DE102011005029A1 - Double clutch transmission for motor vehicle, has two clutches, whose input sides are connected with drive shaft and its output sides are connected with one of two co-axial transmission input shafts of sub-transmissions - Google Patents

Abstract

The double clutch transmission has two clutches (K1,K2), whose input sides are connected with a drive shaft (w0) and its output sides are connected with one of the two co-axial transmission input shafts (w1,w2) of sub-transmissions. Multiple switchable transmission ratios are assigned to the sub-transmissions. The transmission ratios are coupled with another drive shaft (w4) by a counter shaft (w3) and a range groups designed as planetary transmission. The switchable transmission ratio of one of the sub-transmissions independent from the range groups is coupled with an output shaft.

Description

The present invention relates to a dual clutch transmission according to the closer defined in the preamble of claim 1. Art.

For example, from the document DE 10 2005 044 068 A1 is a power shift group transmission with a double clutch is known in which the drive shaft and the output shaft are arranged coaxially to each other. The transmission input shafts associated with the two partial transmissions are each in engagement with one of the countershafts via input constants, the countershafts being arranged coaxially with one another. Furthermore, the known transmission comprises a main shaft, which can be coupled to switch a direct gear with one of the transmission input shafts. The output side end of the main shaft is connected to a sun gear, which forms the input member of a planetary gear formed as a range group. The planet carrier is rotatably connected to a transmission output shaft or output shaft. Thus, all gear ratios are transmitted to the output shaft via the range group. Therefore, at least the gear stage, in which a range shift occurs, are not performed power-shiftable.

Furthermore, from the document DE 198 50 549 A1 a dual-clutch transmission for a motor vehicle, in which an input shaft of the transmission is coupled to an electric machine, so that can be dispensed with a starter and a generator for the internal combustion engine.

The present invention is based on the object to propose a dual-clutch transmission of the type described above with as many powershift gear ratios and as few gear planes and switching elements.

This object is achieved by the features of claim 1, wherein further advantageous embodiments of the dependent claims and the drawings and the associated description.

Thus, a dual-clutch transmission is proposed with two clutches, which are connected on the one hand with the drive shaft and on the other hand with associated transmission input shafts of the two partial transmissions. The two partial transmissions are assigned a plurality of shiftable gear ratios or gear planes, which can be coupled via a countershaft and a trained as a planetary gear range group with an associated output shaft to transmit the selected gear ratio to the output. The output shaft of the dual-clutch transmission is arranged offset in axial direction to the drive shaft. According to the invention, it is now provided that at least one shiftable ratio stage is not realized via the range group. This means that at least one ratio or gear ratio of at least one of the partial transmissions is transmitted to the output shaft independently of the range group formed as a planetary gear set.

In this way, a range-independent power path to the output is provided so that all forward gears can be sequentially power shifted. As a result, in the proposed dual-clutch transmission, the advantages of a range group and the advantages of independent power paths can be combined, so that a wheelset is realized, which has few components due to the double use of gear ratios or gear planes and a maximum number of powershift gears constructively easy to implement.

As part of a possible embodiment of the invention can be provided that in the dual clutch transmission according to the invention, the switching elements used for switching the gear ratios are assigned to the transmission input shafts of the partial transmission. However, it is also conceivable that at least one switching element is assigned to the countershaft. For example, such that the switching element can switch both gear ratios of the first sub-transmission and transmission stages of the second sub-transmission. As switching elements double acting switching elements or double switching elements can be used, which connect one or the other associated idler gear of the wheel plane with the associated shaft depending on the switching direction. It is possible that a double-acting switching element is replaced by two unilaterally acting switching elements or vice versa. As switching elements z. As hydraulic, electric, pneumatic, mechanically actuated clutches or positive jaw clutches and any type of synchronizations are used, which serve for the rotationally fixed connection of a loose wheel with a shaft.

The intended range group or the planetary gear can be switched for example by one or more switching elements by, for example, a ring gear of the planetary gear can be connected via the switching element to the housing or with the planet carrier. Thus, the gear levels associated gear levels can be coupled via the intermediate shaft or countershaft and the planetary gear with the output shaft, so that depending on the switching direction of the associated switching element, the number of gears through the planetary gear can be doubled, whereby four courses are provided for each partial transmission. The range group translation can be selected with a large jump, so that the course sequence is extended accordingly.

In addition, the power path, which is selected independently of the range group, can be coupled directly to the output shaft via a gear plane of the first subtransmission, independently of the countershaft, by directly connecting the corresponding gear plane to the planet carrier. This translation stage can be placed, for example, on the fifth gear, so that before switching to the sixth gear, the range group can be switched. In this way, at least the first eight forward gears are sequentially Lastschaltbar executable.

In the dual-clutch transmission according to the invention thus preferably nine forward gears and two reverse gears can be realized with only six of the two partial transmissions associated gear ratios or gear planes. Preferably, the shiftable gear ratios can be designed as a spur gear transmission stages. Five of the gear trains associated with the gear trains are coupled via the countershaft and the planetary gear to the output shaft, wherein the sixth gear ratio or gear plane is coupled independently of the range group with the output shaft.

