DE102011080565A1 - Input group for gear-wheel changing gear for use in vehicles, particularly tractors, has main group and gear optionally carried out as high speed gear or as creep speed gear, which has input shaft and counter shaft - Google Patents

Abstract

The input group (2) has a main group (3) and a gear (20) optionally carried out as a high speed gear or as a creep speed gear. The gear has an input shaft (5), a counter shaft (6) formed parallel to the input shaft and another counter shaft (7) arranged parallel to the input shaft. The power shift double clutches (A,C) are arranged on the input shaft and on the two countershafts. The clutch bells (8,9,10) of the double clutches are provided with each other directly or indirectly in an engagement through external toothings (11,12,13).

Description

The present invention relates to an input group of a gear change transmission, in particular a change-speed gearbox for tractors and tractor vehicles, according to the preamble of patent claim 1.

From the DE 40 20 558 A1 The applicant is a multi-stage change gear known. Here, an intermediate gear is arranged between an input group and a main group, wherein a double gear forms an additional overdrive (overdrive). This gear change transmission is particularly suitable for use in agricultural and / or construction motor vehicles used, for example in tractors and tractor vehicles.

The known transmission comprises a starting clutch, serving as a range group main group with synchronous clutches and one of the range group upstream input group, which serves as a split group, wherein a first countershaft of the input group is arranged axially aligned with a drive shaft of the main group and wherein a main drive shaft relative to the first countershaft in parallel staggered and can be coupled with a power take-off shaft.

Furthermore, it is provided that axially between a first housing intermediate wall on the output side of the input group and of the starting clutch, an intermediate gear is provided, wherein the intermediate gear is preferably designed as a high-speed gearbox or crawler gear.

Another genus same gear comes from the EP 0 481 014 B1 the applicant. It describes a multi-stage gear change transmission with a starting clutch and multiple gear groups in countershaft design, of which a coarse-stage main group with synchronous clutches as a range group for selecting the desired speed range and one of these upstream, fine-scale input group serve as a splitter group for fine tuning the speeds within a speed range, wherein a first countershaft the input group is axially aligned with a drive shaft of the main group and wherein a main drive and an input shaft relative to the first countershaft offset arranged in parallel and are drivingly coupled with a power take-off shaft.

In the known transmission it is provided that the main drive shaft is guided past the main group and the PTO shaft is provided in the region of the housing rear side of the transmission, that the starting clutch is arranged spatially and instinctively between the first countershaft and the drive shaft and that the starting clutch comprises a forced oil-cooled disk set, in which the oil flow can be switched off when the starting clutch is open. Here are four forward power shift gears and four reverse power shift gears feasible.

From the DE 10 2009 000 778 A1 The applicant is a gear change transmission, comprising an input group serving as a splitter group, a main group and optionally one between the splitter group and the main group switched intermediate gear, wherein the input group an input shaft arranged parallel to the input shaft and the output of the input group forming first countershaft and a second comprises a countershaft arranged parallel to the input shaft and serving as reverse shaft for the realization of the reverse drive, wherein in each case a power-shiftable double multi-plate clutch is arranged on the input shaft and on the two countershafts. Here are the clutch bell of the double clutches on external gears with each other directly or indirectly engaged.

Furthermore, according to the DE 10 2009 000 778 A1 provided that the transmission comprises a third parallel to the input shaft arranged countershaft on which a multi-plate clutch and a fixed gear are arranged and that on the drive side in front of the arranged on the input shaft dual clutch connected to the inner disk carrier of the first clutch of the double clutch fixed wheel is arranged with a arranged on the first countershaft and connected to the inner disk carrier of the first clutch of the arranged on the first countershaft double clutch idler gear is engaged.

The intermediate gear can be designed as a creeper or as overdrive gearbox; with the transmission according to the DE 10 2009 000 778 A1 Six forward powershift gears and at least three reverse powershift gears are feasible.

The present invention has for its object, starting from a multi-stage change-speed gearbox according to the EP 0 481 014 B1 the Applicant an input group of a gear change transmission comprising an input group, a main group and optionally a preferably between the input group and the main group switched gearbox, which is designed as overdrive gear or creeper, specify, in which in the input group in a compact design at least six powershift forward and at least six powershift reverse gears can be realized.

