is connected to the crankshaft, the input shaft, the clutch disk of the simple planetary gear, respectively, the sun gear, the carrier, the ring gear of the clutch when the power is transmitted by friction of the clutch The purpose of the present invention is to provide a power transmission structure of a vehicle using a planetary gear and a clutch that can reduce the capacity and size of the clutch by reducing the power in charge.

상술한 목적을 달성하기 위한 본 발명의 실시예에 따른 유성기어와 클러치를 이용한 차량의 동력전달구조는 엔진의 구동력을 단속하는 클러치를 통해 차량에 탑재된 엔진의 구동력을 변속기로 전달하는 구조에 있어서,In the power transmission structure of the vehicle using the planetary gear and the clutch according to the embodiment of the present invention for achieving the above object in the structure for transmitting the driving force of the engine mounted on the vehicle to the transmission through the clutch to control the driving force of the engine ,

상기 엔진의 크랭크축과 변속기의 입력축 및 클러치 디스크를 단순유성기어 로 연결하되,The crankshaft of the engine and the input shaft and the clutch disk of the transmission are connected by a simple planetary gear,

상기 단순유성기어는 내측에 제공되어 크랭크축과 연결되는 선기어와, 상기 선기어의 외주연에 치합되어 자전하는 피니언 기어와, 이 피니언 기어의 외측에 치합되어 클러치 디스크와 연결되는 링기어와, 상기 링기어와 결합하여 입력축과 연결되는 캐리어로 구성되는 것을 특징으로 한다.The simple planetary gear is provided with an inner gear connected to the crankshaft, a pinion gear engaged with the outer circumference of the sun gear and rotated, a ring gear meshed with the outer side of the pinion gear and connected to a clutch disk, and the ring. It is characterized by consisting of a carrier coupled to the input shaft coupled to the gear.

도 3은 본 발명에 따른 동력전달구조를 나타낸 도면이다.3 is a view showing a power transmission structure according to the present invention.

도시된 바와 같이, 엔진(10)과, 클러치(20)와, 단순유성기어(30) 및 변속기(40)를 포함하여 이루어진다.As shown, the engine 10 includes a clutch 20, a simple planetary gear 30, and a transmission 40.

클러치(20)는 엔진(10)의 구동력을 단속하고, 클러치 커버(22)와 클러치 디스크(24)로 이루어진다.The clutch 20 interrupts the driving force of the engine 10 and consists of a clutch cover 22 and a clutch disk 24.

변속기(40)는 차실에 장착된 변속레버(미도시)의 조작에 따라 상기 클러치(20)를 통해 전달받은 엔진(10)의 구동력을 증감시키고, 후진변속 작용을 행한다.The transmission 40 increases or decreases the driving force of the engine 10 transmitted through the clutch 20 according to an operation of a shift lever (not shown) mounted in a vehicle compartment, and performs a reverse shift action.

상기 변속기(40)는 엔진(10)의 구동력을 전달받아 회전되는 입력축(42)과, 상기 입력축(42)과 평행하게 배치되고 차동장치로 변속된 엔진(10)의 구동력을 전달하는 출력축(44)과, 상기 입력축(42)과 출력축(44) 사이에 배치되어 변속시 상기 입력축(42)과 출력축(44)을 동기화시킴과 아울러 입력축(42)과 출력축(44)을 일정 기어비로 연결하는 동기장치(45,46,47)를 포함하여 구성된다.The transmission 40 has an input shaft 42 which is rotated by receiving the driving force of the engine 10 and an output shaft 44 which is disposed in parallel with the input shaft 42 and transmits the driving force of the engine 10 shifted by a differential device. And the input shaft 42 and the output shaft 44 to synchronize the input shaft 42 and the output shaft 44 at the time of shifting and to connect the input shaft 42 and the output shaft 44 at a constant gear ratio. It comprises a device (45, 46, 47).

상기 단순유성기어(30)는 내측에 제공되어 엔진(10)의 크랭크축(12)과 연결되는 선기어(32)와, 상기 선기어(32)의 외주연에 치합되어 자전하는 피니언기 어(36)와, 이 피니언기어(36)의 외측에 치합되어 클러치 디스크(24)와 연결되는 링기어(34)와, 상기 링기어(34)와 결합하여 변속기(40)의 입력축(42)과 연결되는 캐리어(38)를 포함하여 구성된다.The simple planetary gear 30 is provided on the inside and is connected to the crankshaft 12 of the engine 10 and the sun gear 32, and the pinion gear 36 is engaged with the outer circumference of the sun gear 32 to rotate. And a ring gear 34 engaged with the outer side of the pinion gear 36 and connected to the clutch disk 24, and a carrier connected to the input shaft 42 of the transmission 40 in combination with the ring gear 34. It comprises 38.

