DE102015204600B4 - Gearbox for a motor vehicle and method for operating such - Google Patents

Abstract

Transmission (1), in particular double clutch transmission, for a motor vehicle, comprising at least two partial transmissions (2, 3), each of the partial transmissions (2, 3) comprising at least one input shaft (EW1, EW2) and one output shaft as the output shaft (AW) of both Sub-transmission (2, 3) is arranged and the at least two input shafts (EW1, EW2) are arranged on an input shaft axis (4) and the output shaft (AW) on the input shaft axis (4) or on one, in particular parallel to the input shaft axis (4) Countershaft axis (5) or output shaft axis is arranged, and wherein a countershaft (6) is arranged with at least one countershaft (VW1, VW2), the at least one countershaft (VW1, VW2) being arranged on said countershaft axis (5) and at least one the input shafts (EW1, EW2) by means of at least one wheel plane (a, b, c, d, e) and / or at least one switching element (S1, S2, S3, S4, S5, S6, S7, S8) with the output shaft (AW ) connect dbar, characterized in that a maximum of five wheel planes (a, b, c, d, e) and a maximum of five shifting devices (SE1, SE2, SE3, SE4, SE5) are arranged such that at least nine forward gears (V1, V2, V3 , V4, V5, V6, V7, V8, V9) can be represented by the gear (1).

Description

The present invention relates to a transmission, in particular a double clutch transmission, for a motor vehicle, comprising at least two partial transmissions, each of the partial transmissions comprising at least one input shaft and an output shaft being arranged as the output shaft of both partial transmissions and the at least two input shafts being arranged on an input shaft axis and Output shaft is arranged on the input shaft axis or on a countershaft axis or output shaft axis, in particular parallel to the input shaft axis, and wherein a countershaft is arranged with at least one countershaft, wherein the at least one countershaft is arranged on said countershaft axis and at least one of the input shafts by means of at least one wheel plane and / or at least one switching element can be connected to the output shaft.

The present invention also relates to a method for operating a transmission according to one of claims 1-21.

The present invention further relates to a motor vehicle, in particular a passenger or a truck with a transmission.

Such transmissions for a motor vehicle are designed, inter alia, as so-called double clutch transmissions, in which the input shafts of the two sub-transmissions can each be connected to a drive, for example an internal combustion engine or an electric motor, via an associated power shift element, the two power shift elements being combined in the form of a double clutch . The gear stages that can be represented by such a transmission are then alternately divided between the two sub-transmissions, so that, for example, one sub-transmission represents the odd gears and the other sub-transmission represents the even gears. It is also known to represent the individual gear stages by means of one or more gear stages or levels, each of which has different gear ratios. By means of appropriate switching elements, these can be integrated into the flow of force or torque between the input and output, so that a correspondingly desired ratio between the input and output of the transmission is shown.

By alternately dividing the gears between the two sub-transmissions, it is possible to select a subsequent gear when driving in a gear assigned to one sub-transmission in the other sub-transmission by corresponding actuation of the shifting devices, with a final change to the subsequent gear by opening the Powershift element of one part of the transmission and a shortly thereafter closing of the load switching element of the other part of the transmission is made possible. In this way, the gears or gear stages of the transmission can be shifted under load, which improves the acceleration ability of the motor vehicle due to a gear change that is essentially free of traction force interruption and enables more comfortable shifting operations for a vehicle driver.

Such double clutch transmissions can also be designed with a countershaft arranged in addition to the input and output, so that a compact construction is made possible in the axial direction.

From the DE 10 2012 220 686 A1 a transmission for a motor vehicle in the form of a double clutch transmission has become known. The double clutch transmission is designed in countershaft design with an input shaft axis and a countershaft axis, the output being carried out on the countershaft. Nine forward gears can be represented by means of the double gear. For this purpose, the transmission has eight wheel levels and nine shift elements.

The disadvantage here is that this transmission takes up a large amount of space.

An object of the present invention is therefore to provide a transmission which is more compact without reducing the number of gears which can be represented by the transmission and without increasing the number of shifting elements for representing the different gears.