This object is solved by the features of patent claim 1. Further embodiments and advantages of the invention will become apparent from the dependent claims.

Accordingly, an input group of a change-speed gearbox comprising an input group, a main group and optionally a preferably between the input group and the main group switched, designed as overdrive gear or creep gear proposed transmission, which an input shaft, a parallel to the input shaft arranged, the output of the input group forming first countershaft and a second arranged parallel to the input shaft second countershaft, wherein on the input shaft and on the two countershafts each a load-shiftable dual clutch is arranged, and wherein the clutch bells of the double clutches via external gears are directly or indirectly engaged.

The drive side in front of the arranged on the input shaft dual clutch is arranged with a fixed gear of the second countershaft fixed gear, wherein on the input shaft in front of the inner disk carrier of the first clutch of the double clutch of the input shaft, a further fixed wheel is arranged, which arranged with a on the first countershaft and with the idler carrier of the first clutch of the double clutch mounted on the first countershaft is engaged. By closing the first clutch of the arranged on the first countershaft double clutch this idler gear rotatably connected to the clutch bell of this dual clutch, wherein closing the second clutch arranged on the first countershaft double clutch causes a rotationally fixed connection of the clutch bell of this double clutch with the first countershaft.

It is further provided that arranged on the input shaft dual clutch is connected downstream of a connected to the inner disk carrier of the second clutch of this dual clutch idler gear, said idler gear is arranged with a on the first countershaft on the output side of the dual clutch fixed gear engaged, closing by closing the second clutch arranged on the input shaft dual clutch this idler gear rotatably connected to the clutch bell disposed on the input shaft dual clutch and wherein closing the first clutch arranged on the input shaft dual clutch causes a rotationally fixed connection of the clutch bell of this dual clutch with the input shaft.

Here, a further fixed gear is arranged on the first countershaft, which is connected to a arranged with the inner disk carrier of the second clutch arranged on the second countershaft double clutch idler gear engaged by closing the second clutch arranged on the second countershaft dual clutch this idler gear rotatably the clutch bell of the arranged on the second countershaft dual clutch is connectable and wherein a closing of the first clutch arranged on the second countershaft double clutch causes a rotationally fixed connection of the clutch bell of this double clutch with the second countershaft.

According to the invention, a third countershaft is provided on which a first power-shift clutch is arranged, wherein closing this clutch causes a rotationally fixed connection of the clutch bell of this clutch with the third countershaft, wherein the clutch bell of this clutch via an external toothing with the outer toothing of the clutch bell arranged on the input shaft dual clutch is engaged and wherein the third countershaft has a fixed gear, which meshes with the arranged on the first countershaft on the output side of the dual clutch fixed gear.

By selectively intervening the seven powershift clutches, six load-shiftable forward and six powershift reverse gears can be implemented in the input group.

As part of a further development of the invention, a further power shift clutch is arranged on the third countershaft, which brings together with the powershift clutch whose closing causes a rotationally fixed connection of the clutch bell with the third countershaft to form a double clutch, wherein arranged on the third countershaft a idler gear is, which meshes with an additional fixed gear of the input shaft, said idler gear is connected to the inner disk carrier of the further clutch arranged on the third countershaft double clutch and by closing the other clutch of this dual clutch rotation with the clutch bell of the double clutch is connectable.

By this design of the input group eight power shift forward and eight power shift reverse gears can be realized.

The main group downstream of the input group is designed according to the prior art and can have several gears which can be shifted by means of synchronous clutches.

The invention will be explained in more detail below by way of example with reference to the attached figures. Show it:

1 a schematic view of a preferred embodiment of a gear change transmission according to the invention;

2 : A table illustrating advantageous numbers of teeth for the gears involved in gear ratios of the input group of the transmission after 1 ;

3 : a table illustrating the implementation of the forward and reverse gears in the input section of the transmission to 1 require couplings;

4 a schematic view of another embodiment of the input group of a gear change transmission according to the invention;

5 a schematic view of a further preferred embodiment of a gear change transmission according to the invention;

6 : A table illustrating advantageous numbers of teeth for the gears involved in gear ratios of the input group of the transmission according to 5 ; and

7 FIG. 4 is a table illustrating how to realize the forward and reverse gears in the input section of the transmission according to FIG 5 need couplings.