즉, 클러치 디스크(24)와 변속기의 입력축(42)과 엔진의 크랭크축(12)을 단순유성기어(30)로 연결하되, 엔진의 크랭크축(12)은 선기어(32)와, 입력축(42)은 캐리어(38)와, 클러치 디스크(24)는 링기어(34)와 연결된다.That is, the clutch disc 24 and the input shaft 42 of the transmission and the crankshaft 12 of the engine are connected by a simple planetary gear 30. The crankshaft 12 of the engine is a sun gear 32 and an input shaft 42. Is connected to the carrier 38 and the clutch disk 24 to the ring gear 34.

상기 단순유성기어(30)는 변속기(40)의 내부에 위치되되, 클러치(20)와 단순유성기어(30) 사이의 크랭크축(12) 외측으로는 변속기(40)에 공급되는 오일의 누유를 방지하는 오일 시일(52)과, 크랭크축(12)의 회전을 지지하는 베어링(54)이 구비된다.The simple planetary gear 30 is positioned inside the transmission 40, and leaks oil from the oil supplied to the transmission 40 to the outside of the crankshaft 12 between the clutch 20 and the simple planetary gear 30. An oil seal 52 for preventing and a bearing 54 for supporting the rotation of the crankshaft 12 are provided.

상기한 구성에 따른 클러치 디스크(24)의 파워 담당을 알아보기 위해 먼저 단순유성기어(30)의 회전 및 토크에 관해 설명한다.In order to determine the power charge of the clutch disk 24 according to the above configuration, first, the rotation and torque of the simple planetary gear 30 will be described.

상기 단순유성기어(30)의 회전 관계식은 수학식 2와 같고, 토크 관계식은 수학식 3과 같다. The rotational relationship of the simple planetary gear 30 is represented by Equation 2, and the torque relationship is represented by Equation 3.

(1+R)*Wc = Wr + R*Ws(1 + R) * Wc = Wr + R * Ws

여기서 R는 Zs/Zr(링기어(34)와 선기어(32)의 기어비), Wc는 캐리어(38)의 회전수(입력축(42)의 회전수), Wr는 링기어(34)의 회전수(클러치 디스크(24)의 회전수), Ws는 선기어(32)의 회전수(크랭크축(12)의 회전수)이다.Where R is Zs / Zr (gear ratio of ring gear 34 and sun gear 32), Wc is rotational speed of carrier 38 (rotation of input shaft 42), and Wr is rotational speed of ring gear 34 (Rotational Speed of Clutch Disc 24) Ws is the rotational speed of sun gear 32 (the rotational speed of crankshaft 12).

Ts = R*Tr, Tc = Tr + TsTs = R * Tr, Tc = Tr + Ts

여기서 Ts는 선기어(32)의 토크, Tr은 링기어(34)의 토크, Tc는 캐리어(38)의 토크이다.Ts is the torque of the sun gear 32, Tr is the torque of the ring gear 34, Tc is the torque of the carrier 38.

상기 수학식 2와 수학식 3에서 단순유성기어(30)의 파워 관계식은 수학식 4가 된다.In Equations 2 and 3, the power relational expression of the simple planetary gear 30 is represented by Equation 4.

Tc*Wc = Tr*Wr + Ts*WsTc * Wc = Tr * Wr + Ts * Ws

다음 단순유성기어(30)와 연결된 엔진의 크랭크축(12), 입력축(42), 클러치 디스크(24)의 회전에 대해 설명한다.Next, the rotation of the crankshaft 12, the input shaft 42, and the clutch disk 24 of the engine connected to the simple planetary gear 30 will be described.

클러치(20)를 발로 밟고 변속기(40)가 중립인 경우에, 선기어(32)는 엔진(10)에 의해 구동하고, 클러치(20)를 발로 밟아 연결이 끊어졌으므로 링기어(34)는 자유 상태이며, 캐리어(38)는 변속기(40)가 중립에 위치되어 있으므로 동력이 전달되지 않는다.In the case where the clutch 20 is stepped on and the transmission 40 is neutral, the sun gear 32 is driven by the engine 10, and the ring gear 34 is in a free state because the connection is broken by stepping on the clutch 20. The carrier 38 is not powered because the transmission 40 is in neutral.

클러치(20)를 발로 밟고 변속기(40)의 변속이 이루어지는 경우에, 선기어(32)는 엔진(10)에 의해 구동하고, 클러치(20)를 발로 밟아 연결이 끊어졌으므로 링기어(34)는 자유 상태이며, 캐리어(38)는 타이어에 의해 구동되므로 동력은 전달되지 않는다.In the case where the transmission of the transmission 40 is made by stepping on the clutch 20, the sun gear 32 is driven by the engine 10, and the ring gear 34 is free because the connection is broken by stepping on the clutch 20. In this state, the carrier 38 is driven by the tire, so no power is transmitted.

