reference will now be made in detail to various embodiments of the present invention ( s ), examples of which are illustrated in the accompanying drawings and described below . while the invention ( s ) will be described in conjunction with exemplary embodiments , it will be understood that present description is not intended to limit the invention ( s ) to those exemplary embodiments . on the contrary , the invention ( s ) is / are intended to cover not only the exemplary embodiments , but also various alternatives , modifications , equivalents and other embodiments , which may be included within the spirit and scope of the invention as defined by the appended claims . description of components that are not necessary for explaining the present exemplary embodiment will be omitted , and the same constituent elements are denoted by the same reference numerals in this specification . in the detailed description , ordinal numbers are used for distinguishing constituent elements having the same terms , and have no specific meanings . fig1 is a schematic diagram of a double clutch transmission according to various embodiments of the present invention . referring to fig1 , a double clutch transmission according to various embodiments of the present invention includes a variable connecting device provided with first and second clutches cl 1 and cl 2 , an input device provided with first and second input shafts is 1 and is 2 , a speed output device provided with first and second speed output units out 1 and out 2 converting rotation speed of power input through the input device according to each shift - speed and outputting the converted power , a first transfer gear assembly tga 1 and a second transfer gear assembly tga 2 . the first and second clutches cl 1 and cl 2 included in the variable connecting device selectively transmits torque of an engine eng to the first and second input shafts is 1 and is 2 . the first clutch c 1 selectively transmits the torque of the engine eng to the first input shaft is 1 and the second clutch cl 2 selectively transmits the torque of the engine eng to the second input shaft is 2 . the input device includes a first input shaft is 1 selectively connected to the engine eng through the first clutch cl 1 and a second input shaft is 2 selectively connected to the engine eng through the second clutch cl 2 . the second input shaft is 2 is a hollow shaft , and the first input shaft is 1 is inserted in the second input shaft is 2 without rotational interference with the second input shaft is 2 . first , second and third input gears g 1 , g 2 , and g 3 are disposed at an exterior circumference of the first input shaft is 1 with predetermined distances . the first , second and third input gears g 1 , g 2 , and g 3 are positioned at a rear portion of the first input shaft is 1 penetrating the second input shaft is 2 and are disposed in a sequence of the first , second and third input gears g 1 , g 2 , and g 3 . fourth and fifth input gears g 4 and g 5 are disposed on the second input shaft is 2 with a predetermined distance . the fourth input gear g 4 is disposed at a front portion of the second input shaft is 2 and the fifth input gear g 5 is disposed at a rear portion of the second input shaft is 2 . therefore , the first , second and third input gears g 1 , g 2 and g 3 as well as the first input shaft is 1 are rotated if the first clutch cl 1 is operated , and the fourth and fifth input gears g 4 and g 5 as well as the second input shaft is 2 are rotated if the second clutch cl 2 is operated . the first , second , third , fourth and fifth input gears g 1 , g 2 , g 3 , g 4 and g 5 are input gears operating at each shift - speed and teeth numbers thereof are determined according to target gear ratio at each shift - speed . the speed output device that changes rotation speed of the torque input through the input device and outputs the changed speed includes the first and second speed output units out 1 and out 2 disposed in parallel or substantially in parallel with the first and second input shafts is 1 and is 2 . the first speed output unit out 1 includes a first output shaft os 1 disposed in parallel with and away from the first and second input shafts is 1 and is 2 , third , fourth , sixth and seventh forward speed gears d 3 , d 4 , d 6 , and d 7 , a first synchronizer sl 1 selectively connecting the third forward speed gear d 3 or the seventh forward speed gear d 7 to the first output shaft os 1 , a second synchronizer sl 2 selectively connecting the fourth forward speed gear d 4 or the sixth forward speed gear d 6 to the first output shaft os 1 and a first output gear og 1 . the third forward speed gear d 3 is engaged with the fourth input gear g 4 and the seventh forward speed gear d 7 is engaged with the fifth input gear g 5 . in addition , the first synchronizer sl 1 includes a first hub gear h 1 fixedly disposed on the first output shaft os 1 , a first sleeve sle 1 meshed at an external circumference of the first hub gear h 1 and being slidable in an axial direction , a third forward speed clutch gear cg 3 integrally formed with the third forward speed gear d 3 and selectively engaged with the first sleeve sle 1 and a seventh forward speed clutch gear cg 7 integrally formed