DE102009000776A1 - Variable speed gear transmission for e.g. tractor, has reversing unit including forward driving clutch and rearwards driving clutch, where output side of reversing unit is connected with drive shaft of main group - Google Patents

Abstract

The transmission (1) has an additional fixed wheel (59) arranged at an output side from a fixed wheel (64) and staying in contact with a sliding wheel (41) that is connected with a coupling (K5) arranged on a countershaft (7). An output side of an inlet group (2) and/or an output side (11) of an intermediate gear (4) are connected with a reversing unit (80) that includes a forward driving clutch (KF) and a rearwards driving clutch (KR). An output side of the reversing unit is connected with a drive shaft (13) of a main group (3).

Description

The The present invention relates to a change-speed gearbox, comprising a splitter group, in particular a change-speed gearbox for tractors and tractors, according to the Preamble of 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 change-speed gearbox is particularly suitable for use in agricultural and / or construction industry used motor vehicles, for example in tractors and tractor vehicles.

The known transmission includes a starting clutch, as a range group serving main group with synchronous switching clutches and one of the range group upstream input group, which serves as a split group, where a first countershaft of the input group axially aligned a drive shaft of the main group is arranged and wherein a Main drive shaft opposite the first countershaft arranged offset in parallel and can be driven by a PTO shaft is.

Of Further, 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 preferably as overdrive or creeper is executed.

Furthermore goes from the DE 10 2006011162 A1 the Applicant a gear shift transmission with a splitter gear, which results from the modification of an existing transmission, in which at lower input speed equal or higher terminal speed is enabled; In this case, the fragmentation ratio is changed by changing the number of teeth of at least one of the gears quickly.

That from the DE 10 2006011162 A1 known transmission allows the realization of four forward and four reverse power shift gears.

Of the present invention is based on the object, a change-speed gearbox, comprising a split group indicating at least six forward power shift gears and at least six reverse power shift gears having the number of teeth interventions in the split group should be low in the forward gears. Further should be without a change in the distance between the waves the transmission the realization of different speeds be enabled in the power shift gears.

These The object is solved by the features of claim 1. Further embodiments and advantages of the invention are apparent from the dependent claims.

Therefore a gear change transmission is proposed, comprising a starting clutch, an input group serving as split group, a main group and optionally one between the input group and the main gearbox switched intermediate gear, which as a high-speed gearbox or can be designed as creeper gear.

The Input group includes an input shaft, one parallel to the input shaft arranged first countershaft, which the intermediate gear or the main group drives and a second parallel to the input shaft arranged countershaft, wherein on the input shaft and the first countershaft each a power shift double-plate clutch arranged and on the second countershaft a power shiftable Lamella clutch is arranged, wherein the clutch bell of the Double clutches over external gears engage each other. Furthermore, there is the clutch bell the arranged on the second countershaft multi-disc clutch with the clutch bell of the arranged on the first countershaft double clutch engaged.

in this connection is provided that in front of arranged on the input shaft Double clutch on with the inner disc carrier of the first Coupling of the double clutch connected fixed wheel is arranged which arranged with a on the first countershaft and with the inner disk carrier of the first clutch on the first countershaft arranged dual clutch connected idler gear engaged.

Of Further, it is provided that the arranged on the input shaft Double clutch with the inner disc carrier of the second Coupling of the double clutch is connected downstream idler gear, which with a on the first countershaft on the output side of the Double clutch arranged fixed gear is engaged, which with the inner disk carrier of the second clutch of the double clutch connected is.

in this connection On the output side of this fixed gear is another on the first Countershaft arranged fixed wheel provided, which with a with the inner disk carrier on the second countershaft arranged clutch connected idler gear is engaged.

Forms according to the invention the first countershaft the output of the input group and serves as the drive shaft of the intermediate gear, wherein the output of the intermediate gear serves as the drive of the main group.

According to the Invention is the input group or the intermediate gear, if provided downstream of a reversing unit, which is a forward drive clutch and a reverse clutch, preferably have a common outer disk carrier; the output side of the reversing unit is connected to the drive shaft Main group connected.

at Closed forward clutch becomes the moment directly directed to the drive shaft of the main group, with closed reverse clutch the moment over at least two gear stages and another Transfer countershaft to the drive shaft of the main group becomes.

By the inventive design of the input group are at least six forward power shift gears and at least six reverse power shift gears feasible, wherein in the input group a maximum of three tooth interventions needed; in an advantageous way is for the fastest power shift forward gear only a meshing needed.