Regardless of the respective variants of the dual-clutch transmission can be provided that at least one electric machine is provided to realize a hybrid concept. The electric machine can be coupled, for example, to the main group or to the partial transmissions and / or also in the region of the intermediate shaft or countershaft with the wheelset. For connecting the electric machine with one of the partial transmission, this can be coupled directly or via a switchable connection with the associated transmission input shaft.

If, in the hybrid concept, the electric machine is assigned to the countershaft, this may for example be connected laterally via a spur gear stage to a fixed gear of the countershaft. In this arrangement possibility arise, among other space advantages.

In order to minimize the dimensions of the dual-clutch transmission according to the invention as possible, there is a desire to provide as many Doppelradebenen gear ratios, in which the gears of the countershaft are both with gears of the transmission input shafts of the partial transmission and with gears of the range group or the output shaft engaged.

Due to Mehrfachnutzungen of idler gears of the gear ratios, a maximum number of translations can be realized in the proposed dual-clutch transmission with as few gear planes, preferably the first eight forward gears are sequentially load-shiftable in sequential design.

To optimize the gradation in the proposed double-clutch transmission according to the invention, for example, a double-wheel plane can be replaced by two single wheel planes by a fixed gear is replaced by two fixed wheels. As a result, a particularly harmonious, progressive gear gradation can be achieved. It is also possible to replace two single gear planes with a double gear plane.

Advantageously, the lower forward gears and the reverse gears can be actuated via a starting or shifting clutch, so as to concentrate higher loads on this clutch and thus to perform the second clutch space and cheaper. In particular, the wheel planes in the proposed dual-clutch transmission can be arranged so that both can be approached via the inner transmission input shaft or via the outer transmission input shaft and thus via the respectively more suitable coupling, which also allows for a concentrically arranged, radially nested construction of the double clutch becomes. For this purpose, the wheel planes can be arranged or exchanged in accordance with mirror symmetry.

Furthermore, the present invention will be further explained with reference to the drawings. Show it:

1 a schematic view of a first embodiment of a dual clutch transmission according to the invention;

1A a possible circuit diagram of the first embodiment of the dual-clutch transmission;

1B a possible circuit diagram relating to the powershiftability of the first embodiment of the dual-clutch transmission;

2 a schematic view of a second possible embodiment of the dual clutch transmission according to the invention;

2A a possible circuit diagram of the second embodiment of the dual clutch transmission;

2 B a possible circuit diagram with respect to the powershiftability of the second embodiment of the dual-clutch transmission;

3 a schematic view of a possible hybrid concept by way of example with reference to the first embodiment of the dual clutch transmission; and

4 a schematic view of another embodiment of the hybrid concept by way of example with reference to the first embodiment of the dual clutch transmission.

In the figures, two possible embodiments of a dual-clutch transmission according to the invention are exemplified. The Neungang or eight-speed dual-clutch transmission, for example, preferably has two reverse gears R1 and R2, wherein at least the first eight forward gears, in addition to further power shift gears, can be executed in a sequential power shiftable manner. However, the number of the aforementioned gears are only examples, so that other gear ratios can be readily provided.

Independently of the respective embodiment variants, the dual-clutch transmission comprises two clutches K1, K2 whose input sides are connected to a drive shaft w0 and whose output sides are each connected to one of two transmission input shafts w1, w2 of the two partial transmissions arranged coaxially with one another. The first transmission input shaft w1 is exemplified as a solid shaft and the second transmission input shaft w2 is exemplified as a hollow shaft. The drive shaft w0 is arranged off-axis to an output shaft w4. The partial transmissions or the transmission input shafts w1, w2 are assigned, for example, six shiftable spur gear transmission stages as wheel planes. Five of the associated gear ratios are coupled to the output shaft w4 via a countershaft w3 and a range group formed as a planetary gear. The sixth, the first partial transmission associated gear ratio is independently of the range group coupled to the output shaft w4 by the translation stage is directly connected to the planet carrier PT of the planetary gear, which in turn is rotatably coupled to the output shaft w4.

For switching the gear ratios four double-acting switching elements S1, S2, S3, S4 are provided, which are each shown in the figures in their neutral position N, which is characterized only in the fourth switching element S4.

The gear ratios, which are realized via the range group, are each assigned to two gear stages or gears. This is indicated in the figures in that the gear ratios associated gear ratios are indicated one above the other, wherein the respective upper gear the translation of the range group in the slow or low (L) and the respective lower gear, the translation of the range group into fast or high ( H) corresponds.

Regardless of the particular embodiment, the independent power path is used for fifth gear. Due to the fact that the fifth gear can be set independently with regard to the gear ratio or number of teeth of the gears involved, the first gear can also be selected independently. This has the advantage that, in spite of the geometric grading necessary in the case of group transmissions, a progressive graduation is possible in the shifting from the first to the second gear. Since the gear ratio for the reverse gears are switched over the range group, two reverse gears R1 and R2 result in an advantageous manner.