Gear change gears are well known to those skilled in the art, so that in the description of the figures, only the components relevant to the invention are described and explained in detail.

In 1 is a gear change transmission according to the invention 1 shown. It includes an input group 2 , which serves as a splitter group, an intermediate gearbox 20 and a main group 3 ,

The entrance group 2 includes an input shaft 5 , one parallel to the input shaft 5 arranged first countershaft 6 and a second parallel to the input shaft 5 arranged second countershaft 7 ,

How out 1 It can be seen on the input shaft 5 and on the two countershafts 6 . 7 in each case a power shift double clutch A, B, C arranged. The on the input shaft 5 arranged dual clutch A includes the clutches K1, K2, on the first countershaft 6 arranged dual clutch B, the clutches K3, K4 and on the second countershaft 7 arranged dual clutch C includes the clutches K5 and K6. According to the invention, the clutch bells are 8th . 9 . 10 the double clutches A, B, C on external gears 11 . 12 . 13 engaged with each other directly or indirectly. Here is the clutch bell 8th with the clutch bells 9 and 10 engaged, with the clutch bell 9 with the clutch bell 10 not engaged.

Here is the input group 2 designed such that the drive side in front of the on the input shaft 5 arranged dual clutch A a with a fixed wheel 14 the second countershaft 7 combing wheel 4 is arranged, being on the input shaft 5 in front of the inner disk carrier of the first clutch K1 of the dual clutch A a fixed gear 15 is arranged, which with one on the first countershaft 6 arranged and with the inner disk carrier of the first clutch K3 on the first countershaft 6 arranged dual clutch B connected idler gear 65 engaged.

By closing the clutch K3 is the idler gear 65 rotatably with the clutch bell 9 the double clutch B connectable, wherein a closing of the clutch K4 a rotationally fixed connection of the clutch bell 9 the double clutch B with the first countershaft 6 causes.

In addition, it is provided that on the input shaft 5 arranged dual clutch A a with the inner disc carrier of the second clutch K2 of the dual clutch A connected idler gear 16 is downstream, with the idler gear 16 with one on the first countershaft 6 output side of the double clutch B arranged fixed wheel 17 engaged. By closing the clutch K2 is the idler gear 16 rotatably with the clutch bell 8th the double clutch A connectable, wherein a closing of the clutch K1 a rotationally fixed connection of the clutch bell 8th the double clutch A with the input shaft 5 causes.

Further, on the first countershaft 6 another festival bike 18 arranged with one with the inner disc carrier of the second clutch K6 on the second countershaft 7 arranged dual clutch C connected idler gear 19 engaged. By closing the clutch K6 is the idler gear 19 rotatably with the clutch bell 10 the double clutch C connectable, wherein a closing of the clutch K5 a rotationally fixed connection of the clutch bell 10 the double clutch C with the second countershaft 7 causes.

The already described components of the input group 2 correspond to the prior art according to the EP 0 481 014 B1 the applicant. According to the invention, the input group 2 To realize the realization of eight power-shiftable forward and eight power-shiftable reverse gears in the input group 2 to enable.

For this purpose, according to the invention, a third countershaft 59 provided, which a loose wheel 60 includes that with an additional fixed wheel 61 the input shaft 5 meshes, taking on the third countershaft 59 a further power shift double clutch D, comprising two clutches K7 and K8 is arranged. The idler wheel 60 is connected to the inner disk carrier of the clutch K7 and by closing the clutch K7 of the dual clutch D rotatably with the clutch bell 62 the double clutch D connectable, with a closing of the clutch K8 of the dual clutch D a rotationally fixed connection of the clutch bell 62 with the third countershaft 59 causes.

Furthermore, there is the clutch bell 62 over an external toothing 63 with the external teeth 11 the clutch bell 8th the double clutch A in engagement, wherein the third countershaft 59 a festival bike 64 which, with that on the first countershaft 6 arranged fixed wheel 17 combs.

Through this extension of the input group 2 Eight power shiftable forward and eight power shift reverse gears can be realized. A geometric increment in the input group, for example, by the in 2 shown numbers of teeth for the involved gears 4 . 11 . 12 . 14 . 15 . 16 . 17 . 18 . 19 . 60 . 61 . 63 . 64 and 65 be achieved, wherein the corresponding circuit diagram is the subject of Figure 3.

