KR101765496B1

KR101765496B1 - Transmission apparatus

Info

Publication number: KR101765496B1
Application number: KR1020150165174A
Authority: KR
Inventors: 서각하; 이병민
Original assignee: 현대 파워텍 주식회사
Priority date: 2015-11-25
Filing date: 2015-11-25
Publication date: 2017-08-08
Also published as: KR20170061202A

Abstract

Disclosure of the Invention The invention relating to a transmission is disclosed. A transmission device of the present invention includes: a first input shaft connected to a power source by a first clutch and to which a plurality of first drive gears are connected; A second input shaft connected to the power source by the second clutch and provided so as to be concentric with the first input shaft and to which a plurality of second drive gears are connected; A first driven gear portion in which a plurality of first driven gears are formed to be coupled to the first drive gear; A second driven gear portion in which a plurality of second driven gears are formed to be coupled to the plurality of first drive gears; An output shaft connected to the first driven gear portion and the second driven gear portion; A third driven gear portion having a plurality of third driven gears coupled to the plurality of second drive gears; A plurality of synchronizers arranged between the plurality of second drive gears, between the plurality of first driven gears and between the plurality of second driven gears, respectively, and connected to the second drive gear, the first driven gear and the second driven gear part; And a planetary gear set connected to the output shaft and variably connected to the third driven gear portion by a third clutch.

Description

[0001] TRANSMISSION APPARATUS [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a speed change device, and more particularly, to a speed change device capable of reducing overall length and weight.

Generally, the vehicle is equipped with a transmission. The transmission can shift the speed of the vehicle to a plurality of stages by driving the plurality of clutches. A double clutch transmission in which two clutches are installed may be applied to the transmission. The double clutch transmission is equipped with two clutch mechanisms, making it easy to operate and less power loss.

As the vehicle speeds up, the number of shift stages increases. The number of clutch mechanisms or the number of synchronous portions increases in order to increase the number of speed-change stages. As the number of clutch mechanisms or synchro sections increases, the number of parts, length and weight of the transmission increases. As the weight of the vehicle increases and the parts increase, the fuel economy increases and the manufacturing cost increases. Therefore, there is a need to improve this.

Background Art [0002] The background art of the present invention is disclosed in Korean Patent Laid-Open Publication No. 2014-0053824 (titled Vehicle Drive System Including a Transmission, published on Apr. 05, 2008).

SUMMARY OF THE INVENTION It is an object of the present invention to provide a transmission capable of reducing overall length and weight.

A transmission according to the present invention includes: a first input shaft connected to a power source by a first clutch and to which a plurality of first drive gears are connected; A second input shaft connected to a power source by a second clutch and provided so as to be concentric with the first input shaft and to which a plurality of second drive gears are connected; A first driven gear portion having a plurality of first driven gears to be engaged with the first drive gear; A second driven gear portion in which a plurality of second driven gears are formed to be coupled to the plurality of first drive gears; An output shaft connected to the first driven gear portion and the second driven gear portion; A third driven gear portion having a plurality of third driven gears coupled to the plurality of second drive gears; A first drive gear, a second driven gear, a second driven gear, and a second driven gear, the second drive gear, the second driven gear, the first driven gear, A plurality of synchronizing units connected to the plurality of synchronizing units; And a planetary gear set connected to the output shaft and variably connected to the third driven gear portion by a third clutch.

The planetary gear set including: a sun gear coupled to the output shaft; A carrier disposed to engage with the sun gear; And a ring gear meshed with the carrier and connected to the third driven gear portion.

And the third clutch can variably connect the third driven gear portion and the carrier.

When the third driven gear portion and the carrier are disconnected by the third clutch, the planetary gear set can be shifted at an intermediate speed between the sun gear and the ring gear.

When the third driven gear portion and the carrier are disconnected by the third clutch, an even-numbered forward speed change stage can be achieved.

When the third driven gear portion and the carrier are connected by the third clutch, the third driven gear portion and the carrier may not be shifted in the planetary gear set.

When the third driven gear portion and the carrier are connected by the third clutch, an odd-numbered forward speed change stage can be achieved.

The rotary shaft of the planetary gear set may be formed in parallel with the output shaft.

The transmission may further include a parking gear connected to a rotation shaft of the carrier.

