KR20090043121A - An automatic transmission for vehicles - Google Patents

Abstract

To reduce the overall length, increase the mountability and space utilization, and contribute to the weight reduction;

In arranging two clutches which are disposed adjacent to each other on the rear side of the planetary gear set and variably transmit the rotational power transmitted from the front side to the two rotating elements forming the planetary gear set, respectively.

The first clutch is disposed adjacent to the rear side of the planetary gear set, and the second clutch is disposed behind the first clutch so that the first clutch is driven by a rotating element (sun gear) located at the central side of the planetary gear set. Variablely transmit the power, and the second clutch provides a vehicle automatic transmission that can variably transmit power to a rotating element (oil carrier) located on the outer circumferential side of the rotating element receiving the power of the first clutch.

Clutch, Clutch Hub, Clutch Retainer

Description

Automotive automatic transmission {AN AUTOMATIC TRANSMISSION FOR VEHICLES}

The present invention relates to an automatic transmission for a vehicle in which a plurality of clutches applied to a gear train of an automatic transmission for a vehicle are arranged adjacent to each other, thereby reducing the overall length and increasing space utilization.

The vehicle automatic transmission detects the driving state of the vehicle from the detection means disposed in place of the vehicle, and based on this, the transmission control unit (TCU) automatically controls the gear train composed of a combination of planetary gear sets and automatically It is configured to carry out shifting.

Accordingly, the gear train applied to the automatic transmission is preferably configured to implement more transmission stages in order to improve power performance and fuel consumption rate.

Even if the same number of gear stages are implemented, the durability, power transmission efficiency, size and weight of the planetary gear set vary greatly depending on the combination method of the planetary gear set. Efforts for development are ongoing.

In developing a gear train using a planetary gear set, a new planetary gear set is not developed, but a simple combination of a conventional planetary gear set and a composite planetary gear set in some way, and the accompanying clutch and brake In addition, various studies have been actively conducted with the aim of realizing a desired shift stage and a shift ratio without any power loss by arranging several one-way clutches at any position.

In particular, in the case of a manual transmission, if there are too many shift stages, the driver should shift frequently. However, in the case of an automatic transmission, the shift is automatically performed according to the driving state. Therefore, more shift stages can be realized. Developing a well-trained gear train is of great value.

From this point of view, four-speed and five-speed automatic transmissions are the mainstream automatic transmissions currently in use, but recently six-speed automatic transmissions have been developed and applied to vehicles. Development of an automatic transmission that can realize a speed shift stage is being actively progressed.

In view of this, an example of the automatic transmission gear train already proposed may be Korean Patent Application No. 2007-0082377 (August 16, 2007) proposed by the present applicant.

More specifically, as shown in FIG. 1, the first planetary gear set PG1 consisting of a single pinion planetary gear set, the second planetary gear set PG2 consisting of a double pinion planetary gear set, a ring gear and a planet carrier By combining a third planetary gear set (PG3) consisting of a shared planetary type planetary gear set to provide a gear train that can implement a shift stage of 8 forward speed and 1 reverse speed.

The first planetary gear set PG1 has a sun gear S1 directly connected to the input shaft IS to operate as an input element at all times, and the planet carrier PC1 forms a first intermediate output path MOP1 as an output element. , The ring gear R1 is directly connected to the transmission housing H as a fixed element.

In the second planetary gear set PG2, the sun gear S2 is directly connected to the first intermediate output path MOP1 of the first planetary gear set PG1 to form a first intermediate input path MIP1. The carrier PC2 forms a second intermediate output path MOP2 as an output element, and the one-way clutch F and the first brake disposed in parallel with each other so that the ring gear R3 can operate as an optional fixing element. It connects with the transmission housing H via B1), and the 2nd clutch C2 is arrange | positioned between the ring gear R2 and the planet carrier PC2.

The third planetary gear set PG3 is a composite planetary gear set sharing a planetary carrier with a ring gear, and the small diameter sun gear S4 has a first intermediate output path MOP1 of the first planetary gear set PG1 and a first planetary gear set. Variablely connected via the clutch C1 to form the first intermediate variable input path MAIP1, and the large diameter sun gear S3 is directly connected to the second intermediate output path MOP2 of the second planetary gear set PG2. To form the second intermediate input path MIP2, and the planet carrier PC3 is variably connected via the input shaft IS and the third clutch C3 to form the second intermediate variable input path MAIP2, and the ring The gear R3 is variably connected to the large diameter sun gear S4 via the fourth clutch C4 to form an output path OP as an output element.