with the seventh forward speed gear d 7 and selectively engaged with the first sleeve sle 1 . if the first sleeve sle 1 is engaged with the third forward speed clutch gear cg 3 , rotation speed of the engine eng is changed according to gear ratios of the fourth input gear g 4 and the third forward speed gear d 3 and the changed rotation speed is output through the first output shaft os 1 and the first output gear og 1 . therefore , a third forward speed is achieved . in addition , if the first sleeve sle 1 is engaged with the seventh forward speed clutch gear cg 7 , the rotation speed of the engine eng is changed according to gear ratios of the fifth input gear g 5 and the seventh forward speed gear d 7 and the changed rotation speed is output through the first output shaft os 1 and the first output gear og 1 . therefore , a seventh forward speed is achieved . the fourth forward speed gear d 4 is engaged with the first input gear g 1 and the sixth forward speed gear d 6 is engaged with the third input gear g 3 . in addition , the second synchronizer sl 2 includes a second hub gear h 2 fixedly disposed on the first output shaft os 1 , a second sleeve sle 2 meshed at an external circumference of the second hub gear h 2 and being slidable in the axial direction , a fourth forward speed clutch gear cg 4 integrally formed with the fourth forward speed gear d 4 and selectively engaged with the second sleeve sle 2 and a sixth forward speed clutch gear cg 6 integrally formed with the sixth forward speed gear d 6 and selectively engaged with the second sleeve sle 2 . if the second sleeve sle 2 is engaged with the fourth forward speed clutch gear cg 4 , the rotation speed of the engine eng is changed according to gear ratios of the first input gear g 1 and the fourth forward speed gear d 4 and the changed rotation speed is output through the first output shaft os 1 and the first output gear og 1 . therefore , a fourth forward speed is achieved . in addition , if the second sleeve sle 2 is engaged with the sixth forward speed clutch gear cg 6 , the rotation speed of the engine eng is changed according to gear ratios of the third input gear g 3 and the sixth forward speed gear d 6 and the changed rotation speed is output through the first output shaft os 1 and the first output gear og 1 . therefore , a sixth forward speed is achieved . the power converted by the first speed output unit out 1 is transmitted to the first output gear og 1 mounted on a front end portion of the first output shaft os 1 to a final reduction gear fd of a differential apparatus diff . the second speed output unit out 2 includes an output shaft os 2 disposed in parallel with and away from the first and second input shafts is 1 and is 2 , the first transfer gear assembly tga 1 , second and fifth forward speed gears d 2 and d 5 , a third synchronizer sl 3 selectively connecting the second forward speed gear d 2 or the fifth forward speed gear d 5 to the second output shaft os 2 and a second output gear og 2 . the first transfer gear assembly tga 1 includes a first transfer gear shaft ts 1 being a hollow shaft and disposed at a radial exterior of the second output shaft os 2 , a first transfer input gear ti 1 disposed at a side portion of the first transfer gear shaft ts 1 and engaged with the fourth input gear g 4 and a first transfer output gear to 1 disposed at the other side portion of the first transfer gear shaft ts 1 . in addition , since a diameter of the first transfer input gear ti 1 is larger than that of the first transfer output gear to 2 , the rotation speed input to the first transfer input gear ti 1 is reduced through the first transfer output gear to 2 . in addition , the second forward speed gear d 2 is engaged with the second input gear g 2 and the fifth forward speed gear d 5 is engaged with the fifth input gear g 5 . the third synchronizer sl 3 includes a third hub gear h 3 fixedly disposed on the second output shaft os 2 , a third sleeve sle 3 engaged at an external circumference of the third hub gear h 3 and being slidable in the axial direction , a second forward speed clutch gear cg 2 integrally formed with the second forward speed gear d 2 and selectively engaged with the third sleeve sle 3 and a fifth forward speed clutch gear cg 5 integrally formed with the fifth forward speed gear d 5 and selectively engaged with the third sleeve sle 3 . if the third sleeve sle 3 is engaged with the second forward speed clutch gear cg 2 , the rotation speed of the engine eng is changed according to gear ratios of the second input gear g 2 and the second forward speed gear d 2 and the changed rotation speed is output through the second output shaft is 2 and the second output gear og 2 . therefore , a third forward speed is achieved . in addition , if the third sleeve sle 3 is engaged with the fifth forward speed clutch gear cg 5 , the rotation speed of the engine eng is changed according to gear ratios of the fifth input gear g 5 and the fifth forward speed gear d 5 and the changed rotation speed is output through the second output shaft os 2 and the second output gear og 2 . therefore , a fifth forward speed is achieved . the power converted by the second speed output unit out 2 is transmitted to the final reduction gear fd