According to 1 . 3 and 4 be in the first embodiment of the dual clutch transmission of the second transmission input shaft w2 of the second partial transmission associated with two idler gears z11, z21, which can be rotatably connected by the first switching element S1 depending on the switching direction with the second transmission input shaft w2. The first transmission input shaft w1 of the first partial transmission are assigned four idler gears z31, z41, z51, z61, wherein the idler gears z31 and z41 can be rotatably connected to the transmission input shaft w1 by the associated second switching element S2, depending on the switching direction. Depending on the switching direction, the two idler gears z51 and z61 are connected to the first transmission input shaft w1 via the third shift element S3. The countershaft w3 has five fixed gears z12, z22, z32, z42, z52 and a loose wheel z62 in the first embodiment of the dual clutch transmission. The fixed gears z12, z22, z32, z42, z52 are connected via the countershaft w3 with a sun gear SR formed as an input member of the range group, wherein depending on the switching direction of the ring gear HR of the planetary gear associated fourth switching element S4 a translation into Fast H or L slow can be transmitted to the output shaft w4. The countershaft w3 associated idler gear z62 is directly connected to the planet carrier PT of the planetary gear to connect the independent power path directly to the output shaft w4, as in this translation, the fourth switching element S4 is in its neutral position N.

In the first single gear plane as a gear ratio, the idler gear z11 of the second transmission input shaft w2 engages with the fixed gear z12 of the countershaft w3. In the second simple Gear plane is the idler gear z21 of the second transmission input shaft w2 the fixed gear z22 of the countershaft w3 engaged. The third single-gear plane comprises the idler gear z31 of the first transmission input shaft w1, which meshes with the fixed gear z32 of the countershaft w3. In the fourth single gear plane, the idler gear z41 of the first transmission input shaft w1 engages with the fixed gear z42 of the countershaft w3. In the fifth double-gear plane meshes the idler gear z51 of the first transmission input shaft w1 with an idler zr for speed reversal for the reverse ratios, the idler zr with the fixed gear z52 of the countershaft w3 is engaged. In the sixth single-gear plane, the idler gear z61 of the first transmission input shaft w1 engages with the idler gear z62 of the countershaft w3, the idler gear z62 being directly connected to the planet carrier PT of the planetary gear. The idler gear z62 can also be designed as a short hollow shaft on the countershaft w3.

Thus, by way of example, at least five single gear planes and a double gear plane with a total of at least 13 gears and a planetary gear set as a range group result in the first embodiment variant, wherein the gear ratios are balanced and low tooth forces occur in the gears. In addition, small synchronizations result in the first three switching elements S1, S2, S3, so that only a larger-sized synchronization in the fourth switching element S4 is required.

The corresponding circuit diagram is in 1A illustrated with exemplary translations i and increments k and the spread, wherein the respective actuation direction of the switching elements S1, S2, S3, S4 indicated with left for li and right for each right with respect to the direction of movement of the schematically illustrated switching elements in the drawing plane of the figures are.

From the shift pattern results, by way of example, that the first forward gear 1 via the first clutch K1 and via the idler gear z31 with the first transmission input shaft w1 connecting second switching element S2 and via the ring gear HR of the planetary gear with the housing connecting the fourth switching element S4 is switchable. The second forward gear 2 can via the second clutch K2 and via the idler gear z11 to the second transmission input shaft w2 connecting first switching element S1 and via the ring gear HR of the planetary gear with the. Switching fourth switching element S4 are connected, wherein the third forward gear 3 via the first clutch K1 and via the idler gear z41 to the first transmission input shaft w1 connecting second switching element S2 and via the ring gear HR of the planetary gear to the housing connecting the fourth switching element S4 is switched , The fourth forward gear 4 is connected via the second clutch K2 and via the idler gear z21 to the second transmission input shaft w2 connecting first switching element S1 and via the ring gear HR of the planetary gear with the housing connecting fourth switching element S4, wherein the fifth forward gear 5 via the first Clutch K1 and via which the idler gear z61 is connected to the first transmission input shaft w1 connecting third switching element S3. The idler gear z61 is engaged with the idler gear z62 of the countershaft w3, the idler gear z62 being connected to the output shaft w4 via the planet carrier PT. The sixth forward gear 6 can be connected via the second clutch K2 and via the idler gear z11 to the second transmission input shaft w2 connecting first switching element S1 and the ring gear HR connected to the planet carrier PT of the planetary gear fourth switching element S4, wherein the seventh forward gear 7 via the first clutch K1 and via the idler gear z41 to the first transmission input shaft w1 connecting second switching element S2 and via the ring gear HR connected to the planet carrier PT of the planetary gear fourth switching element S4 is connected. Finally, the eighth forward gear 8 can be switched via the second clutch K2 and via the idler gear z21 to the second transmission input shaft w2 connecting first switching element S1 and the ring gear HR connected to the planet carrier PT of the planetary gear fourth switching element S4.