The transmission includes a first forward speed change stage achieved when the first clutch and the third clutch are driven and the synchro portion is connected to the first gear; A second forward speed change stage achieved when the first clutch and the second clutch are driven and the synchro portion is connected to the first gear and the third gear; A third forward speed change stage achieved when the second clutch and the third clutch are driven and the synchro portion is connected to the third gear; A fourth forward speed change stage achieved when the first clutch and the second clutch are driven and the synchro portion is connected to the third gear and the fifth gear; A fifth forward speed change stage achieved when the first clutch and the third clutch are driven and the synchro portion is connected to the fifth gear; A sixth forward speed change stage achieved when the first clutch and the second clutch are driven and the synchro portion is connected to the fifth gear and the seventh gear; A seventh forward speed change stage achieved when the second clutch and the third clutch are driven, and the synchro portion is connected to the seventh gear; An eighth forward speed change stage achieved when the first clutch and the second clutch are driven and the synchro portion is connected to the seventh gear and the ninth gear; A ninth forward speed change stage achieved when the first clutch and the third clutch are driven and the synchro portion is connected to the ninth gear; And a reverse shift stage achieved when the first clutch and the third clutch are driven and the synchro portion is connected to the reverse gear.

A transmission according to the present invention includes: a first input shaft connected to a power source by a first clutch and to which a plurality of first drive gears are connected; A second input shaft connected to a power source by a second clutch and provided so as to be concentric with the first input shaft and to which a plurality of second drive gears are connected; A first driven gear portion having a plurality of first driven gears to be engaged with the first drive gear; A second driven gear portion in which a plurality of second driven gears are formed to be coupled to the plurality of first drive gears; An output shaft connected to the first driven gear portion and the second driven gear portion; A third driven gear portion having a plurality of third driven gears coupled to the plurality of second drive gears; A first driven gear, a second driven gear, a third driven gear, and a third driven gear, wherein the first driven gear, the second driven gear, and the third driven gear are disposed between the plurality of first driven gears, between the plurality of second driven gears, Respectively; And a planetary gear set connected to the output shaft and variably connected to the third driven gear portion by a third clutch.

And the third clutch can variably connect the third driven gear portion and the ring gear.

When the third driven gear portion and the ring gear are disconnected by the third clutch, the planetary gear set can be shifted at an intermediate speed between the sun gear and the ring gear.

When the third driven gear portion and the ring gear are disconnected by the third clutch, an even-numbered forward speed change stage can be achieved.

When the third driven gear portion and the ring gear are connected by the third clutch, they may not be shifted in the planetary gear set.

When the third driven gear portion and the ring gear are connected by the third clutch, an odd-numbered forward speed change stage can be achieved.

And the third driven gear portion may be installed so as to be concentric with the output shaft.

According to the present invention, since the planetary gear set is connected to the third driven gear portion by the third clutch, the rotation speed of the output shaft and the third driven gear portion can be changed. Therefore, since the number of synchro parts and gears can be reduced while increasing the number of transmission stages, the overall length and weight of the transmission can be reduced.

Further, according to the present invention, the odd-numbered gear stages and the even-numbered gear stages are achieved as the third clutch connects and disconnects the third driven gear portion and the carrier. Therefore, since the speed change stage of the double speed is achieved by the operation of the third clutch, the structure of the speed change device can be simplified while increasing the speed change stage of the speed change device.

1 is a configuration diagram illustrating a transmission according to an embodiment of the present invention.
FIG. 2 is a table showing a control method of the transmission according to an embodiment of the present invention. FIG.
3 is a diagram showing a linear velocity of a transmission according to an embodiment of the present invention.
4 is a configuration diagram illustrating a transmission according to another embodiment of the present invention.

Hereinafter, embodiments of a transmission according to the present invention will be described with reference to the accompanying drawings. In the course of describing the transmission, the thickness of the lines and the size of the components shown in the drawings may be exaggerated for clarity and convenience of explanation. In addition, the terms described below are defined in consideration of the functions of the present invention, which may vary depending on the intention or custom of the user, the operator. Therefore, definitions of these terms should be made based on the contents throughout this specification.

1 is a configuration diagram illustrating a transmission according to an embodiment of the present invention.

Referring to FIG. 1, a transmission according to an embodiment of the present invention includes a first input shaft 10, a second input shaft 20, a first driven gear portion 30, a second driven gear portion 40, A third driven gear portion 60, a plurality of synchro portions 71, 72, and 73, and a planetary gear set 80.

The first input shaft 10 is connected to the power source by the first clutch Kl. A plurality of first driving gears (11) are connected to the first input shaft (10).