Accordingly, the first clutch C1 and the one-way clutch F at the first speed, the first clutch C1 and the second brake B2 at the second speed, and the first clutch C1 and the fourth clutch at the third speed ( C4), the first clutch C1 and the third clutch C3 at the fourth speed, the third clutch C3 and the fourth clutch C4 at the fifth speed, the second clutch C2 and the third clutch at the sixth speed (C3), the third clutch C3 and the second brake B2 at the seventh speed, the third clutch C3 and the first brake B1 are operated at the eighth speed, and the fourth clutch C4 and the fourth clutch C4 at the reverse speed. The shift is made while the first brake B1 is operated.

In the above-described gear train of the automatic transmission, the first clutch (under clutch; C1) operating at the forward 1, 2, 3, and 4 speeds, and the third clutch operating at the forward 4, 5, 6, and 7 speeds (over) The drive clutch C4 is received from the front side of the third planetary gear set PG3 and is variably transferred to the small diameter sun gear S4 and the planet carrier PG3 of the third planetary gear set PG3. Is placed.

As described above, in arranging the first and third clutches C1 and C3 adjacent to each other, the connection structure is conventionally arranged as shown in FIG.

First, the third clutch C1 is disposed to be close to the third planetary gear set PG3, and the first clutch C1 is disposed to the rear side thereof.

To this end, the hub 100 of the third clutch C3 is connected to the first power transmission member 102 connected to any one rotating element (oil carrier) of the planetary gear set by means of welding or the like. The third clutch retainer 104 is disposed at a predetermined distance to the outer circumferential side of the third clutch hub 100 so that the third clutch retainer 104 and the third clutch retainer 104 are disposed as usual. The clutch plate 106 and the clutch disk 108 were disposed.

The third clutch retainer 104 extends to the rear side and is connected to the input shaft 110 by means of welding or the like, so that the rotational power of the input shaft 110 can be transmitted.

In addition, a third clutch hydraulic actuator 112 is formed inside the rear end of the third clutch retainer 104 so that the push rod 116 extending from the piston 114 thereof may retain the third clutch retainer 104. It is configured such that the end thereof is in a state of being close to the third clutch C3 in a state where interference with an inner portion of the is not caused.

Accordingly, when the hydraulic pressure is supplied to the hydraulic chamber 118 of the third clutch hydraulic actuator 112, the piston 114 moves forward to rub the clutch plate 106 and the disk 108 to rotate the input shaft 110. Power is transmitted to the rotating element (oil carrier) of the planetary gear set connected to it through the first power transmission member (102).

In addition, in arranging the first clutch C1, a rear side portion of the first clutch retainer 120 extends unintentionally with the inner surface of the push rod 116 of the third clutch piston 114, and thus the input shaft 110. The second power transmission member 122 coupled to the outer circumferential side of the c) without rotation interference is connected by means of welding or the like.

The third clutch hub 124 is disposed at an inner portion of the first clutch retainer 120 at a predetermined interval so that the first clutch hub 124 and the first clutch retainer 120 are operated as usual. Clutch plate 126 and clutch disk 128 were placed.

In addition, the first clutch hub 124 is connected to the rear end of the third power transmission member 130 coupled to the outer circumferential side of the second power transmission member 122 without welding interference by welding means or the like. The rotational power of the second power transmission member 122 can be transmitted to the third power transmission member 130 through the first clutch C1.

In addition, the first clutch hydraulic actuator 132 is formed inside the rear end of the first clutch retainer 120 and the push rod 136 extending from the piston 134 thereof is retained for the first clutch retainer 120. It is configured such that an end thereof is in a state of being close to the first clutch C1 in a state where interference with an inner side of the is not generated.

Accordingly, when the hydraulic pressure is supplied to the hydraulic chamber 138 of the hydraulic actuator 132 for the first clutch, the piston 134 moves forward to rub the clutch plate 126 and the disk 128, thereby providing a second power transmission member ( The rotating power of 122 is transmitted to the rotating element (large diameter sun gear in FIG. 1) of the planetary gear set connected thereto through the third power transmission member 130.

However, in the clutch arrangement structure as described above, the third clutch hydraulic actuator for operating the third clutch is arranged at the rear of the first clutch, so that the transmission length is increased, the weight is increased, and the mountability is not good. In other words, it has a problem of being a factor of cost increase.

Therefore, the present invention has been invented to solve the above problems, the object of the present invention is to arrange two clutches adjacent to each other, to reduce the overall length to increase the mountability and space utilization, and contribute to light weight An automatic transmission for a vehicle is provided.