In addition, the reverse gear R1 via the first clutch K1 and via the idler gear z51 with the first transmission input shaft w1 connecting third switching element S3 and via the ring gear HR of the planetary gear with the housing connecting fourth switching element S4 and the further reverse R2 on the first clutch K1 and via which the idler gear z51 connected to the first transmission input shaft w1 third switching element S3 and connected via the ring gear HR connecting the planet carrier PT of the planetary gear fourth switching element S4.

In addition, a further forward gear 5 G as a range group gear on the first clutch K1 and via the idler gear z31 with the first transmission input shaft w1 connecting second switching element S2 and via the ring gear HR connected to the planet carrier PT of the planetary gear fourth switching element S4 are connected. Thus, nine forward gears and two reverse gears R1, R2 can be realized.

In the first embodiment according to 1 . 3 and 4 are thus the first gear ratio or gear plane gears 2 and 6, the second wheel plane, the gears 4 and 8, the third gear plane, the gears 1 and 5 G, the fourth gear plane, the gears 3 and 7, the fifth gear plane, the reverse gears R1 and R2 and the sixth gear plane of the fifth gear 5 assigned. The planetary gear as a range group is assigned to both the output side end of the countershaft w3 and the output shaft w4, in which the sun gear SR is connected to the countershaft w3 and the planet carrier PT to the output shaft w4. For switching the transmission ranges of the ring gear HR, the fourth switching element S4 is assigned such that the ring gear HR is connected to the housing in a first switching position, which is directed in the drawing plane to the left and in a second switching position, in the drawing plane to the right directed, is connected to the planet carrier PT. In addition to the neutral position N, the fourth switching element S4 can thus be switched to the right to implement the transmission range to the fast H and to the left into the slow L. In the exemplary design of the wheelset, the transmission range to Fast H means that the sun gear SR rotates at the same speed as the planet carrier PT, with the transmission range into the slow L meaning a reduction.

According to 1B For example, a circuit diagram of the first embodiment with respect to the load shiftability of the gears of the dual clutch transmission is given. From this circuit diagram resulting in X gear shifts or gear changes, which are load shiftable executable.

According to 2 be in the second embodiment of the dual clutch transmission of the second transmission input shaft w2 of the second partial transmission associated with two idler gears z11, z21 and a fixed gear z51, the two idler gears z11, z21 can be rotatably connected by the first switching element S1 depending on the switching direction with the second transmission input shaft w2. The first transmission input shaft w1 of the first partial transmission are assigned two idler gears z31, z61 and a fixed gear z43, wherein either the idler gear z31 or the idler gear z61 can be rotatably connected to the first transmission input shaft w1 depending on the switching direction or direction of movement of the second switching element S2. The countershaft w3 in the second embodiment of the dual-clutch transmission comprises three fixed gears z12, z22, z32. In addition, the countershaft w3 comprises two switchable idler gears z53, z44 and a non-shiftable idler gear z62. The two shiftable idler gears z53, z44 can be connected in a rotationally fixed manner to the countershaft w3 via the associated third shift element S3. The non-shiftable idler gear z62 is connected via the planet carrier PT of the planetary gear to the output shaft w4.

At the in 2 in the first single gear plane or gear ratio stage, the idler gear z11 of the second transmission input shaft w2 engages with the fixed gear z12 of the countershaft w3, in the second single gear plane the idler gear z21 of the second transmission input shaft w2 with the fixed gear z22 of the countershaft w3 combs. In the third double-gear plane or gear ratio is an idler zr for speed reversal for the reverse ratios both with the idler gear z53 of the countershaft w3 and the fixed gear z51 of the second transmission input shaft w2 in engagement. In the fourth single gear plane, the fixed gear z43 of the first transmission input shaft w1 engages with the idler gear z44 of the countershaft w3. In the fifth single gear plane, the fixed gear z32 of the countershaft w3 is engaged with the idler gear z31 of the first transmission input shaft w1. In the sixth single gear plane, idler gear z62 of countershaft w3 engages idler gear z61 of the first transmission input shaft. The idler gear z62 can also be designed as a short hollow shaft on the countershaft w3.

Thus, for example, in the second embodiment according to 2 Five single gear planes and one dual gear plane with a total of 13 gears and a planetary gear set designed as a range group.

The corresponding circuit diagram is in 2A illustrated with exemplary translations i and increments k and the spread, wherein the respective actuation direction of the switching elements S1, S2, S3, S4 indicated with left for li and right for each right with respect to the direction of movement of the schematically illustrated switching elements in the drawing plane of the figures are.