The second input shaft 20 is connected to the power source by the second clutch K2 and installed so as to be concentric with the first input shaft 10. A plurality of second driving gears 21 are connected to the second input shaft 20. The second drive gear 21 includes a third gear G3 and a seventh gear G7.

A plurality of first driven gears 31 are formed in the first driven gear portion 30 to be engaged with the first drive gear 11. The plurality of first driven gears 31 include a first gear G1 and a reverse gear GR.

The second driven gear portion 40 is formed with a plurality of second driven gears 41 to be engaged with the plurality of first drive gears 11. The plurality of second driven gears 41 include a fifth gear G5 and a ninth gear G9.

The output shaft 50 is connected to the first driven gear portion 30 and the second driven gear portion 40. At this time, the output shaft 50 is axially coupled to the first driven gear portion 30 and the second driven gear portion 40.

The third driven gear portion 60 is formed with a plurality of third driven gears 61 coupled to the plurality of second drive gears 21.

The synchronizing portions 71, 72, and 73 are disposed between the plurality of second drive gears 21, between the plurality of first driven gears 31, and between the plurality of second driven gears 41, respectively. The synchronizing portions 71, 72, and 73 are connected to the second driving gear 21, the first driven gear 31, and the second driven gear 41, respectively. That is, the synchromes 71, 72 and 73 are connected to the reverse gear GR, the first gear G1, the second gear, the fifth gear G5, the seventh gear G7 and the ninth gear G9 Respectively.

The planetary gear set 80 is connected to the output shaft 50 and is variably connected to the third driven gear portion 60 by the third clutch K3. The planetary gear set 80 is connected to the third driven gear portion 60 by the third clutch K3 so that the rotational speeds of the output shaft 50 and the third driven gear portion 60 can be changed. Therefore, the number of gears 71, 72, and 73 and the number of gears can be reduced while increasing the number of gearshifts, so that the overall length and weight of the transmission can be reduced.

The planetary gear set 80 includes a sun gear S connected to the output shaft 50, a carrier C meshed with the sun gear S, and a third driven gear portion 60 And a ring gear R connected to the ring gear R. The power transmitted to the output shaft 50 is output through the sun gear S and the carrier C. Further, the power transmitted to the third driven gear portion 60 is output through the ring gear R and the carrier C. The planetary gear set 80 shifts the rotation speed of the output shaft 50 and the third driven gear portion 60 and outputs the output.

And the third clutch K3 variably connects the third driven gear portion 60 and the carrier C. [ Therefore, when the third clutch K3 connects the third driven gear portion 60 and the carrier C, the ring gear R and the carrier C are rotated at the same speed. When the third clutch K3 releases the connection between the third driven gear portion 60 and the carrier C, as the ring gear R and the carrier C are engaged and rotated, the output shaft 50 and the third The rotational speed of the driven gear portion 60 is shifted.

When the third driven gear portion 60 and the carrier C are disconnected by the third clutch K3, the rotational speed of the third driven gear portion 60 and the output shaft 50 in the planetary gear set 80 becomes And is shifted at an intermediate speed between the sun gear S and the ring gear R.

At this time, when the third driven gear portion 60 and the carrier C are disconnected by the third clutch K3, an even-numbered forward speed change stage is achieved.

When the third driven gear portion 60 and the carrier C are connected by the third clutch K3, the rotational speed of the third driven gear portion 60 and the output shaft 50 Is not shifted. That is, the rotational speed input to the planetary gear set 80 becomes equal to the rotational speed output from the planetary gear set 80.

When the third driven gear portion 60 and the carrier C are connected by the third clutch K3, an odd forward speed change stage is achieved.

As described above, when the third clutch K3 disconnects the third driven gear portion 60 from the carrier C, an even-numbered gear stage is achieved, and the third clutch K3 is engaged with the third driven gear portion 60, And the carrier C are connected to each other. Therefore, since the speed change stage of the double speed is achieved by the operation of the third clutch K3, the structure of the speed change device can be simplified while increasing the speed change stage of the speed change device. As the structure of the transmission is simplified, the overall length and weight of the transmission can be reduced.

The rotation axis of the planetary gear set 80 is formed in parallel with the output shaft 50. Therefore, the length of the transmission can be reduced.

The transmission further includes a parking gear (90) connected to the rotational axis of the carrier (C). As the parking gear 90 is driven, the transmission is restrained and the vehicle can be parked.