The invention achieves the object in a transmission, in particular a double clutch transmission, for a motor vehicle, comprising at least two partial transmissions, each of the partial transmissions comprising at least one input shaft and with an output shaft being arranged as an output shaft of both partial transmissions and with the at least two input shafts being arranged on an input shaft axis and the output shaft is arranged on the input shaft axis or on a countershaft axis or output shaft axis, in particular parallel to the input shaft axis, and wherein a countershaft is arranged with at least one countershaft, the at least one countershaft being arranged on said countershaft axis and at least one of the input shafts using at least one The wheel plane and / or at least one shift element can be connected to the output shaft, in that at most five forward gear wheel planes and at most five shifting devices are arranged in this way that at least nine forward gears can be represented by the transmission.

The present invention also achieves the object in a method for operating a transmission according to one of claims 1-21, in that a first gear is represented by means of actuated second, sixth and eighth shifting elements and in that a second gear is represented by means of actuated second and eighth shifting elements and that a third gear is represented by actuated second and fifth shifting elements and that a fourth gear is represented by actuated second and seventh shifting elements, and that a fifth gear is represented by actuated first shifting element, and that a sixth gear is represented by actuated fourth and eighth shift element is shown, and that a seventh gear is represented by actuated fourth and fifth shift elements, and that an eighth gear is represented by actuated fourth and seventh shift elements, and that a ninth gear is represented by actuated third and fourth shift elements rd, wherein the other shift elements are open or are in the neutral position and a first clutch is closed in the even gears and a second clutch is closed in the odd gears and the other clutch is open.

The invention also achieves the object in a motor vehicle, in particular a passenger or a truck with a transmission according to one of claims 1-21 and / or operated with a method according to one of claims 22-23.

In the description, in particular in the claims, the term “wheel stage” or “wheel plane” preferably means essentially two mutually cooperating transmission elements for the transmission of torques from one transmission element to the other transmission element, which are preferably an under- or translation for provide in particular with the transmission elements interacting shafts in the transmission.

The term “switching element” is preferably to be understood in the description, in particular in the claims, to be a device which has at least one open and one closed state, the device having no torque in the open state and torque between two in the closed state can cooperate with this device or the switching element interacting other devices or transmission elements.

The term “transmission element” is preferably to be understood in the description, in particular in the claims, as a device with which force and / or torques can be transmitted. Transmission elements can preferably be designed as wheels, preferably as gears, in particular spur gears, bevel gears, worm gears or the like.

The term “adjacent” in relation to shifting elements shifting devices and / or wheel planes is preferably to be understood in the description, in particular in the claims, shifting devices, shifting elements and / or wheel planes which run along the input shaft axis or the countershaft axis of the transmission directly alongside one another along the respective axis are arranged and, in the case of switching devices or switching elements, one of the switching elements of the switching devices is connected directly to the other switching element of the adjacent switching device by means of a shaft.

A torque or a rotational movement of a drive shaft, for example an internal combustion engine, is particularly preferably introduced into the transmission via the drive shaft.

A shaft is not only to be understood to mean, for example, a cylindrical, rotatably mounted machine element for transmitting torque, but rather also general connecting elements that connect individual components or elements to one another, in particular connecting elements that connect several elements in a rotationally fixed manner.

Two elements are particularly referred to as being connected to one another if there is a fixed, in particular rotationally fixed connection between the elements. In particular, such connected elements rotate at the same speed.

Two elements are referred to below as connectable if there is a detachable connection between these elements. In particular, such elements rotate at the same speed when the connection is established.

The various components and elements can be connected to one another via a shaft or a connecting element, but also directly, for example by means of a welding, pressing or other connection.

A coupling is preferably to be understood in the description, in particular in the claims, as a switching element which, depending on the actuation state, permits a relative movement between two components or represents a connection for transmitting a torque. A relative movement is understood to mean, for example, a rotation of two components, the speed of the first component and the speed of the second component differing from one another. In addition, the Rotation of only one of the two components is conceivable while the other component is stationary or rotating in the opposite direction.

In the following, a clutch that is not actuated is to be understood as an opened clutch. This means that a relative movement between the two components is possible. When the clutch is actuated or closed, the two components accordingly rotate in the same direction at the same speed.