In order to realize the above object, the present invention, as in claim 1, the rotational power which is disposed adjacent to each other on the rear side of the planetary gear set and transmitted from the front side to each of the two rotating elements forming the planetary gear set In arranging two clutches which variably transmit,

The first clutch is disposed adjacent to the rear side of the planetary gear set, and the second clutch is disposed behind the first clutch so that the first clutch is driven by a rotating element (sun gear) located at the central side of the planetary gear set. And variably transmit the power, and the second clutch provides a vehicle automatic transmission that can variably transmit power to a rotating element (oil carrier) positioned on the outer circumferential side of the rotating element that receives the power of the first clutch.

The power transmission means for transmitting power to the first and second clutches includes an input shaft positioned at the center of the shaft as in claim 2, and a first power transmission member coupled to the outer circumference of the input shaft without rotation interference. .

In arranging the first and second clutches as described above, the first clutch has a first clutch hub coupled to the outer circumferential side of the first power transmission member without rotation interference as described in claim 3 so that the front end thereof is planetary. Is connected to the second power transmission member connected to the rotary element located in the center of the gear set, the first clutch retainer arranged at a predetermined interval on the outer peripheral side of the first clutch hub extends to the rear side by a predetermined length It is characterized in that the end side thereof is connected to the first power transmission member in a state bent in a predetermined shape toward the inner diameter portion.

And the second clutch is connected to a third power transmission member which extends to the front side and is connected to the corresponding rotating element (the planet carrier) of the planetary gear set, as in claim 4, wherein the second clutch 2 is characterized in that the rear portion of the second clutch retainer, which is arranged at a predetermined interval on the outer circumferential side of the clutch hub, is connected to the input shaft in a state of being bent in a predetermined shape toward the inner diameter portion.

In the above, a disc set is disposed between the first and second clutch hubs and the retainer, and a hydraulic actuator is disposed in the inner diameter of the rear first and second clutch retainers of the disc set.

As described above, the present invention, unlike the prior art, the first clutch for variably transmitting power to the rotating element (sun gear) on the central side of the planetary gear set is disposed adjacent to the planetary gear set, the outer periphery of the planetary gear set By arranging a second clutch on the rear side of the first clutch that transmits power to a rotating element (oil carrier) located on the side, the hydraulic actuators controlling these first and second clutches can be arranged forward, as much as the automatic The overall length of the transmission can be reduced, the weight of the reduced length is reduced, and the miniaturization can improve the mountability and space utilization of the engine room.

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

 Figure 2 is an enlarged cross-sectional view of the main part of the present invention, the present invention is a gear train of the automatic transmission, the planetary gear set (PG) is disposed adjacent to each other adjacent to each other the planetary gear set to apply the rotational power transmitted from the front side ( Two clutches {K1; each variablely transmitted to two rotating elements forming PG); It is characterized by the arrangement structure of K2; corresponding to the third clutch C3 of FIG. 1, corresponding to the first clutch C1 of FIG.

The power transmission means transmitted from the front side to the first and second clutches K1 and K2 comprises an input shaft 2 and a first power transmission member 4 coupled to the outer circumferential side of the input shaft 2 without rotation interference. .

The first clutch K1 is installed adjacent to the rear side of the planetary gear set PG, and the second clutch K2 is disposed at the rear side of the first clutch K1, so that the first clutch K1 is Variable power is transmitted to a rotating element (sun gear) positioned at the center of the planetary gear set PG, and the second clutch K2 is an outer circumference of the rotating element that receives the power of the first clutch K1. The power is variably transmitted to the rotating element (oil carrier) located on the side.

To this end, the first clutch hub 6 forming the first clutch K1 is coupled to the outer circumferential side of the first power transmission member 4 without rotation interference so that the front end thereof is the center of the planetary gear set PG. The first clutch retainer 10 is connected to the second power transmission member 8 connected to the rotating element (sun gear) positioned at the side, and is disposed at a predetermined interval on the outer circumferential side of the first clutch hub 6. The first power transmission member 4 is connected to the first power transmission member 4 by welding means in a state where the end side thereof is bent in a predetermined shape toward the inner diameter portion while extending to the rear side by a predetermined length.

And, as is known in the art, a disc set 16 including a clutch plate 12 and a clutch disc 14 is disposed between the first clutch hub 6 and the retainer 10, and the disc set 16 is disposed. The hydraulic actuator 18 is disposed in the inner diameter portion of the rear first clutch retainer 10.