Accordingly, the first forward speed results in the input group 2 by closing the clutches K1 and K2, the second forward speed by closing the clutches K2 and K7, the third forward speed by closing the clutches K2 and K5, the fourth forward speed by closing the clutches K2 and K3, the fifth forward speed by closing the clutches K1 and K4, the sixth forward speed by closing the clutches K4 and K7, the seventh forward speed by closing the clutches K4 and K5 and the eighth forward speed is obtained by closing the clutches K3 and K4.

Furthermore, there is the first reverse gear in the input group 2 by closing the clutches K1 and K8, the second reverse by closing the clutches K7 and K8, the third reverse by closing the clutches K5 and K8, the fourth reverse by closing the clutches K3 and K8, the fifth reverse by closing the clutches K1 and K6, the sixth reverse by closing the clutches K6 and K7, the seventh reverse by closing the clutches K5 and K6 and the eighth reverse, is obtained by closing the clutches K3 and K6.

The numbers of teeth can in principle be chosen freely, resulting in different combinations depending on the number of teeth for the necessary to realize the individual gears clutches. Furthermore, further wheel planes or spur gear stages can be integrated to realize further translations into the input group.

According to the invention, the powershift clutches of the input group 2 as starting elements of the transmission 1 serve. Furthermore, it is possible at any suitable point in the input group 2 Provide freewheels, for example, between a shaft and the housing or between two waves. In addition, an electric machine or a further drive unit can be arranged on each shaft.

At the in 1 the example shown forms the first countershaft 6 the input group 2 the output of the input group 2 , When viewed in the direction of power flow in train operation between the input group 2 and the main group 3 a gearbox designed as a crawler gear group 20 is arranged. As an alternative to the crawler gear group, an overdrive group may be provided within the scope of further embodiments.

The intermediate gear 20 includes one with the first countershaft 6 connected fixed wheel 21 , which with a fixed wheel 22 a fourth countershaft 23 meshes with the fourth countershaft 23 another festival bike 24 having, which with a loose wheel 25 the downforce 26 of the intermediate gear 20 engaged. By pressing a switching element 27 You can choose the fixed wheel 21 or the idler gear 25 with the downforce 26 of the intermediate gear 20 releasably connected, whereby a 1: 1 transmission of the torque to the output 26 of the intermediate gear 20 or a transmission of the torque can be achieved with a high translation.

In the context of further embodiments, the intermediate gear in the direction of power flow in the train operation considered after the main group 3 or in front of the entrance group 2 be arranged.

The main group shown 3 is carried out according to the prior art. Within the scope of further embodiments, the main group may be designed in accordance with further embodiments known from the prior art. By closing the starting clutch 28 is the input shaft 29 of the main group 3 with the downforce 26 of the intermediate gear 20 or in the event that no intermediate gear is provided, with the second countershaft 7 the input group 2 connectable.

The main group 3 includes the input shaft 29 , on the two double synchronizer clutches 30 . 31 are arranged over the two loose wheels 32 . 33 respectively. 34 . 35 with the input shaft 29 optionally rotatably connected, wherein the loose wheels 32 . 33 . 34 . 35 with one each on a parallel to the input shaft 29 arranged fifth countershaft 36 arranged fixed wheel 37 . 38 . 39 . 40 comb. The fifth countershaft 36 forms the output of the gearbox 1 ,

By operating the double synchronizer clutches 30 . 31 will be four different translations in the main group 3 realized.

How out 1 seen, are on the fifth countershaft 36 two loose wheels 41 . 42 arranged, which by means of a double synchronizer clutch 43 optionally with the fifth countershaft 36 are connectable, with the Lösräder 41 . 42 with one each on the input shaft 29 the main group 3 arranged fixed wheel 44 . 45 engage. By operating the double synchronizer clutch 43 will be two more translations in the main group 3 realized, so that in the main group 3 six courses are feasible.

As a result, with the transmission according to the invention without an intermediate gear 20 forty-eight forward gears and forty-eight reverse gears are realized because in the input group 2 eight powershift gears can be achieved per direction of travel.

In 1 is with the reference numeral 46 one with the output of the transmission 1 forming fifth countershaft 36 Connected differential called, which with brakes 47 . 48 provided rear axle shafts 49 . 50 drives. In 1 is a wheel 52 the rear axle shown, which via a planetary gear 51 is driven.