이때 링기어(34)의 회전수는 수학식 5가 된다.At this time, the rotation speed of the ring gear 34 is expressed by Equation 5.

Wr = (1+r)*Wc - R*WsWr = (1 + r) * Wc-R * Ws

이를 각 기어 간의 회전관계로 나타내면 도 4에 나타낸 바와 같이, Wc가 Ws와 Wr사이에서 1: r로 내분된 값이다.As shown in the rotational relationship between the gears, as shown in FIG. 4, Wc is a value obtained by integrating 1: r between Ws and Wr.

클러치(20)에서 발을 떼어 동력이 전달되는 경우에, 선기어(32)는 엔진(10)에 의해 구동되고, 클러치(20)가 연결되면서 링기어(34)의 회전수는 선기어(32)와 회전수가 같게 되며, 캐리어(38)는 선기어(32) 및 링기어(34)와 직결되어, 도 5에 나타낸 바와 같이, 모든 기어(32,34,38)의 회전수는 모두 같아져 엔진(10)의 동력이 변속기(40)로 전달된다.When power is transmitted by releasing the clutch 20, the sun gear 32 is driven by the engine 10, and the rotation speed of the ring gear 34 is connected to the sun gear 32 while the clutch 20 is connected. The rotation speed becomes the same, and the carrier 38 is directly connected to the sun gear 32 and the ring gear 34, and as shown in FIG. 5, the rotation speed of all the gears 32, 34, 38 is the same, and the engine 10 Is transmitted to the transmission 40.

다음 클러치 디스크(24)의 파워 담당에 대해 설명한다.Next, power charge of the clutch disk 24 will be described.

상기한 클러치(20)와 단순유성기어(30)를 이용한 동력전달구조에서, 변속기(10)를 통해 기어 변속을 한 후 클러치 페달을 떼면서 클러치(20)의 마찰에 의해 동력이 링기어(34)로 전달되고 있고 이때 클러치(20)에서의 손실이 없다고 가정하면, 도 6으로 도시할 수 있다.In the power transmission structure using the clutch 20 and the simple planetary gear 30, the gear is shifted through the transmission 10, and then the power is released by the friction of the clutch 20 while releasing the clutch pedal. Assuming that there is no loss in the clutch 20 at this time, it can be shown in FIG.

도 6에서 클러치(20)가 담당하는 파워는 Tr*Wr으로 Tc*Wc보다 작다(Tr*Wr < Tc*Wc)In FIG. 6, the power that the clutch 20 is responsible for is Tr * Wr, which is smaller than Tc * Wc (Tr * Wr <Tc * Wc).

이는 클러치(20)에서 마찰에 의해 링기어(34)로 동력이 전달되면서 동시에 선기어(32)를 통해 캐리어(입력축)로 동력이 전달되기 때문이다.This is because power is transmitted from the clutch 20 to the ring gear 34 by friction and at the same time, power is transmitted to the carrier (input shaft) through the sun gear 32.

본 발명에 따른 동력전달구조에서 클러치(20) 부분의 파워는 Te'*We' = Tr*Wr 이고, 종래 클러치(2) 부분의 파워는 Te*We = Tt*Wt로 이의 대소관계를 살펴보면, Te'*We' = Tr*Wr < Te*We = Tt*Wt 로서, 클러치가 담당하는 파워가 종래보다 감소함을 알 수 있다.In the power transmission structure according to the present invention, the power of the clutch 20 is Te '* We' = Tr * Wr, and the power of the conventional clutch 2 is Te * We = Tt * Wt. As Te '* We' = Tr * Wr <Te * We = Tt * Wt, it can be seen that the power in charge of the clutch is reduced than before.

이와 같이 클러치(20)가 담당하는 파워를 감소시킴으로써 클러치(20)의 용량이나, 사이즈를 줄일 수 있다.As described above, the power and size of the clutch 20 can be reduced by reducing the power that the clutch 20 is responsible for.

이러한 클러치(20)와 단순유성기(30)어를 이용한 동력전달구조는 변속기의 입력축(42)과 차동축(48)의 축간거리 등 레이아웃 문제로 클러치(20)의 사이즈(외경)를 증대시킬 수 없거나 운전자 페달 조작의 편의를 위해 면압(clamping load)에 제약이 있을 때 유리한 구조이다.The power transmission structure using the clutch 20 and the simple planetary gear 30 can increase the size (outer diameter) of the clutch 20 due to layout problems such as the distance between the shaft of the input shaft 42 and the differential shaft 48 of the transmission. It is an advantageous structure when there is no constraint on clamping load or for convenience of driver pedal operation.