Particularly preferably, the shifting elements can be actuated selectively, that is to say individually and as required, so that different gears can be realized by means of different transmission ratios between the input shaft and the output shaft. The higher the number of gears, the finer a gear gradation can be realized with a large gear spread and thus, for example, an internal combustion engine of a motor vehicle can be operated in an optimal speed range and thus as economically as possible. At the same time, this contributes to an increase in driving comfort, since the internal combustion engine can preferably be operated at a low speed level. For example, noise emissions caused by the operation of the internal combustion engine are also reduced.

Furthermore, the switching elements can be designed such that energy is required for changing a switching state of the switching elements, but not for maintaining the switching state itself.

Switch elements which can be actuated as required, such as electromechanical switching elements or electromagnetic switching elements, are particularly suitable for this purpose. They are characterized, in particular in comparison to conventionally hydraulically actuated switching elements, by a particularly low and efficient energy requirement, since they can be operated almost without loss. In addition, it is advantageously possible to dispense with permanently maintaining a control pressure for actuating the conventional hydraulic switching elements, for example, or to apply the required hydraulic pressure permanently to the respective switching element in the switched state. In this way, for example, additional components such as a hydraulic pump can be dispensed with, insofar as these serve exclusively to control and supply the conventionally hydraulically actuated switching elements. If the supply of additional components with lubricants does not take place via a separate lubricant pump, but via the same hydraulic pump, then this can be dimensioned at least smaller. Any leaks at the oil transfer points of the hydraulic circuit, especially in the case of rotating components, are also eliminated. This also particularly preferably contributes to an increase in efficiency of the transmission in the form of a higher efficiency.

When using switching elements of the aforementioned type which can be actuated as required, it is particularly advantageous if they are easily accessible from the outside. Among other things, this has the advantage that the required switching energy can be supplied to the switching elements well. Switching elements are therefore particularly preferably arranged such that they are easily accessible from the outside. Easily accessible from the outside in the sense of the switching elements means that no further components are arranged between the housing of the transmission and the switching element, or that the switching elements are particularly preferably arranged on the drive shaft or on the output shaft.

The term “bindability” should preferably be understood in the description, in particular in the claims, that in the case of different geometrical positions, the same connection or binding of interfaces is guaranteed without individual connecting elements or waves crossing.

Further advantageous embodiments, features and advantages of the invention are described in the subclaims.

At least five wheel planes are expediently arranged. The advantage here is that at least nine forward gears can be made available in a simple manner.

The plurality of switching devices advantageously each comprise two switching elements. In this way, the overall space for the switching elements is further reduced, since they can be combined in switching devices.

The plurality of switching devices and / or the plurality of switching elements are expediently arranged on the countershaft axis. This makes the gearbox particularly simple and compact on the input shaft axis.

All switching devices on the countershaft axis advantageously each comprise two switching elements. This means that the installation space can be made even more compact with regard to the switching elements on the countershaft axis.

At least one switching device is expediently designed in such a way that a transmission element of a wheel plane on an axis of the transmission with different is used by means of the latter Shafts on the same axis of the transmission is connectable. This increases the flexibility with regard to the representation of different gears by said switching device (s), so that a sufficient number of gears can be made available. In the following, the “switching device” means a switching device by means of which a transmission element of a wheel plane on one axis of the transmission can be connected to different shafts on the same axis of the transmission.

At least two, in particular exactly two, of said switching devices are expediently arranged. As a result, the overall manufacturing outlay for the transmission is not significantly increased, since other shifting elements or shifting devices can be designed conventionally.

The at least two said switching devices are expediently arranged on different axes of the transmission. This further increases the flexibility of the transmission with regard to the representation of possible gears. At the same time, a simple manufacture of the transmission is possible since only one switching device has to be arranged on one axis of the transmission.

Advantageously, only one of the switching devices can be used to connect transmission elements in the sense of idler gears on the various shafts. This means that different gear planes can be coupled with other shafts particularly easily by means of said switching device, so that the flexibility of the transmission is increased.

The said switching devices are expediently each arranged between two wheel planes. This means that the installation space between the two respective wheel levels can be used efficiently.

At least one switching device, in particular comprising only one switching element, is advantageously arranged between the drive side and the first wheel plane. In this way, for example, the area between a double clutch and the first wheel plane can also already be used to represent gears by means of a shift element.