A control method of the transmission according to an embodiment of the present invention will now be described.

FIG. 2 is a table showing a control method of a transmission according to an embodiment of the present invention, and FIG. 3 is a diagram showing a linear velocity of a transmission according to an embodiment of the present invention.

2 and 3, the first forward speed change stage is achieved by driving the first clutch K1 and the third clutch K3 and connecting the synchro section 71 to the first gear G1 . The power of the first input shaft 10 is transmitted to the first gear G1, the output shaft 50, the sun gear S and the carrier C. At this time, since the third clutch K3 restrains the third driven gear portion 60 and the carrier C, the rotational speed inputted to the planetary gear set 80 becomes equal to the output rotational speed.

The second forward speed change stage is achieved by driving the first clutch K1 and the second clutch K2 and connecting the synchromes 71 and 73 to the first gear G1 and the third gear G3 . The power of the first input shaft 10 is transmitted to the first gear G1, the output shaft 50, the sun gear S and the carrier C. The power of the second input shaft 20 is transmitted to the third gear G3, the third driven gear 61, the ring gear R, and the carrier C. At this time, since the third clutch K3 releases the restraint of the third driven gear portion 60 and the carrier C, the rotational speed output from the planetary gear set 80 is transmitted to the sun gear S and the ring gear R, .

The third forward speed change stage is achieved by driving the second clutch K2 and the third clutch K3 and connecting the synchro portion 73 to the third gear G3. The power of the second input shaft 20 is transmitted to the third gear G3, the third driven gear 61, the ring gear R, and the carrier C. At this time, since the third clutch K3 restrains the third driven gear portion 60 and the carrier C, the rotational speed inputted to the planetary gear set 80 becomes equal to the output rotational speed.

The fourth forward speed change stage is achieved by driving the first clutch K1 and the second clutch K2 while the synchromes 72 and 73 are connected to the third gear G3 and the fifth gear G5 . The power of the first input shaft 10 is transmitted to the fifth gear G5, the output shaft 50, the sun gear S, and the carrier C. The power of the second input shaft 20 is transmitted to the third gear G3, the third driven gear 61, the ring gear R, and the carrier C. At this time, since the third clutch K3 releases the restraint of the third driven gear portion 60 and the carrier C, the rotational speed output from the planetary gear set 80 is transmitted to the sun gear S and the ring gear R, .

The fifth forward speed change stage is achieved by the first clutch K1 and the third clutch K3 being driven and the synchromesh 72 being connected to the fifth gear G5. The power of the first input shaft 10 is transmitted to the fifth gear G5, the output shaft 50, the sun gear S, and the carrier C. At this time, since the third clutch K3 restrains the third driven gear portion 60 and the carrier C, the rotational speed inputted to the planetary gear set 80 becomes equal to the output rotational speed.

The sixth forward speed change stage is achieved by driving the first clutch K1 and the second clutch K2 while the synchromes 72 and 73 are connected to the fifth gear G5 and the seventh gear G7 . The power of the first input shaft 10 is transmitted to the fifth gear G5, the output shaft 50, the sun gear S, and the carrier C. The power of the second input shaft 20 is transmitted to the seventh gear G7, the third driven gear 61, the ring gear R, and the carrier C. At this time, since the third clutch K3 releases the restraint of the third driven gear portion 60 and the carrier C, the rotational speed output from the planetary gear set 80 is transmitted to the sun gear S and the ring gear R, .

The seventh forward speed change stage is achieved by driving the second clutch K2 and the third clutch K3 while the synchromesh 72 is connected to the seventh gear G7. The power of the second input shaft 20 is transmitted to the seventh gear G7, the output shaft 50, the sun gear S, and the carrier C. At this time, since the third clutch K3 restrains the third driven gear portion 60 and the carrier C, the rotational speed inputted to the planetary gear set 80 becomes equal to the output rotational speed.

The eighth forward speed change stage is achieved by driving the first clutch K1 and the second clutch K2 while the synchromes 72 and 73 are connected to the seventh gear G7 and the ninth gear G9 . The power of the first input shaft 10 is transmitted to the ninth gear G9, the output shaft 50, the sun gear S and the carrier C. The power of the second input shaft 20 is transmitted to the seventh gear G7, the third driven gear 61, the ring gear R, and the carrier C. At this time, since the third clutch K3 releases the restraint of the third driven gear portion 60 and the carrier C, the rotational speed output from the planetary gear set 80 is transmitted to the sun gear S and the ring gear R, .