of the differential apparatus diff through the second output gear og 2 mounted at a front portion of the second output shaft os 2 . meanwhile , the second transfer gear assembly tga 2 changes direction and rotation speed of the power transmitted from the first transfer gear assembly tga 1 and outputs the changed power to the second output shaft os 2 . for this purpose , the second transfer gear assembly tga 2 includes a second transfer gear shaft ts 2 disposed in parallel with and away from the first and second input shafts is 1 and is 2 , a second transfer input gear ti 2 , a rotating direction changing device rc , a fourth synchronizer sl 4 , a second transfer output gear to 2 and a parking brake gear pg . the rotating direction changing device rc is integrally formed with an idle shaft ids being a hollow shaft and disposed on a radial exterior of the second transfer gear shaft ts 2 without rotational interference therebetween . the rotating direction changing device rc includes a second transfer input gear ti 2 formed at a side portion of the idle shaft ids and engaged with the first transfer output gear to 1 , a first sun gear s 1 integrally formed at the other side portion of the idle shaft ids , a second sun gear s 2 integrally formed with the second transfer gear shaft ts 2 and a carrier pc rotatably supporting a first pinion p 1 disposed at a radial exterior of the second transfer gear shaft ts 2 without rotational interference therebetween and engaged with the first sun gear s 1 and a second pinion p 2 engaged with the first pinion p 1 and the second sun gear s 2 . that is , the first sun gear s 1 engaged with the first pinion p 1 is directly connected to the second transfer input gear ti 2 so as to be operated as an input element , a second sun gear s 2 is operated as an output element that outputs a negative rotation speed at a reverse speed , and the carrier pc is operated as an output element at a first forward speed and is operated as a fixed element at the reverse speed . meanwhile , the fourth synchronizer sl 4 includes a fourth hub gear h 4 fixedly disposed on the carrier pc , a fourth sleeve sle 4 engaged at an external circumference of the fourth hub gear h 4 and being slidable in the axial direction , a first forward speed clutch gear cg 1 integrally formed with the second transfer gear shaft ts 2 at a side of the fourth hub gear h 4 and selectively engaged with the fourth sleeve sle 4 and a fixed clutch gear fc connected to a transmission housing h at the other side of the fourth hub gear h 4 and selectively engaged with the fourth sleeve sle 4 . if the fourth sleeve sle 4 is engaged with the first forward speed clutch gear cg 1 , the power transmitted from the carrier pc is output through the second transfer gear shaft ts 2 and the second transfer output gear to 2 . if the fourth sleeve sle 4 is engaged with the fixed clutch gear fc , the negative rotation speed transmitted from the second sun gear s 2 is output through the second transfer gear shaft ts 2 and the second transfer output gear to 2 . sleeves sle 1 , sle 2 , sle 3 and sle 4 applied respectively to the first , second , third and fourth synchronizers sl 1 , sl 2 , sl 3 and sl 4 are operated by additional actuators and the actuators are controlled by a transmission control unit . the actuator may be operated by an electric motor or a hydraulic control system but is not limited to this . fig2 is schematic diagram illustrating arrangement of shafts used in a double clutch transmission according to an exemplary embodiment of the present invention . referring to fig2 , the first and second input shafts is 1 and is 2 , the first and second output shafts os 1 and os 2 , the second transfer gear shaft ts 2 and the differential apparatus diff are disposed away from each other , and the first and second output gears og 1 and og 2 fixedly disposed respectively on the first and second output shafts os 1 and os 2 are connected to the final reduction gear fd of the differential apparatus diff . fig3 is a schematic diagram illustrating flow of power at the first forward speed in a double clutch transmission according to an exemplary embodiment of the present invention . odd - numbered speeds and even - numbered speeds are alternately realized at the second forward speed , the third forward speed , the fourth forward speed , the fifth forward speed , the sixth forward speed and the seventh forward speed other than the reverse speed and the first forward speed in the double clutch transmission according to some embodiments of the present invention . alternate realization of the odd - numbered speeds and the even - numbered speeds is known . therefore , detailed description thereof will be omitted . referring to fig3 , the power of the engine eng is transmitted to the second input shaft is 2 by operation of the second clutch c 2 , the third sleeve sle 3 of the third synchronizer sl 3 is engaged with the second forward speed clutch gear cg 2 , and the fourth sleeve sle 4 of the fourth synchronizer sl 4 is engaged with the first forward speed clutch gear cg 1 at the first forward speed . at this time , the rotation speed of the second input shaft is 2 is input to the first transfer gear assembly tga 1 as the negative rotation speed