이상에서와 같이 본 발명에 의하면, 클러치의 마찰에 의해 동력이 전달될 때 클러치가 담당하는 파워를 단순유성기어를 이용해 감소시킴으로써 클러치의 사이즈 및 용량을 줄일 수 있고, 클러치가 담당하는 파워가 감소하는 만큼 열손실이 줄어 내구성도 향상시킬 수 있다.As described above, according to the present invention, by reducing the power of the clutch when the power is transmitted by the friction of the clutch using a simple planetary gear, the size and capacity of the clutch can be reduced, the power that the clutch is reduced As a result, heat loss can be reduced, thereby improving durability.

Claims (3)

엔진의 구동력을 단속하는 클러치를 통해 차량에 탑재된 엔진의 구동력을 변속기로 전달하는 구조에 있어서,In a structure for transmitting the driving force of the engine mounted on the vehicle to the transmission through a clutch to control the driving force of the engine, 상기 엔진(10)의 크랭크축(12)과 변속기(40)의 입력축(42) 및 클러치 디스크(24)를 단순유성기어(30)로 연결하되,The crankshaft 12 of the engine 10 and the input shaft 42 and the clutch disk 24 of the transmission 40 are connected by a simple planetary gear 30, 상기 단순유성기어(30)는 내측에 제공되어 크랭크축(12)과 연결되는 선기어(32)와, 상기 선기어(32)의 외주연에 치합되어 자전하는 피니언 기어(36)와, 이 피니언(36) 기어의 외측에 치합되어 클러치 디스크(24)와 연결되는 링기어(34)와, 상기 링기어(34)와 결합하여 입력축(42)과 연결되는 캐리어(38)로 구성되는 것을 특징으로 하는 유성기어와 클러치를 이용한 차량의 동력전달구조.The simple planetary gear 30 is provided with an inner gear 32 connected to the crank shaft 12, a pinion gear 36 engaged with the outer circumference of the sun gear 32 to rotate, and the pinion 36. A planetary gear comprising a ring gear 34 engaged with the outer side of the gear and connected to the clutch disk 24 and a carrier 38 coupled to the ring gear 34 and connected to the input shaft 42. Power transmission structure of vehicle using gear and clutch. 제 1 항에 있어서,The method of claim 1, 상기 클러치(20)의 마찰에 의해 링기어(34)로 동력이 전달되면서 동시에 선기어(32)를 통해 캐리어(38) 및 입력축(42)으로 동력이 전달되어 클러치(20)에서 담당하는 파워가 단순유성기어(40)에 의해 감소하는 것을 특징으로 하는 유성기어와 클러치를 이용한 차량의 동력전달구조.Power is transmitted to the ring gear 34 by friction of the clutch 20, and at the same time, power is transmitted to the carrier 38 and the input shaft 42 through the sun gear 32, thereby simplifying the power in charge of the clutch 20. Power transmission structure of the vehicle using the planetary gear and clutch, characterized in that the reduction by the planetary gear (40). 제 1 항 또는 제 2 항에 있어서,The method according to claim 1 or 2, 상기 단순유성기어(30)는 변속기(40)의 내부에 위치되되, 클러치(20)와 단순 유성기어(30) 사이의 크랭크축(12) 외측으로는 변속기(40)에 공급되는 오일의 누유를 방지하는 오일 시일(52)과, 크랭크축(12)의 회전을 지지하는 베어링(54)이 구비되는 것을 특징으로 하는 유성기어와 클러치를 이용한 차량의 동력전달구조.The simple planetary gear 30 is positioned inside the transmission 40, and leaks oil from the oil supplied to the transmission 40 to the outside of the crankshaft 12 between the clutch 20 and the simple planetary gear 30. Oil transmission (52) to prevent, and a bearing (54) for supporting the rotation of the crankshaft (12) is provided, the power transmission structure of a vehicle using a planetary gear and a clutch.
KR1020060078645A 2006-08-21 2006-08-21 Power transmission structure for cars by planetary gear and clutch KR100757251B1 (en)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR960040760A (en) * 1995-05-13 1996-12-17 이병홍 Automotive automatic transmission
KR970075478A (en) * 1996-05-08 1997-12-10 박병재 Semi-automatic transmission for automobile
KR100534229B1 (en) 2004-04-14 2005-12-08 현대자동차주식회사 Manual transmission

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR960040760A (en) * 1995-05-13 1996-12-17 이병홍 Automotive automatic transmission
KR970075478A (en) * 1996-05-08 1997-12-10 박병재 Semi-automatic transmission for automobile
KR100534229B1 (en) 2004-04-14 2005-12-08 현대자동차주식회사 Manual transmission

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