The ninth forward speed change stage is achieved by driving the first clutch K1 and the third clutch K3 and connecting the synchromesh 72 to the ninth gear G9. The power of the first input shaft 10 is transmitted to the ninth gear G9, the output shaft 50, the sun gear S and the carrier C. At this time, since the third clutch K3 restrains the third driven gear portion 60 and the carrier C, the rotational speed inputted to the planetary gear set 80 becomes equal to the output rotational speed.

The reverse shift stage is achieved by the first clutch K1 and the third clutch K3 being driven and the synchro section 71 being connected to the reverse gear GR. The power of the first input shaft 10 is transmitted to the reverse gear GR, the output shaft 50, the sun gear S and the carrier C. [ At this time, since the third clutch K3 restrains the third driven gear portion 60 and the carrier C, the reverse shift stage is outputted in the planetary gear set 80. [

Next, the transmission according to another embodiment of the present invention will be described.

4 is a configuration diagram illustrating a transmission according to another embodiment of the present invention.

Referring to FIG. 4, the transmission according to another embodiment of the present invention includes a first input shaft 10, a second input shaft 20, a first driven gear portion 30, a second driven gear portion 40, A third driven gear portion 60, a plurality of synchro portions 71, 72, and 73, and a planetary gear set 80.

The second input shaft 20 is connected to the power source by the second clutch K2 and installed so as to be concentric with the first input shaft 10. A plurality of second driving gears 21 are connected to the second input shaft 20.

The output shaft 50 is connected to the first driven gear portion 30 and the second driven gear portion 40. At this time, the output shaft 50 is axially coupled to the first driven gear portion 30, the second driven gear portion 40, and the third driven gear portion 60.

The third driven gear portion 60 is formed with a plurality of third driven gears 61 coupled to the plurality of second drive gears 21. The plurality of third driven gears 61 include a third gear G3 and a seventh gear G7.

The synchronizing portions 71, 72 and 73 are disposed between the plurality of first driven gears 31, between the plurality of second driven gears 41, and between the plurality of third driven gears 61, respectively. The synchronizing portions 71, 72, and 73 are connected to the first driven gear 31, the second driven gear 41, and the third driven gear 61, respectively. In other words, the synchrosections 71, 72 and 73 are connected to the reverse gear GR, the first gear G1, the third gear G3, the fifth gear G5, the seventh gear G7, G9, respectively.

The planetary gear set 80 is connected to the output shaft 50 and is variably connected to the third driven gear portion 60 by the third clutch K3. The planetary gear set 80 is connected to the third driven gear portion 60 by the third clutch K3 so that the rotational speeds of the output shaft 50 and the third driven gear portion 60 can be changed. Therefore, the number of synchronizing portions 71, 72, 73 and the number of external gears can be reduced while increasing the number of speed shift stages, so that the overall length and weight of the transmission can be reduced.

The planetary gear set 80 includes a sun gear S connected to the output shaft 50, a carrier C meshed with the sun gear S, and a third driven gear portion 60 And a ring gear R connected to the ring gear R. The power transmitted to the output shaft 50 is output through the carrier C.

The third clutch K3 variably connects the third driven gear portion 60 and the ring gear R. [ Therefore, when the third clutch K3 connects the third driven gear portion 60 and the ring gear R, the ring gear R and the carrier C are rotated at the same speed. When the third clutch K3 releases the connection between the third driven gear portion 60 and the carrier C, as the ring gear R and the carrier C are engaged and rotated, the output shaft 50 and the third The rotational speed of the driven gear portion 60 is shifted.

When the third driven gear portion 60 and the ring gear R are disconnected by the third clutch K3, the rotational speed of the third driven gear portion 60 and the output shaft 50 Is shifted at an intermediate speed between the sun gear (S) and the ring gear (R).

At this time, when the third driven gear portion 60 and the ring gear R are disconnected by the third clutch K3, an even-numbered forward speed change stage is achieved.

When the third driven gear portion 60 and the ring gear R are connected by the third clutch K3, the rotational speeds of the ring gear R and the carrier C in the planetary gear set 80 are the same It becomes. That is, the rotational speed input to the planetary gear set 80 becomes equal to the rotational speed output from the planetary gear set 80.

When the third driven gear portion 60 and the ring gear R are connected by the third clutch K3, the odd forward speed change stage is achieved.