From the. Circuit diagram results, for example, that the first forward gear 1 is connected via the first clutch K1 and via the idler gear z31 to the first transmission input shaft w1 connecting the second switching element S2 and via the ring gear HR of the planetary gear with the housing connecting fourth switching element S4, wherein the second forward gear 2 via the second clutch K2 and on the idler gear z11 with the The second transmission input shaft w2 connecting first switching element S1 and via the ring gear HR of the planetary gear connecting to the housing fourth switching element S4 is connected. The third forward gear 3 is connected via the first clutch K1 and via the third gear S3 connecting the idler gear z44 with the countershaft w3 and the fourth switching element S4 connecting the ring gear HR of the planetary gear with the housing, the fourth forward gear 4 via the second clutch K2 and via which the idler gear z21 with the second transmission input shaft w2 connecting first switching element S1 and via the ring gear HR of the planetary gear to the housing connecting the fourth switching element S4 is connected. The fifth forward gear 5 is connected via the first clutch K1 and via the idler gear z61 to the first transmission input shaft w1 connecting second switching element S2, wherein the idler gear z61 meshing idler gear z62 of the countershaft w3 is connected via the planet carrier PT with the output shaft w4. The sixth forward gear 6 is connected via the second clutch K2 and via the idler gear z11 to the second transmission input shaft w2 connecting first switching element S1 and via the ring gear HR connected to the planet carrier PT of the planetary gear fourth switching element S4. The seventh forward gear 7 is connected via the first clutch K1 and via the idler gear z44 with the countershaft w3 connecting third switching element S3 and via the ring gear HR connected to the planet carrier PT of the planetary gear fourth switching element S4, wherein the eighth forward gear 8 via the second Coupling K2 and via the idler gear z21 to the second transmission input shaft w2 connecting first switching element S1 and via the ring gear HR connected to the planet carrier PT of the planetary gear fourth switching element S4 is connected.

In addition, the reverse gear R1 is connected via the second clutch K2 and via the third gear S3 connecting the idler gear z53 with the countershaft w3 and the fourth switching element S4 connecting the ring gear HR of the planetary gear to the housing, wherein the further reverse gear R2 via the second clutch K2 and via which the idler gear z53 with the countershaft w3 connecting third switching element S3 and via the ring gear HR connected to the planet carrier PT of the planetary gear fourth switching element S4 is connected.

In addition, a further forward gear 5G as a range group gear on the first clutch K1 and via the idler gear z31 with the first transmission input shaft w1 connecting second switching element S2 and via the ring gear HR connected to the planet carrier PT of the planetary gear fourth switching element S4 are connected. Thus, nine forward gears and two reverse gears R1, R2 can also be realized in the second embodiment variant.

In the second embodiment according to 2 Thus, the first gear ratio or gear plane, the gears 2 and 6, the second gear plane, the gears 4 and 8, the third gear plane, the reverse gears R1 and R2, the fourth gear plane, the gears 3 and 7, the fifth gear plane, the gears 1 and 5G and the sixth wheel plane of the fifth gear 5 assigned. The planetary gear as a range group is assigned to both the output side end of the countershaft w3 and the output shaft w4, in which the sun gear SR is connected to the countershaft w3 and the planet carrier PT to the output shaft w4. For switching the transmission ranges of the ring gear HR, the fourth switching element S4 is assigned such that the ring gear HR is connected to the housing in a first switching position, which is directed in the drawing plane to the left and in a second switching position, in the drawing plane to the right directed, is connected to the planet carrier PT. In addition to the neutral position N, the fourth switching element S4 can thus be switched to the right to implement the transmission range to the fast H and to the left into the slow L. In the exemplary design of the wheelset, the transmission range to Fast H means that the sun gear SR rotates at the same speed as the planet carrier PT, with the transmission range into the slow L meaning a reduction.

According to 2 B For example, a circuit diagram of the second embodiment variant with respect to the load shiftability of the gears of the dual-clutch transmission is given. From this circuit diagram resulting in X gear shifts or gear changes, which are load shiftable executable.

The second embodiment according to 2 is characterized inter alia by the fact that the reverse ratios R1, R2 are assigned to the second partial transmission. This results in the advantage that circuits from the first gear 1 in the reverse gears R1, R2 or vice versa can be performed power shiftable.

In 3 For example, based on the first embodiment, a hybrid concept is shown, in which the electric machine EM is connected to the second partial transmission by the electric machine EM is connected directly to the second transmission input shaft w2. This results in the electric driving over the range group the opportunity to use the gear ratios of the second, fourth, sixth and eighth gear. The start of the internal combustion engine in neutral, for example, can be done directly with a 1: 1 ratio via the second transmission input shaft w2 when the second clutch K2 is closed.

Due to the possibility of disconnection of the output shaft via the neutral circuit of the range group, the methodology that the engine can be started via the first partial transmission can also be obtained with particular advantage. This can z. B. the smallest gear 2 of the second sub-transmission and the largest gear 7 of the first When the second clutch K2 is open, the idler gear z11 is connected to the second transmission input shaft w2 via the first shifting element S1 and, moreover, the idler gear z41 is connected to the first transmission input shaft w1 via the second shifting element S2 and the first clutch K1 is closed and the range group or the fourth switching element S4 is in its or its neutral position N, as shown for example in FIG 3 is shown. This results in a favorable ratio between the electric machine EM and the engine when starting. For starting the internal combustion engine via the first partial transmission but also other gear ratios than those mentioned above can be used.