The drive shaft of the front axle is in 1 with the reference number 56 Mistake. It is over a spur gear stage 57 and a clutch 58 with the output of the transmission 1 forming fifth countershaft 36 connectable if the front axle drive is to be switched on.

In the example shown, the pump 53 of the transmission 1 over the input shaft 5 over two spur gears 54 . 55 driven.

Subject of the 4 is a variant of the input group 2 that differ from the in 1 shown input group 2 thereby distinguishes that the fixed wheel 4 deleted, with its functionality by the fixed wheel 61 is taken, which with the fixed wheel 14 the second countershaft 7 and with that on the third countershaft 59 arranged loose wheel 60 combs.

According to one embodiment of the invention further gears can also be used several times, so that for example on the first countershaft 6 arranged fixed wheel 17 can be omitted, in which case the idler gear 16 the input shaft 5 with the fixed wheel 18 the first countershaft 6 meshes with one with the inner disk carrier of the second clutch K6 on the second countershaft 7 arranged dual clutch C connected idler gear 19 engaged.

As a result, gears can be saved, which has a positive effect on the manufacturing and assembly costs.

This in 5 The embodiment shown differs from the exemplary embodiment 1 in that the clutch K7 is omitted, resulting in lower manufacturing and assembly costs in the input group 2 six powershift forward and six powershift reverse gears are shiftable. This also eliminates the fixed wheel 61 and the idler gear 60 ,

The embodiment according to 1 results from the embodiment according to 5 in that on the third countershaft 59 a further power-shift clutch K7 is arranged, with the power-shiftable clutch K8, the closing of a rotationally fixed connection of the clutch bell 62 with the third countershaft 59 causes, is summarized to a double clutch D, being on the third countershaft 59 a loose wheel 60 is arranged, with an additional fixed wheel 61 the input shaft 5 meshes and by closing the other clutch K7 of the double clutch D rotatably with the clutch bell 62 the double clutch D is connectable.

A geometric increment in the input group 2 can at the in 5 shown gear 1 for example, by the in 6 shown numbers of teeth for the involved gears 4 . 11 . 12 . 14 . 15 . 16 . 17 . 18 . 19 . 63 . 64 and 65 be achieved; the corresponding circuit diagram is the subject of 7 ,

Accordingly, the first forward speed results in the input group 2 by closing the clutches K5 and K2, the second forward speed by closing the clutches K5 and K4, the third forward speed by closing the clutches K1 and K2, the fourth forward speed by closing the clutches K1 and K4, the fifth forward speed by closing the clutches K2 and K3 and the sixth forward speed is obtained by closing the clutches K3 and K4.

Furthermore, there is the first reverse gear in the input group 2 by closing the clutches K5 and K6, the second reverse by closing the clutches K5 and K8, the third reverse by closing the clutches K1 and K6, the fourth reverse by closing the clutches K1 and K8, the fifth reverse by closing the clutches K3 and K6, wherein the sixth reverse gear results by closing the clutches K3 and K8.

The concept of the invention, a transmission is provided, the input group has at least six powersupply forward and at least six powershift reverse gears, so that no additional reverse gear for the realization of the reverse gears is required. For example, due to the high number of gears in the input group, two gears of the main group can be eliminated, resulting in a reduction of the cost.

Of course, also falls any structural design, especially any spatial arrangement of the components of the transmission in itself and to one another and as far as technically feasible, within the scope of the present claims, without affecting the function of the transmission, as specified in the claims, even if these training are not explicitly shown in the figures or in the description.