As described above, when the third clutch K3 disconnects the third driven gear portion 60 and the ring gear R, an even-numbered gear stage is achieved, and the third clutch K3 is engaged with the third driven gear portion 60 And the ring gear R are connected to each other, an odd-numbered gear stage is achieved. Therefore, since the speed change stage of the double speed is achieved by the operation of the third clutch K3, the structure of the speed change device can be simplified while increasing the speed change stage of the speed change device. As the structure of the transmission is simplified, the overall length and weight of the transmission can be reduced.

A control method of the transmission according to another embodiment of the present invention configured as described above will be described.

FIG. 2 is a table showing a control method of a transmission according to an embodiment of the present invention. FIG. 3 is a diagram showing a linear velocity of a transmission according to an embodiment of the present invention, FIG. 7 is a configuration diagram showing a transmission according to another embodiment of the present invention. FIG.

2 to 4, the first forward speed change stage is achieved by driving the first clutch K1 and the third clutch K3 and connecting the synchro section 71 to the first gear G1 . The power of the first input shaft 10 is transmitted to the first gear G1, the output shaft 50, the sun gear S and the carrier C. At this time, since the third clutch K3 restrains the third driven gear portion 60 and the ring gear R, the rotational speed inputted to the planetary gear set 80 becomes equal to the output rotational speed.

The second forward speed change stage is achieved by driving the first clutch K1 and the second clutch K2 and connecting the synchromes 71 and 73 to the first gear G1 and the third gear G3 . The power of the first input shaft 10 is transmitted to the first gear G1, the output shaft 50, the sun gear S and the carrier C. The power of the second input shaft 20 is transmitted to the third gear G3, the third driven gear 61, the ring gear R, and the carrier C. At this time, since the third clutch K3 releases the restraint of the third driven gear portion 60 and the ring gear R, the rotational speed output from the planetary gear set 80 is transmitted to the sun gear S and the ring gear R ). &Lt; / RTI >

The third forward speed change stage is achieved by driving the second clutch K2 and the third clutch K3 while the synchromesh 72 is connected to the third gear G3. The power of the second input shaft 20 is transmitted to the third gear G3, the third driven gear 61, the ring gear R, and the carrier C. At this time, since the third clutch K3 restrains the third driven gear portion 60 and the ring gear R, the rotational speed inputted to the planetary gear set 80 becomes equal to the output rotational speed.

The fourth forward speed change stage is achieved by driving the first clutch K1 and the second clutch K2 while the synchromes 72 and 73 are connected to the third gear G3 and the fifth gear G5 . The power of the first input shaft 10 is transmitted to the fifth gear G5, the output shaft 50, the sun gear S, and the carrier C. The power of the second input shaft 20 is transmitted to the third gear G3, the third driven gear 61, the ring gear R, and the carrier C. At this time, since the third clutch K3 releases the restraint of the third driven gear portion 60 and the ring gear R, the rotational speed output from the planetary gear set 80 is transmitted to the sun gear S and the ring gear R ). &Lt; / RTI >

The fifth forward speed change stage is achieved by the first clutch K1 and the third clutch K3 being driven and the synchromesh 72 being connected to the fifth gear G5. The power of the first input shaft 10 is transmitted to the fifth gear G5, the output shaft 50, the sun gear S, and the carrier C. At this time, since the third clutch K3 restrains the third driven gear portion 60 and the ring gear R, the rotational speed inputted to the planetary gear set 80 becomes equal to the output rotational speed.

The sixth forward speed change stage is achieved by driving the first clutch K1 and the second clutch K2 while the synchromes 72 and 73 are connected to the fifth gear G5 and the seventh gear G7 . The power of the first input shaft 10 is transmitted to the fifth gear G5, the output shaft 50, the sun gear S, and the carrier C. The power of the second input shaft 20 is transmitted to the seventh gear G7, the third driven gear 61, the ring gear R, and the carrier C. At this time, since the third clutch K3 releases the restraint of the third driven gear portion 60 and the ring gear R, the rotational speed output from the planetary gear set 80 is transmitted to the sun gear S and the ring gear R ). &Lt; / RTI >

The seventh forward speed change stage is achieved by driving the second clutch K2 and the third clutch K3 and connecting the synchro section 73 to the seventh gear G7. The power of the second input shaft 20 is transmitted to the seventh gear G7, the third driven gear 61, the ring gear R and the carrier C. [ At this time, since the third clutch K3 restrains the third driven gear portion 60 and the ring gear R, the rotational speed inputted to the planetary gear set 80 becomes equal to the output rotational speed.