through the fourth input gear g 4 and the first transfer input gear ti 1 , and the negative rotation speed of the first transfer gear assembly tga 1 is input to the second transfer input gear ti 2 as positive rotation speed through the first transfer output gear to 1 and drives the first sun gear s 1 . at this time , the carrier pc is connected to the second transfer gear shaft ts 2 though the fourth hub gear h 4 , the fourth sleeve sle 4 and the first forward speed clutch gear cg 1 , and the second sun gear s 2 is engaged with the second pinion p 2 such that the rotating direction changing device rc becomes a direct - coupling state . therefore , the power input to the first sun gear s 1 is transmitted to the second transfer gear shaft ts 2 without change of the rotation speed . in this case the power of the second transfer gear shaft ts 2 is output to the differential apparatus diff through the second transfer output gear to 2 , the second forward speed gear d 2 , the second forward speed clutch gear cg 2 , the second output shaft os 2 , and the second output gear og 2 . at this time , speed ratio at the first forward speed is determined by gear ratios of the fourth input gear g 4 , the first transfer input gear ti 1 , the first transfer output gear to 1 , the second transfer input gear ti 2 , the second transfer output gear to 2 , and the second forward speed gear d 2 . fig4 is a schematic diagram illustrating flow of power at a reverse speed in a double clutch transmission according to an exemplary embodiment of the present invention . referring to fig4 , the power of the engine eng is transmitted to the second input shaft is 2 by operation of the second clutch cl 2 , the third sleeve sle 3 of the third synchronizer sl 3 is engaged with the second forward speed clutch gear cg 2 , and the fourth sleeve sle 4 of the fourth synchronizer sl 4 is engaged with the fixed clutch gear fc at the reverse speed . at this time , the rotation speed of the second input shaft is 2 is input to the transfer gear assembly tga 1 as the negative rotation speed through the fourth input gear g 4 and the first transfer input gear ti 1 , and the negative rotation speed of the first transfer gear assembly tga 1 is input to the second transfer input gear ti 2 as the positive rotation speed through the first transfer output gear to 1 and drives the first sun gear s 1 . at this time , since the fourth sleeve sle 4 is engaged with the fixed clutch gear fc , the carrier pc is operated as the fixed element and the first sun gear s 1 is operated as the input element in the rotating direction changing device rc . therefore , the negative rotation speed is output to the second sun gear s 2 . therefore , the second transfer gear shaft ts 2 fixedly connected to the second sun gear s 2 rotates inversely , and the negative rotation speed of the second transfer gear shaft ts 2 is output to the differential apparatus diff through the second transfer output gear to 2 , the second forward speed gear d 2 , the second forward speed clutch gear cg 2 , the second output shaft os 2 , and the second output gear og 2 . at this time , speed ratio at the reverse speed is determined by gear ratios of the fourth input gear g 4 , the first transfer input gear ti 1 , the first transfer output gear to 1 , the second transfer input gear ti 2 , the second transfer output gear to 2 , and the second forward speed gear d 2 . meanwhile , the parking brake gear pg is disposed at a front end portion of the second transfer gear shaft ts 2 and performs parking function . according to various embodiments of the present invention , the first transfer gear assembly tga 1 including one synchronizer sl 3 , two speed gears , and two gears is disposed on the second output shaft os 2 , and the rotating direction changing device rc , one synchronizer sl 4 , and two gears are disposed on the second transfer gear shaft ts 2 disposed in parallel with the second output shaft os 2 . therefore , a length of the transmission may be shortened . thereby , the transmission can be mounted in an engine compartment without layout change of the engine compartment . in addition , since the layout of the engine compartment is not changed , cost may be curtailed . for convenience in explanation and accurate definition in the appended claims , the terms “ front ” or “ rear ”, and etc . are used to describe features of the exemplary embodiments with reference to the positions of such features as displayed in the figures . the foregoing descriptions of specific exemplary embodiments of the present invention have been presented for purposes of illustration and description . they are not intended to be exhaustive or to limit the invention to the precise forms disclosed , and obviously many modifications and variations are possible in light of the above teachings . the exemplary embodiments were chosen and described in order to explain certain principles of the invention and their practical application , to thereby enable others skilled in the art to make and utilize various exemplary embodiments of the present invention , as well as various alternatives and modifications thereof . it is intended that the scope of the invention be defined by the claims appended hereto and their equivalents .