Accordingly, when the hydraulic pressure is supplied to the hydraulic chamber 20 of the hydraulic actuator 18 for the first clutch, the piston 22 moves forward, thereby causing the disk set 16 to be rubbed, thereby reducing the pressure of the first power transmission member 4. The rotational power is to be transmitted to the second power transmission member (8).

The hub 30 of the second clutch K2 disposed on the rear side of the first clutch K1 extends to the front side and is connected to the corresponding rotating element (the planet carrier) of the planetary gear set PG. The rear side portion of the second clutch retainer 34, which is connected to the member 32 and disposed at a predetermined interval on the outer circumferential side of the second clutch hub 30, is bent into a predetermined shape toward the inner diameter portion. Is connected by the input shaft (2) and the welding means.

As described in the related art, a disc set 40 including a clutch plate 36, a clutch disc 38, and the like is disposed between the second clutch hub 30 and the retainer 34, and the disc set 40 is disposed. The hydraulic actuator 42 is disposed in the inner diameter portion of the rear second clutch retainer 34 at.

Accordingly, when operating hydraulic pressure is supplied to the hydraulic chamber 44 of the second clutch hydraulic actuator 42, the piston 46 moves forward, thereby causing the disk set 40 to friction, thereby reducing rotational force of the input shaft 2. 3 is to be transmitted to the power transmission member (32).

That is, according to the present invention, the first clutch K1 which variably transmits power to the rotating element (sun gear) on the central side of the planetary gear set PG is disposed adjacent to the planetary gear set PG. The first and second clutches K2 are disposed on the rear side of the first clutch K1 to transmit power to the rotating element (oil carrier) located on the outer circumferential side of the planetary gear set PG3. Hydraulic actuators 18 and 42 for controlling K1 and K2 can be disposed in the inner diameter portions of the first and second clutches K1 and K2.

As a result, the hydraulic actuators 18 and 42 of the first and second clutches K1 and K2 are disposed forward, as compared with the related art, thereby reducing the overall length of the automatic transmission, and the weight is reduced as much as the total length is reduced. As a result, the compactness and the space utilization of the engine room can be improved.

Although the preferred embodiments of the present invention have been described above, the present invention is not limited to the above embodiments, and those of ordinary skill in the art can easily invent and equalize the same from the embodiments of the present invention. It includes all changes in the ranges that become.

1 is an example of an automatic transmission gear train for explaining the application of the present invention.

2 is an enlarged cross-sectional view of the main portion of the present invention.

3 is a conventional cross-sectional view.

Claims (4)

In arranging two clutches which are disposed adjacent to each other on the rear side of the planetary gear set and variably transmit the rotational power transmitted from the front side to the two rotating elements forming the planetary gear set, respectively. The first clutch is disposed adjacent to the rear side of the planetary gear set, and the second clutch is disposed behind the first clutch so that the first clutch is driven by a rotating element (sun gear) located at the central side of the planetary gear set. And variably transmit the power, and the second clutch is arranged so that the power can be variably transmitted to a rotating element (oil carrier) positioned on the outer circumferential side of the rotating element receiving the power of the first clutch. Transmission. The vehicle automatic transmission device according to claim 1, wherein the power transmission means for transmitting power to the first clutch comprises an input shaft positioned at the center of the shaft and a first power transmission member coupled to the outer circumferential side of the input shaft without rotation interference. Transmission. 3. The first clutch of claim 1 or 2, wherein the first clutch comprises a rotating element having a first clutch hub coupled to the outer circumferential side of the first power transmission member without rotation interference so that its front end is located at the central side of the planetary gear set. It is connected to the second power transmission member connected, The first power transmission in a state in which the first clutch retainer arranged at a predetermined interval on the outer circumferential side of the first clutch hub extends to the rear side by a predetermined length and the end side thereof is bent into a predetermined shape toward the inner diameter portion. Connected to the member, A disc set is disposed between the first clutch hub and the retainer, and a hydraulic actuator is disposed in the inner diameter of the rear first clutch retainer of the disc set. 4. The second clutch of claim 1 or 3, wherein the second clutch is connected to a third power transmission member which extends forward and is connected to a corresponding rotating element (oil carrier) of the planetary gear set. The rear side portion of the second clutch retainer, which is arranged at a predetermined interval on the outer circumferential side of the second clutch hub, is connected to the input shaft in a state bent in a predetermined shape toward the inner diameter portion, And a disc set is disposed between the second clutch hub and the retainer, and a hydraulic actuator is disposed in the inner diameter of the rear second clutch retainer of the disc set.

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