The eighth forward speed change stage is achieved by driving the first clutch K1 and the second clutch K2 while the synchromes 72 and 73 are connected to the seventh gear G7 and the ninth gear G9 . The power of the first input shaft 10 is transmitted to the ninth gear G9, the output shaft 50, the sun gear S and the carrier C. The power of the second input shaft 20 is transmitted to the seventh gear G7, the third driven gear 61, the ring gear R, and the carrier C. At this time, since the third clutch K3 releases the restraint of the third driven gear portion 60 and the ring gear R, the rotational speed output from the planetary gear set 80 is transmitted to the sun gear S and the ring gear R ). &Lt; / RTI >

The ninth forward speed change stage is achieved by driving the first clutch K1 and the third clutch K3 and connecting the synchromesh 72 to the ninth gear G9. The power of the first input shaft 10 is transmitted to the ninth gear G9, the output shaft 50, and the sun gear S. At this time, since the third clutch K3 restrains the third driven gear portion 60 and the ring gear R, the rotational speed inputted to the planetary gear set 80 becomes equal to the output rotational speed.

The reverse shift stage is achieved by the first clutch K1 and the third clutch K3 being driven and the synchro section 71 being connected to the reverse gear GR. The power of the first input shaft 10 is transmitted to the reverse gear GR, the output shaft 50, and the sun gear S. At this time, since the third clutch K3 restrains the third driven gear portion 60 and the ring gear R, the reverse shift stage is output in the planetary gear set 80. [

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it will be understood by those of ordinary skill in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims. I will understand.

Accordingly, the true scope of protection of the present invention should be defined by the claims.

10: first input shaft 11: first drive gear
20: second input shaft 21: second drive gear
30: first driven gear unit 31: first driven gear
40: second driven gear portion 41: second driven gear
50: Output shaft 60: Third driven gear
71, 72, 73: Synchro part 80: Planetary gear set
90: parking gear S: sun gear
C: Carrier R: Ring gear
K1: first clutch K2: second clutch
K3: Third clutch G1: First gear
G3: Third gear G5: fifth gear
G7: Seventh gear G9: Ninth gear

Claims

A first input shaft connected to the power source by the first clutch and having a plurality of first drive gears connected thereto;
A second input shaft connected to a power source by a second clutch and provided so as to be concentric with the first input shaft and to which a plurality of second drive gears are connected;
A first driven gear portion having a plurality of first driven gears to be engaged with the first drive gear;
A second driven gear portion in which a plurality of second driven gears are formed to be coupled to the plurality of first drive gears;
An output shaft connected to the first driven gear portion and the second driven gear portion;
A third driven gear portion having a plurality of third driven gears coupled to the plurality of second drive gears;
A first drive gear, a second driven gear, a second driven gear, and a second driven gear, the second drive gear, the second driven gear, the first driven gear, A plurality of synchronizing units connected to the plurality of synchronizing units;
And a planetary gear set connected to the output shaft and variably connected to the third driven gear portion by a third clutch.

The method according to claim 1,
The planetary gear set includes:
A sun gear connected to the output shaft;
A carrier disposed to engage with the sun gear; And
And a ring gear provided to be engaged with the carrier and connected to the third driven gear portion.

3. The method of claim 2,
And the third clutch changes the third driven gear portion and the carrier.

The method of claim 3,
And when the third driven gear portion and the carrier are disconnected by the third clutch, the planetary gear set shifts at an intermediate speed between the sun gear and the ring gear.

The method of claim 3,
And when the third driven gear portion and the carrier are disconnected by the third clutch, an even-numbered forward speed change stage is achieved.

The method of claim 3,
And when the third driven gear portion and the carrier are connected by the third clutch, the transmission is not shifted in the planetary gear set.

The method of claim 3,
And when the third driven gear portion and the carrier are connected by the third clutch, an odd-numbered forward speed change stage is achieved.