LIST OF REFERENCE NUMBERS

1

Gear shift transmission

2

input group

3

main group

4

fixed gear

5

input shaft

6

first countershaft

7

second countershaft

8th

Kupplungsglocke

9

Kupplungsglocke

10

Kupplungsglocke

11

External toothing of the clutch bell 8th

12

External toothing of the clutch bell 9

13

External toothing of the clutch bell 10

14

fixed gear

15

fixed gear

16

Losrad

17

fixed gear

18

fixed gear

19

Losrad

20

intermediate gear

21

fixed gear

22

fixed gear

23

fourth countershaft

24

fixed gear

25

Losrad

26

Output of the intermediate gear 20

27

switching element

28

clutch

29

Input shaft of the main group 3

30

synchronous clutch

31

synchronous clutch

32

Losrad

33

Losrad

34

Losrad

35

Losrad

36

fifth countershaft

37

fixed gear

38

fixed gear

39

fixed gear

40

fixed gear

41

Losrad

42

Losrad

43

synchronous clutch

44

fixed gear

45

fixed gear

46

differential

47

brake

48

brake

49

rear axle shaft

50

rear axle shaft

51

planetary gear

52

Wheel of the rear axle

53

pump

54

spur gear

55

spur gear

56

Drive shaft of the front axle

57

spur gear

58

clutch

59

third countershaft

60

Losrad

61

fixed gear

62

Kupplungsglocke

63

External toothing of the clutch bell 62

64

fixed gear

65

Losrad

K1

 clutch

K2

 clutch

K3

 clutch

K4

 clutch

K5

 clutch

K6

 clutch

K7

 clutch

K8

 clutch

A

 Double coupling

B

 Double coupling

C

 Double coupling

D

 Double coupling

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 4020558 A1 [0002]
• EP 0481014 B1 [0005, 0010, 0037]
• DE 102009000778 A1 [0007, 0008, 0009]

Claims (6)