The Invention will be described below with reference to the accompanying figures exemplified in more detail. Show it:

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

2 : An exemplary circuit diagram for a transmission according to 1 , to which the clutch combinations for the powershift gears as well as achievable travel speeds and increments for all gears are to be taken.

Gear shift transmission are well known to those skilled in the art, so that in the context of the description of the figures only the invention relevant components, in particular the components the input group, described and explained.

In 1 is a gear change transmission according to the invention 1 shown. It includes an input group 2 , which serves as a split group, a main group 3 and one between the input group 2 and the main gearbox 3 arranged intermediate gear 4 , which is executed in the example shown as creeper.

The entrance group 2 includes an input shaft 5 , one parallel to the input shaft 5 arranged first countershaft 6 which the intermediate gear 4 drives and a second parallel to the input shaft 5 arranged countershaft 7 ,

How out 1 It can be seen on the input shaft 5 and on the counterwave 6 in each case a power shift double-plate clutch A, B arranged. The on the input shaft 5 arranged dual clutch A includes the clutches K1, K2, on the first countershaft 6 arranged double clutch B, the clutches K3, K4; on the second countershaft 7 is arranged a multi-plate clutch K5. According to the invention, the clutch bells are 8th . 9 the double clutches A, B over external gears 35 ' . 52 engaged directly with each other. Furthermore, there is the clutch bell 10 the clutch K5 via external gears 52 . 35 with the clutch bell 9 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 the inner disc carrier of the first clutch K1 of the dual clutch A fixed wheel 42 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 29 engaged.

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 37 is downstream, with the idler gear 37 with one on the first countershaft 6 output side of the double clutch B arranged fixed wheel 64 is engaged, which with the inner disk carrier of the second clutch K4 of the double clutch B of the countershaft 6 connected is.

Furthermore, the output side of this fixed gear 64 another on the first counter-wave 6 arranged fixed wheel 59 provided, which with one with the inner disk carrier of the second countershaft 7 arranged clutch K5 connected idler gear 41 engaged.

According to the invention, it is optionally provided that the toothing 35 the clutch bell 10 , which with the toothing 52 the clutch bell 9 meshes axially extending in the opposite direction than the toothing 35 ' the clutch bell 8th , which with the toothing 52 the clutch bell 9 combs. As a result, the advantage is achieved that these gears at the same distance between the waves 5 . 6 and 7 can be sized larger or a larger teeth number.

In the example shown, the first countershaft is used 6 the input group 2 as the drive shaft of the intermediate gear 4 , where the output 11 of the intermediate gear 4 with a reversing unit 80 is connected, which comprises a forward drive clutch KF and a reverse drive clutch KR, which preferably have a common outer disc carrier; like out 1 can be seen, the output side of the reversing unit 80 with the drive shaft 13 the main group 3 connected.

The reversing unit 80 includes a countershaft 81 with two fixed wheels 82 . 83 , being a fixed wheel 82 with one on the output shaft 11 of the intermediate gear 4 arranged and connected to the inner disk carrier of the reverse drive clutch KR loose wheel 84 combs and being the fixed wheel 83 with one with one on the drive shaft 13 of the main gearbox 3 arranged gear 85 meshing gear 86 engaged. In the event that no intermediate gear is provided, the idler gear 84 on the output of the input group 2 arranged. In 1 is the gear 86 shown offset. When the forward drive clutch KF is closed, the torque is applied directly to the drive shaft 13 the main group 3 passed, with the closed reverse clutch KR, the torque over at least two gear stages, ie via the gears 84 . 82 , the countershaft 81 and the gears 83 . 86 . 85 on the drive shaft 13 the main group 3 is transmitted.

The intermediate gear 4 is designed according to the prior art and includes one with the countershaft 6 connected fixed wheel 31 which with one on an intermediate shaft 14 arranged fixed wheel 59 is engaged; on the intermediate shaft 14 is another festrad 17 arranged, which is smaller than the fixed wheel 59 , where the fixed wheel 17 with a loose wheel 73 meshes, which on the output shaft 11 of the intermediate gear 4 is arranged.

Furthermore, viewed axially between the fixed gear 31 and the idler wheel 73 a synchronous clutch 15 arranged by their operation when engaged in the fixed gear 31 the fixed wheel 31 directly with the output shaft 11 of the intermediate gear 4 is connectable or - when engaged in the idler gear 73 - one on the intermediate shaft 14 going momentum flow is effected in order to achieve a reduction.