According to 4 is a further hybrid concept illustrated by way of example with reference to the first embodiment. The electric machine EM is associated with this concept, for example, via the idler gear z11 coaxial with the second transmission input shaft w2 the second sub-transmission. The idler gear z11 and the electric machine EM could also be arranged by means of a common short hollow shaft or the like coaxial with the second transmission input shaft w2, which is connectable via the associated switching element S1 with the second transmission input shaft w2. Alternatively or additionally, an electric machine EM can be coupled to the countershaft w3 via the fixed gear z32, for example. Thus, the electric machine EM is laterally or axially parallel to the countershaft w3 connected via a spur gear.

This results in the advantage that the double clutch does not rotate with purely electric driving, so that no drag losses occur when driving over the partial transmission. In addition, the electric machine EM can replace a large synchronization, for example, at the fourth switching element, which is associated with the ring gear HR of the planetary gear.

The illustrated hybrid concepts, which are shown by way of example only in the first embodiment, but can also readily in the second embodiment according to 2 be provided.

LIST OF REFERENCE NUMBERS

1

first forward

2

second forward gear

3

third forward speed

4

fourth forward gear

5

fifth forward gear

5G

fifth forward gear as a range group gear

6

sixth forward gear

7

seventh forward gear

8th

eighth forward gear

R1

reverse gear

R2

reverse gear

w0

drive shaft

w1

first transmission input shaft of the first partial transmission

w2

second transmission input shaft of the second partial transmission

w3

Countershaft

w4

output shaft

K1

first clutch

K2

second clutch

z11

Idler gear of the second partial transmission

z21

Idler gear of the second partial transmission

z51

Fixed gear of the second partial transmission

z31

Idler gear of the first partial transmission

z41

Idler gear of the first partial transmission

z51

Idler gear of the first partial transmission

z61

Idler gear of the first partial transmission

z43

Fixed gear of the first partial transmission

z12

Fixed gear of the countershaft

z22

Fixed gear of the countershaft

z32

Fixed gear of the countershaft

Z42

Fixed gear of the countershaft

z52

Fixed gear of the countershaft

Z44

Idler gear of the countershaft

Z53

Idler gear of the countershaft

z62

Idler gear of the countershaft

SR

Sun gear of the planetary gear or range group

MR

Ring gear of the planetary gear or range group

PT

Planet carrier of the planetary gear or range group

zr

Intermediate wheel for speed reversal for reverse gear ratio

EM

electric machine

H

high range of the range group

L

low range of the range group

N

Neutral position of the range group or of the switching element

S1

first double-acting switching element

S2

second double-acting switching element

S3

third double-acting switching element

S4

fourth double-acting switching element

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 102005044068 A1 [0002]
• DE 19850549 A1 [0003]

Claims (17)