Input group ( 2 ) of a gear change transmission ( 1 ), comprising an input group ( 2 ), a main group ( 3 ) and optionally an overdrive or creeper type transmission ( 20 ), which has an input shaft ( 5 ), one parallel to the input shaft ( 5 ), the output of the input group ( 2 ) forming the first countershaft ( 6 ) and a second parallel to the input shaft ( 5 ) second countershaft ( 7 ), wherein on the input shaft ( 5 ) and on the two countershafts ( 6 . 7 ) in each case a power-shiftable double clutch (A, B, C) is arranged, wherein the clutch bell ( 8th . 9 . 10 ) of the double clutches via external gearing ( 11 . 12 . 13 ) are engaged with each other directly or indirectly, with the drive side in front of the on the input shaft ( 5 ) arranged dual clutch (A) with a fixed wheel ( 14 ) of the second counter-wave ( 7 ) combing fixed wheel ( 4 ) is arranged and on the input shaft ( 5 ) in front of the inner disk carrier of the first clutch (K1) of the double clutch (A) another fixed gear ( 15 ) arranged with one on the first countershaft ( 6 ) and with the inner disk carrier of the first clutch (K3) of the first countershaft ( 6 ) arranged double clutch (B) connected loose wheel ( 65 ) is engaged, wherein by closing the first clutch (K3) on the first countershaft ( 6 ) arranged double clutch (B) the idler gear ( 65 ) rotatably with the clutch bell ( 9 ) of the dual clutch (B) is connectable, wherein a closing of the second clutch (K4) of the on the first countershaft ( 6 ) arranged double clutch (B) a rotationally fixed connection of the clutch bell ( 9 ) of the double clutch (B) with the first countershaft ( 6 ) is effected, wherein the on the input shaft ( 5 ) arranged double clutch (A) connected to the inner disk carrier of the second clutch (K2) of the double clutch (A) idler gear ( 16 ), which is connected to one on the first countershaft ( 6 ) on the output side of the double clutch (B) fixed wheel ( 17 ) is engaged, wherein by closing the second clutch (K2) of the on the input shaft ( 5 ) arranged double clutch (A) the idler gear ( 16 ) rotatably with the clutch bell ( 8th ) of the double clutch (A) is connectable, wherein a closing of the first clutch (K1) of the on the input shaft ( 5 ) arranged double clutch (A) a non-rotatable connection of the clutch bell ( 8th ) of the double clutch (A) with the input shaft ( 5 ), whereby on the first countershaft ( 6 ) another fixed wheel ( 18 ) arranged with one with the inner disk carrier of the second clutch (K6) of the second countershaft ( 7 ) arranged double clutch (C) connected loose wheel ( 19 ), which by closing the second clutch (K6) on the second countershaft ( 7 ) arranged double clutch (C) rotatably with the clutch bell ( 10 ) of the double clutch (C) is connectable, wherein a closing of the first clutch (K5) of the second countershaft ( 7 ) arranged double clutch (C) a non-rotatable connection of the clutch bell ( 10 ) of the double clutch (C) with the second countershaft ( 7 ), characterized in that a third countershaft ( 59 ) is provided, on which a power shift clutch (K8) is arranged, wherein a closing of this clutch (K8) a rotationally fixed connection of the clutch bell ( 62 ) of this clutch (K8) with the third countershaft ( 59 ), wherein the clutch bell ( 62 ) of this coupling (K8) via an external toothing ( 63 ) with the external toothing ( 11 ) the clutch bell ( 8th ) on the input shaft ( 5 ) arranged double clutch (A) is engaged and wherein the third countershaft ( 59 ) a fixed wheel ( 64 ), which coincides with that on the first countershaft ( 6 ) on the output side of the double clutch (A) arranged fixed wheel ( 17 ) combs. Input group ( 2 ) of a gear change transmission ( 1 ) according to claim 1, characterized in that in the input group ( 2 ), six forward-shifting powers and six powershifting reverse speeds can be realized, the first forward speed by closing the clutches (K5) and (K2), the second forward speed by closing the clutches (K5) and (K4), the third forward speed by closing the Clutches (K1) and (K2), the fourth forward gear by closing the clutches (K1) and (K4), the fifth forward by closing the clutches (K2) and (K3), the sixth forward by closing the clutches (K3 ) and (K4) and wherein the first reverse gear by closing the clutches (K5) and (K6), the second reverse by closing the clutches (K5) and (K8), the third reverse by closing the clutches (K1) and (K6), the fourth reverse by closing the clutches (K1) and (K8), the fifth reverse by closing the clutches (K3) and (K6), and the sixth reverse by closing the couplings (K3) and (K8). Input group ( 2 ) of a gear change transmission ( 1 ), according to claim 1, characterized in that on the third countershaft ( 59 ) a further power shift clutch (K7) is arranged, which with the power shift clutch (K8), the closing of a rotationally fixed connection of the clutch bell ( 62 ) with the third countershaft ( 59 ) is combined into a double clutch (D), wherein on the third countershaft ( 59 ) a loose wheel ( 60 ) arranged with an additional fixed wheel ( 61 ) of the input shaft ( 5 ) meshes and by closing the other clutch (K7) of the double clutch (D) rotatably with the clutch bell ( 62 ) of the double clutch (D) is connectable. Input group ( 2 ) of a gear change transmission ( 1 ), according to claim 3, characterized in that in the input group ( 2 ) eight power shift forward and eight power shift reverse gears are feasible, with the first forward by closing the clutches (K1) and (K2), the second forward by closing the clutches (K2) and (K7), the third forward by closing the Couplings (K2) and (K5), the fourth forward gear by closing the clutches (K2) and (K3), the fifth forward by closing the clutches (K1) and (K4), the sixth forward by closing the clutches (K4) and (K7), the seventh forward speed by closing the clutches (K4) and (K5), and the eighth forward speed being obtained by closing the clutches (K3) and (K4), and the first reverse speed by closing the clutches (K1) and (K8), the second reverse by closing the clutches (K7) and (K8), the third reverse by closing the clutches (K5) and (K8), the fourth reverse by closing the clutches (K3) and (K8), the fifth reverse by closing the clutches (K1) and (K6), the sixth reverse by closing the clutches (K6) and (K7), the seventh reverse by closing the clutches (K5) and (K6) and the eighth reverse gear is obtained by closing the clutches (K3) and (K6). Input group ( 2 ) of a gear change transmission ( 1 ), according to claim 1, 2, 3 or 4, characterized in that on the first countershaft ( 6 ) fixed wheel ( 17 ) is omitted, whereby the loose wheel ( 16 ) of the input shaft ( 5 ) with the fixed wheel ( 18 ) of the first counter-wave ( 6 ) meshes with one with the inner disk carrier of the second clutch (K6) of the second countershaft ( 7 ) arranged double clutch (C) connected loose wheel ( 19 ) is engaged. Input group ( 2 ) of a gear change transmission ( 1 ) according to claim 3, 4 or 5, characterized in that the fixed wheel ( 4 ), whereby its functionality by the fixed wheel ( 61 ), which with the fixed wheel ( 14 ) of the second counter-wave ( 7 ) and with the third countershaft ( 59 ) arranged loose wheel ( 60 ) combs.

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