In the event that the intermediate gear 4 is designed as overdrive gear, is the gear 59 smaller than the gear 17 executed.

The the intermediate gear 4 downstream main group 3 is also carried out according to the prior art and comprises a drive shaft 13 , on the two double synchronizer clutches 16 . 27 are arranged over the two loose wheels 43 . 30 respectively. 58 . 47 with the drive shaft 13 optionally rotatably connected, wherein the loose wheels 43 . 30 . 58 . 47 with one each on a parallel to the drive shaft 13 arranged and serving as output shaft countershaft 18 arranged fixed wheel 39 . 41 . 25 . 32 comb.

On the countershaft 18 are two loose wheels 57 . 75 arranged by means of a double synchronizer clutch 69 with the countershaft 18 are rotatably connected and which with one on the drive shaft 13 arranged fixed wheel 26 respectively. 19 comb.

By operating the double synchronizer clutches 16 . 27 and 69 be in the main group 3 realized six courses, wherein the respective actuation direction of the double synchronizer clutches corresponding passages by the arrows in the upper part of the 1 are illustrated; For example, by a rotationally fixed connection of the idler gear 75 the countershaft 18 realized with the countershaft of the first gear. In the upper part of the 1 is also that of the respective operating direction of the double synchronizer clutch 15 corresponding operating mode indicated, where NO denotes the normal gears and KR the creeper gears.

In 1 is with 56 one with the output shaft 18 connected differential and with 60 a power take-off (PTO) called.

Due to the inventive design of the input group are advantageously six forward load shift gears and six reverse power shift gears feasible, as described 2 illustrated.

2 are the speeds in km / h of the respective load shift gear associated creeper gears and normal gears for an exemplary tire index 20.8-R42 refer. Furthermore, in the right part of the figure, the increments φ can be seen between the powershift gears. Here, the increments in all gears 1.18, whereby an overload of the couplings of the input group is avoided. In the lower part of the 2 are the increments φ indicated between the gears of a power shift stage.

The first, slowest power shift forward gear XL results in closed forward clutch KF by closing the clutches K1 and K2, the second power shift forward L by closing the clutches K1 and K5, the third power shift forward gear M by closing the clutches K1 and K4, the fourth power shift forward gear H by closing the clutches K3 and K2, the fifth power shift forward gear S by closing the clutches K3 and K5 and the sixth power shift forward gear XS is obtained by closing the clutches K3 and K4.

Of the first, slowest power shift reverse gear RL results when the reverse drive clutch is closed KR by closing the clutches K1 and K2, the second Power shift reverse RH by closing the clutches K1 and K5, the third power shift reverse gear RS by closing the clutches K1 and K4, the fourth power shift reverse gear RL2 by closing the clutches K3 and K2, the fifth Power shift reverse RH2 by closing the clutches K3 and K5 and the sixth power shift reverse RS2 results from closing the clutches K3 and K4.

In the load shift forward gears and the powershift reverse gears, a maximum of three meshing operations are required in the input group, with only one meshing action being required for the fastest forward power-shift forward gear XS and the fastest power-shift reverse gear RS2, namely a meshing engagement between the fixed gear 42 and the idler wheel 29 ,

At the in 2 Schematics shown are five normal gears specified with a transmission according to 1 can be realized, with the gears 58 . 25 omitted.

Of course Every constructive training, especially every one, also falls spatial arrangement of the components of the transmission itself as well as to each other and as far as technically reasonable, under the scope of protection the present claims, without the function of the transmission, as indicated in the claims, to influence even if these trainings are not explicitly in the figures or are shown in the description.