Double-clutch transmission with two clutches (K1, K2) whose input sides are connected to a drive shaft (w0) and whose output sides are each connected to one of two transmission input shafts (w1, w2) arranged coaxially with one another, whereby a plurality of shiftable gear ratios are assigned to the partial transmissions, which via a countershaft (w3) and designed as a planetary gear range group with an output shaft (w4) can be coupled, the output shaft (w4) is arranged offset in axial direction to the drive shaft (w0), characterized in that at least one switchable gear ratio at least one of the sub-gearbox independently from the range group with at least one output shaft (w4) can be coupled. Dual-clutch transmission according to claim 1, characterized in that for the sequential powershiftable switching at least the first eight forward gears four double-acting switching elements (S1, S2, S3, S4) are provided. Dual-clutch transmission according to one of the preceding claims, characterized in that the independent of the range group switchable gear ratio of the first sub-transmission via the planet carrier (PT) of the planetary gear directly to the output shaft (w4) is connected to the ring gear (HR) associated fourth switching element ( S4) is switched to a neutral position (N). Dual-clutch transmission according to one of the preceding claims, characterized in that the further transmission stages via the countershaft (w3) with the formed as an input member of the range group sun gear. (SR) of the planetary gear are coupled, wherein depending on the switching position of the ring gear (HR) associated fourth switching element (S4) is a range ratio to the fast (H) or slow (L). Dual-clutch transmission according to one of the preceding claims, characterized in that the two transmission input shafts (w1, w2) of the partial transmission six gear planes are assigned as gear ratios, wherein five gear planes via the countershaft (w3) and via the planetary gear to the output shaft (w4) are coupled and wherein the sixth gear plane via a loose wheel (z62) of the countershaft (w3) and the planet carrier (PT) with the output shaft (w4) is coupled. Dual-clutch transmission according to one of the preceding claims, characterized in that the second transmission input shaft (w2) of the second partial transmission associated with two idler gears (z11, z21), which are switchable by the first double-acting switching element (S1) that the first transmission input shaft (w1) of the four idler gears (z31, z41, z51, z61) are associated with the first subgear, wherein the two idler gears (z31, z41) of the double-acting second switching element (S2) and the two idler gears (z51, z61) of the double-acting third switching element (S3) are switchable, and that the countershaft (W3) five fixed wheels (Z12, Z22, Z32, Z42, Z52) and a loose wheel (Z62) are assigned, wherein the output side end of the countershaft (w3) with the sun gear (SR) as the range group trained planetary gear is connected. Dual-clutch transmission according to one of the preceding claims, characterized in that in a first gear plane, the idler gear (z11) of the second. Transmission input shaft (w2) with the fixed gear (z12) of the countershaft (w3) meshes that in a second gear plane, the idler gear (z21) of the second transmission input shaft (w2) with the fixed gear (z22) of the countershaft (w3) meshes, that in a third Wheel plane the fixed gear (Z32) of the countershaft (W3) with the idler gear (Z31) of the first transmission input shaft (w1) meshes that in a fourth gear plane, the idler gear (z41) of the first transmission input shaft (w1) with the fixed gear (z42) of the countershaft ( w3) meshes, that in a fifth gear plane, the fixed gear (z52) of the countershaft (w3) with an intermediate gear (zr) for speed reversal for the reverse gear meshes, the intermediate gear (zr) also with the idler gear (z51) of the first transmission input shaft (w1 meshes, and that in a sixth gear plane meshes the idler gear (z61) of the first transmission input shaft (w1) with the idler gear (z62) of the countershaft (w4), wherein the idler gear (z62) via the planet carrier (PT) with the output shaft (w4 ) connected is. Dual-clutch transmission according to one of the preceding claims, characterized in that a first forward gear (1) via the first clutch (K1) and via the idler gear (Z31) with the first transmission input shaft (w1) connecting the second switching element (S2) and via the ring gear (HR) of the planetary gear with the housing connecting fourth switching element (S4) is switchable, that a second forward gear (2) via the second clutch (K2) and via the idler gear (z11) to the second transmission input shaft (w2) connecting the first switching element ( S1) and via which the ring gear (HR) of the planetary gear with the housing connecting fourth switching element (S4) is switchable, that a third forward gear (3) via the first clutch (K1) and on the idler gear (Z41) with the first transmission input shaft (W1) connecting the second switching element (S2) and via the the ring gear (HR) of the planetary gear with the housing connecting the fourth switching element (S4) is switchable that a fourth Forward gear (4) via the second clutch (K2) and via the idler gear (z21) to the second transmission input shaft (w2) connecting the first switching element (S1) and via the ring gear (HR) of the planetary gear with the housing connecting the fourth switching element (S4 ) is switchable, that a fifth forward gear (5) via the first clutch (K1) and via the idler gear (z61) to the first transmission input shaft (w1) connecting the third switching element (S3) and via the ring gear (HR) of the planetary gear associated and in a neutral position (N) provided fourth switching element (S4) is switchable, that a sixth forward gear (6) via the second clutch (K2) and via the idler gear (z11) with the second transmission input shaft (w2) connecting the first switching element (S1 ) and via which the ring gear (HR) with the planet carrier (PT) of the planetary gear connecting fourth switching element (S4) is switchable that a seventh forward gear (7) via the first clutch (K1) and via which the idler gear (z41) is connected to the first transmission input shaft (w1) connecting second switching element (S2) and via the ring gear (HR) with the planet carrier (PT) of the planetary gear connecting fourth switching element (S4) and that an eighth forward gear ( 8) via the second clutch (K2) and via the idler gear (z21) to the second transmission input shaft (w2) connecting the first switching element (S1) and via the ring gear (HR) with the planet carrier (PT) of the planetary gear connecting fourth switching element ( S4) is switchable. Double-clutch transmission according to one of the preceding claims, characterized in that a