3. The method of claim 2,
And the rotation axis of the planetary gear set is formed in parallel with the output shaft.

3. The method of claim 2,
And a parking gear connected to a rotation shaft of the carrier.

The method according to claim 1,
A first forward speed change stage achieved when the first clutch and the third clutch are driven and the synchro portion is connected to the first gear;
A second forward speed change stage achieved when the first clutch and the second clutch are driven and the synchro portion is connected to the first gear and the third gear;
A third forward speed change stage achieved when the second clutch and the third clutch are driven and the synchro portion is connected to the third gear;
A fourth forward speed change stage achieved when the first clutch and the second clutch are driven and the synchro portion is connected to the third gear and the fifth gear;
A fifth forward speed change stage achieved when the first clutch and the third clutch are driven and the synchro portion is connected to the fifth gear;
A sixth forward speed change stage achieved when the first clutch and the second clutch are driven and the synchro portion is connected to the fifth gear and the seventh gear;
A seventh forward speed change stage achieved when the second clutch and the third clutch are driven, and the synchro portion is connected to the seventh gear;
An eighth forward speed change stage achieved when the first clutch and the second clutch are driven and the synchro portion is connected to the seventh gear and the ninth gear;
A ninth forward speed change stage achieved when the first clutch and the third clutch are driven and the synchro portion is connected to the ninth gear;
And a reverse shift stage achieved when the first clutch and the third clutch are driven, and the synchro portion is connected to the reverse gear.

A first input shaft connected to the power source by the first clutch and having a plurality of first drive gears connected thereto;
A second input shaft connected to a power source by a second clutch and provided so as to be concentric with the first input shaft and to which a plurality of second drive gears are connected;
A first driven gear portion having a plurality of first driven gears to be engaged with the first drive gear;
A second driven gear portion in which a plurality of second driven gears are formed to be coupled to the plurality of first drive gears;
An output shaft connected to the first driven gear portion and the second driven gear portion;
A third driven gear portion having a plurality of third driven gears coupled to the plurality of second drive gears;
A first driven gear, a second driven gear, a third driven gear, and a third driven gear, wherein the first driven gear, the second driven gear, and the third driven gear are disposed between the plurality of first driven gears, between the plurality of second driven gears, Respectively;
And a planetary gear set connected to the output shaft and variably connected to the third driven gear portion by a third clutch.

12. The method of claim 11,
The planetary gear set includes:
A sun gear connected to the output shaft;
A carrier disposed to engage with the sun gear; And
And a ring gear provided to be engaged with the carrier and connected to the third driven gear portion.

13. The method of claim 12,
And the third clutch (C-3) is variable-connected to the third driven gear portion and the ring gear.

14. The method of claim 13,
And when the third driven gear portion and the ring gear are disconnected by the third clutch, the planetary gear set is shifted at an intermediate speed between the sun gear and the ring gear.

14. The method of claim 13,
And when the third driven gear portion and the ring gear are disconnected by the third clutch, an even-numbered forward speed change stage is achieved.

14. The method of claim 13,
And when the third driven gear portion and the ring gear are connected by the third clutch, they are not shifted in the planetary gear set.

14. The method of claim 13,
And when the third driven gear portion and the ring gear are connected by the third clutch, an odd-numbered forward speed change stage is achieved.

13. The method of claim 12,
And the third driven gear portion is provided so as to be concentric with the output shaft.

13. The method of claim 12,
And a parking gear connected to a rotation shaft of the carrier.

12. The method of claim 11,
A first forward speed change stage achieved when the first clutch and the third clutch are driven and the synchro portion is connected to the first gear;
A second forward speed change stage achieved when the first clutch and the second clutch are driven and the synchro portion is connected to the first gear and the third gear;
A third forward speed change stage achieved when the second clutch and the third clutch are driven and the synchro portion is connected to the third gear;
A fourth forward speed change stage achieved when the first clutch and the second clutch are driven and the synchro portion is connected to the third gear and the fifth gear;
A fifth forward speed change stage achieved when the first clutch and the third clutch are driven and the synchro portion is connected to the fifth gear;
A sixth forward speed change stage achieved when the first clutch and the second clutch are driven and the synchro portion is connected to the fifth gear and the seventh gear;
A seventh forward speed change stage achieved when the second clutch and the third clutch are driven, and the synchro portion is connected to the seventh gear;
An eighth forward speed change stage achieved when the first clutch and the second clutch are driven and the synchro portion is connected to the seventh gear and the ninth gear;
A ninth forward speed change stage achieved when the first clutch and the third clutch are driven and the synchro portion is connected to the ninth gear;
And a reverse shift stage achieved when the first clutch and the third clutch are driven, and the synchro portion is connected to the reverse gear.