1

Gear shift transmission

2

input group

3

main group

4

intermediate gear

5

input shaft

6

Countershaft

7

Countershaft

8th

Kupplungsglocke

9

Kupplungsglocke

10

Kupplungsglocke

11

output of the intermediate gear

13

drive shaft the main group

14

intermediate shaft

15

Synchronous clutch

16

Double-synchronous clutch

17

fixed gear

18

Countershaft

19

fixed gear

25

fixed gear

26

fixed gear

27

Double-synchronous clutch

28

fixed gear

29

Losrad

30

Losrad

31

fixed gear

32

fixed gear

35

gearing

35 '

gearing

37

Losrad

39

fixed gear

41

Losrad

42

fixed gear

43

Losrad

47

Losrad

56

differential

57

Losrad

58

Losrad

59

fixed gear

60

PTO

69

Double-synchronous clutch

73

Losrad

75

Losrad

80

reversing unit

81

Countershaft

82

fixed gear

83

fixed gear

84

Losrad

85

gear

86

gear

K1

multi-plate clutch

K2

multi-plate clutch

K3

multi-plate clutch

K4

multi-plate clutch

K5

multi-plate clutch

KR

Reversing clutch

KF

Forward drive clutch

φ

increment

A

Double-disk clutch

B

Double-disk clutch

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - DE 4020558 A1 [0002]
• - DE 102006011162 A1 [0005, 0006]

Claims (10)