reverse gear (R1) via the first clutch (K1) and via the idler gear (Z51) to the first transmission input shaft (w1) connecting the third switching element (S3) and via the ring gear ( HR) of the planetary gear with the housing connecting fourth switching element (S4) is switchable, and that a further reverse gear (R2) via the first clutch (K1) and via the idler gear (z51) with the first transmission input shaft (w1) connecting third switching element ( S3) and via which the ring gear (HR) with the planet carrier (PT) of the planetary gear connecting fourth switching element (S4) is switchable. Dual-clutch transmission according to one of the preceding claims, characterized in that the second transmission input shaft (w2) of the second partial transmission are associated with two idler gears (z11, z21) and a fixed gear (z51), wherein the two idler gears (z11, z21) of the first double-acting switching element (S1) are switchable, that the first transmission input shaft (W1) of the first partial transmission, a fixed gear (Z43) and two idler gears (Z31, Z61) are assigned, wherein the two idler gears (Z31, Z61) of the double-acting second switching element (S2) switchable and that the countershaft (w3) are associated with three fixed wheels (z12, z22, z32) and three loose wheels (z53, z44, z62), wherein the two loose wheels (z53, z44) of the third double-acting switching element (S3) are switchable , and wherein the output side end of the countershaft (w3) is connected to the sun gear (SR) of the planetary gear formed as a range group. Dual-clutch transmission according to claim 10, characterized in that in a first gear plane, the idler gear (z11) of the second transmission input shaft (w2) with the fixed gear (z12) of the countershaft (w3) meshes, that in a second gear plane, the idler gear (z21) of the second transmission input shaft (W2) with the fixed gear (Z22) of the countershaft (W3) meshes that in a third rate plane an intermediate gear (zr) for speed reversal for the realization of the reverse ratios with both the fixed gear (z51) of the second transmission input shaft (w2) and with the Idler gear (z53) of the countershaft (w3) meshes that in a fourth gear plane the fixed gear (z43) of the first transmission input shaft (w1) meshes with the idler gear (z44) of the countershaft (w3), that in a fifth gear plane the fixed gear (z32) the countershaft (w3) meshes with the idler gear (z31) of the first transmission input shaft (w1), and that in a sixth gear plane, the idler gear (z62) of the countershaft (w3) with the idler gear (z61) of the first gear the input shaft (w1) meshes, wherein the idler gear (z62) via the planet carrier (PT) with the output shaft (w4) is connected. Dual-clutch transmission according to claim 10 or 11, characterized in that a first forward gear (1) via the first clutch (K1) and over which the idler gear (z31) with the first transmission input shaft (w1) Connecting second switching element (S2) and via the ring gear (HR) of the planetary gear with the housing connecting the fourth switching element (S4) is switchable, that a second forward gear (2) via the second clutch (K2) and on the idler gear (Z11) with the second transmission input shaft (w2) connecting the first switching element (S1) and via the ring gear (HR) of the planetary gear with the housing connecting the fourth switching element (S4) is switchable, that a third forward gear (3) via the first clutch (K1) and via which the idler gear (z44) with the countershaft (w3) connecting the third switching element (S3) and via the ring gear (HR) of the planetary gear with the housing connecting the fourth switching element (S4) is switchable that a fourth forward gear (4) via the second clutch (K2) and via the idler gear (z21) to the second transmission input shaft (w2) connecting the first switching element (S1) and via the ring gear (HR) of the planetary gear with the housing connecting fourth shift element (S4) is switchable, that a fifth forward gear (5) via the first clutch (K1) and via the idler gear (z61) with the first transmission input shaft (w1) connecting the second switching element (S2) and via the ring gear ( HR) of the planetary gear and in a neutral position (N) provided fourth switching element (S4) is switchable, that a sixth forward gear (6) via the second clutch (K2) and on the idler gear (z11) with the second transmission input shaft (w2) connecting first switching element (S1) and via the the ring gear (HR) with the planet carrier (PT) of the planetary gear connecting fourth switching element (S4) is switchable that a seventh forward gear (7) via the first clutch (K1) and on the idler gear (Z44) with the countershaft (w3) connecting third switching element (S3) and on the ring gear (HR) with the planet carrier (PT) of the planetary gear connecting fourth switching element (S4) is switchable u nd that an eighth forward gear (8) via the second clutch (K2) and via the idler gear (z21) to the second transmission input shaft (w2) connecting the first switching element (S1) and via the ring gear (HR) with the planet carrier (PT) of the planetary gear connecting fourth switching element (S4) is switchable. Dual-clutch transmission according to one of claims 10 to 12, characterized in that a reverse gear (R1) via the second clutch (K2) and via the idler gear (z51) with the countershaft (w3) connecting the third switching element (S3) and via the ring gear (HR) of the planetary gear with the housing connecting fourth switching element (S4) is switchable, and that a further reverse gear (R2) via the second clutch (K2) and via the idler gear (z51) with the countershaft (w3) connecting third switching element ( S3) and via which the ring gear (HR) with the planet carrier (PT) of the planetary gear connecting fourth switching element (S4) is switchable. Dual-clutch transmission according to one of the preceding claims, characterized in that a further forward gear (5G) as a range group gear on the first clutch (K1) and on the idler gear (Z31) with the first transmission input shaft (w1) connecting second switching element (S2) and on the the ring gear (HR) with the planet carrier (PT) of the planetary gear connecting fourth switching element (S4) is switchable. Double-clutch transmission according to one of the preceding claims, characterized in that at least one electric machine (EM) is coupled directly or indirectly with the countershaft (w3). Dual-clutch transmission according to one of the preceding claims, characterized in that at least one electric machine (EM) is directly or indirectly coupled to the second transmission input shaft (w2). Dual-clutch transmission according to one of the preceding claims, characterized in that at least nine forward gears (1, 2, 3, 4, 5, 5G, 6, 7, 8) and at least two reverse gears (R1, R2) are switchable.

Images