Tooth change gear ( 1 ), comprising an input group serving as split group ( 2 ), a main group ( 3 ) and optionally one between the splitter group ( 2 ) and the main group ( 3 ) switched intermediate gear ( 4 ), the input group ( 2 ) an input shaft ( 5 ), one parallel to the input shaft ( 5 ) and the output of the input group ( 2 ) forming the first countershaft ( 6 ) and a second parallel to the input shaft ( 5 ) arranged countershaft ( 7 ), wherein on the input shaft ( 5 ) and on the first counter-wave ( 6 ) is arranged in each case a power shift double-plate clutch (A, B), wherein the clutch bell ( 8th . 9 ) of the double clutches (A, B) via external gearing ( 35 ' . 52 ) are engaged, characterized in that on the second countershaft ( 7 ) a clutch (K5) is arranged, the clutch bell ( 10 ) via external gears ( 52 . 35 ) with the clutch bell ( 9 ) and that on the drive side before the on the input shaft ( 5 ) arranged dual clutch (A) connected to the inner disk carrier of the first clutch (K1) of the dual clutch (A) fixed wheel ( 42 ) with one on the countershaft ( 6 ) and with the inner disk carrier of the first clutch (K3) of the on the countershaft ( 6 ) arranged double clutch (B) connected loose wheel ( 29 ) is engaged, wherein 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 ( 37 ), which is connected to one on the first countershaft ( 6 ) on the output side of the double clutch (B) fixed wheel ( 64 ) is in engagement, whereby the fixed wheel ( 64 ) with the inner disk carrier of the second clutch (K4) of the double clutch (B) of the countershaft ( 6 ), wherein the output side of the fixed wheel ( 64 ) another on the counter-wave ( 6 ) fixed wheel ( 59 ) is arranged, which with one with the inner disk carrier of the second countershaft ( 7 ) arranged hitch be (K5) connected loose wheel ( 41 ) and wherein the output of the input group ( 2 ) or the output ( 11 ) of the optional intermediate gear ( 4 ) with a reversing unit ( 80 ), which comprises a forward drive clutch (KF) and a reverse drive clutch (KR) and wherein the output side of the reversing unit ( 80 ) with the drive shaft ( 13 ) of the main group ( 3 ) connected is. Gear change gear ( 1 ), comprising an input group serving as split group ( 2 ), according to claim 1, characterized in that the reversing unit ( 80 ) a countershaft ( 81 ) with two fixed wheels ( 82 . 83 ), where a fixed wheel ( 82 ) with one on the output of the input group ( 2 ) or on the output shaft ( 11 ) of the optional intermediate gear ( 4 ) and connected to the inner disk carrier of the reverse drive clutch (KR) loose wheel ( 84 ) combs, whereby the fixed wheel ( 83 ) with one on the drive shaft ( 13 ) of the main transmission ( 3 ) arranged gear ( 85 ) meshing gear ( 86 ) is engaged, wherein with closed forward clutch (KF) the moment directly on the drive shaft ( 13 ) of the main group ( 3 ) and wherein with closed reverse clutch (KR), the moment via the gears ( 84 . 82 ), the countershaft ( 81 ) and the gears ( 83 . 86 . 85 ) on the drive shaft ( 13 ) of the main group ( 3 ) is transmitted. Tooth change gear ( 1 ), comprising an input group serving as split group ( 2 ), according to claim 2, characterized in that in the input group ( 2 ) with the forward drive clutch closed (KF), six forward power shift gears can be realized, wherein the first power shift forward gear is engaged by closing the clutches (K1) and (K2), the second power shift forward gear is engaged by closing the clutches (K1) and (K5), the third power shift forward gear by closing the clutches (K1) and (K4), the fourth power shift forward gear by closing the clutches (K3) and (K2), the fifth power shift forward gear by closing the clutches (K3) and (K5) and the sixth power shift forward speed by closing the clutches (K3) and (K4) results. Tooth change gear ( 1 ), comprising an input group serving as split group ( 2 ), according to claim 1 or 2, characterized in that in the input group ( 2 ) with the reversing clutch (KF) closed, six reverse power shift gears can be realized, the first power shift reverse gear being engaged by closing the clutches (K1) and (K2), the second power shift reverse gear being engaged by closing the clutches (K1) and (K5), the third power shift reverse by closing the clutches (K1) and (K4), the fourth power shift reverse by closing the clutches (K3) and (K2), the fifth power shift reverse by closing the clutches (K3) and (K5) and the sixth power shift reverse by closing the clutches (K3) and (K4). Tooth change gear ( 1 ), comprising an input group serving as split group ( 2 ), according to claim 1, 2, 3 or 4, characterized in that in the event that an intermediate gear ( 4 ), the countershaft ( 6 ) of the input group ( 2 ) as the drive shaft of the intermediate gear ( 4 ), the output ( 11 ) of the intermediate gear ( 4 ) as a drive of the main group ( 3 ) and with the drive side of the reversing device ( 80 ) whose output side with the drive shaft ( 13 ) of the main group ( 3 ) connected is. Tooth change gear ( 1 ), comprising an input group serving as split group ( 2 ), according to claim 5, characterized in that the intermediate gear ( 4 ) with the countershaft ( 6 ) connected fixed wheel ( 31 ) with one on an intermediate shaft ( 14 ) fixed wheel ( 59 ) is engaged, wherein on the intermediate shaft ( 14 ) another fixed wheel ( 17 ) is arranged, which with a loose wheel ( 73 ) meshes on the output shaft ( 11 ) of the intermediate gear ( 4 ), wherein axially be sought between the fixed wheel ( 31 ) and the idler gear ( 73 ) a synchronous clutch ( 15 ) is arranged, by their operation when engaged in the fixed wheel ( 31 ) this directly with the primary shaft of the starting clutch ( 12 ) is connectable or when engaged in the loose wheel ( 73 ) via the intermediate shaft ( 14 ) torque flow is effected to achieve a lower or a translation. Tooth change gear ( 1 ), comprising an input group serving as split group ( 2 ), according to claim 6, characterized in that in the event that the intermediate gear ( 4 ) is designed as a creeper, the fixed gear ( 17 ) is smaller than the fixed wheel ( 59 ) in the event that the intermediate gear ( 4 ) is designed as a high-speed gear, the gear ( 59 ) is made smaller than the gear ( 17 ). Tooth change gear ( 1 ), comprising an input group serving as split group ( 2 ), according to one of the preceding claims, characterized in that the main group ( 3 ) a drive shaft ( 13 ), on which two double synchronizer clutches ( 16 . 17 ) are arranged, via the two loose wheels ( 43 . 30 ) respectively. ( 58 . 47 ) with the drive shaft ( 13 ) are selectively rotatably connected, wherein the loose wheels ( 43 . 30 . 58 . 47 ) each with one on a parallel to the drive shaft ( 13 ) and serving as output shaft countershaft ( 18 ) fixed wheel ( 39 . 41 . 25 . 32 ), whereas on the countershaft ( 18 ) two loose wheels ( 57 . 75 ) are arranged, which by means of a double synchronizer clutch ( 69 ) with the countershaft ( 18 ) are rotatably connected and with one on the drive shaft ( 13 ) fixed wheel ( 26 ) respectively. ( 19 ) comb. Tooth change gear ( 1 ), comprising an input group serving as split group ( 2 ), according to claim 8, characterized in that by actuating the double synchronizer clutches ( 16 . 27 . 69 ) in the main group ( 3 ) Six gears are feasible. Tooth change gear ( 1 ), comprising an input group serving as split group ( 2 ), according to one of the preceding claims, characterized in that the toothing ( 35 ) the clutch bell ( 10 ), which with the toothing ( 52 ) the clutch bell ( 9 ), axially extending in the opposite direction, as the toothing ( 35 ' ) the clutch bell ( 8th ), which with the toothing ( 52 ) the clutch bell ( 9 ) combs.