The output is expediently carried out via the countershaft, in particular with the input shafts and output shaft being arranged on the same side of the transmission. This means that the transmission can be made even more compact, since the drive and output take place on the same side of the transmission.

Advantageously, at least one reverse gear can be represented by means of at least one wheel plane. This further increases the flexibility of the transmission with regard to its use in different vehicles, since the vehicle can also be operated with a reverse gear.

The reverse gear stage can expediently be completely decoupled from the force and torque flow. In this way, for example, rotation of transmission elements of the wheel plane of the reverse gear stage is avoided, so that overall the efficiency of the transmission is increased when transmitting force and torque.

At least four reverse gears can advantageously be represented by means of said wheel plane. In this way, a sufficient number of reverse gears is made available, so that the flexibility of the transmission with regard to use in different vehicles is further increased.

At least one wheel plane can expediently be actuated by means of two different switching devices. This also increases the flexibility of the transmission when displaying different gears.

Advantageously, at least one space between two adjacent wheel planes is free of switching devices and / or at least one switching device is arranged in each case between two adjacent wheel planes on different axes. If the space between two adjacent wheel planes is free of switching devices, they can be arranged extremely compactly next to one another in the gearbox. If at least one switching device is arranged between two adjacent wheel planes on different axes, the installation space between two wheel planes is used very efficiently, so that the transmission can be made compact in the axial direction.

The transmission elements in the sense of fixed wheels of wheel planes are expediently arranged on the input shaft axis furthest from the drive side in the transmission. This enables a simple manufacture of the side of the gear in the axial direction opposite the drive side.

To represent the forward and / or reverse gears, an odd number of wheel planes can advantageously be integrated into the force and torque flow from the drive side to the output side. This means that many gears can be integrated with just one wheel level and therefore also few shift elements, so that the efficiency of the transmission is improved.

The lowest two, in particular the lowest four forward gears can expediently be represented as winding gears. This also enables a particularly compact design of the transmission.

Advantageously, a switching device is arranged on each input shaft axis and countershaft axis, which comprises only one switching element, in particular wherein the respective switching element for driving on the input shaft axis and for driving on the countershaft axis is arranged next to one another with respect to further switching elements on the same axis. This simplifies the design of the input area of the gearbox or the output area of the gearbox.

Advantageously, four reverse gears are represented in a method according to claim 22 by actuating the shift elements corresponding to the first four gears and additionally actuating a ninth shift element. In this way, a particularly simple representation or shifting of reverse gears is possible through the transmission.

Further important features and advantages of the invention emerge from the subclaims, from the drawings and from the associated description of the figures on the basis of the drawings.

It goes without saying that the features mentioned above and those yet to be explained below can be used not only in the combination specified in each case, but also in other combinations or on their own without departing from the scope of the present invention.

Preferred embodiments and embodiments of the invention are shown in the drawings and are explained in more detail in the following description, the same reference numerals referring to the same or similar or functionally identical components or elements.

• 1 ein Getriebe gemäß einer ersten Ausführungsform der vorliegenden Erfindung;
• 2 eine Schaltmatrix für ein Getriebe gemäß 1;
• 3 ein Getriebe gemäß einer zweiten Ausführungsform der vorliegenden Erfindung und
• 4 eine Schaltmatrix für ein Getriebe gemäß 3.

Each show in schematic form

• 1 a transmission according to a first embodiment of the present invention;
• 2nd a switching matrix for a transmission according 1 ;
• 3rd a transmission according to a second embodiment of the present invention and
• 4th a switching matrix for a transmission according 3rd .

1 shows a transmission according to a first embodiment of the present invention.

In 1 denotes reference numerals 1 a transmission in the form of a double clutch transmission. The dual clutch transmission 1 has two powershift elements in the form of clutches K1 , K2 on. By means of the double clutch K1 , K2 can drive side ON with the output side on the same side FROM of the transmission 1 be coupled or connected for the transmission of force and torque. For this, the clutch is first K1 with a first input shaft EW1 connected and the second clutch K2 is with a second input shaft EW2 connected. The first input wave EW1 is designed as a solid shaft, whereas the second input shaft EW2 is designed as a hollow shaft. The two input waves EW1 , EW2 are arranged coaxially and parallel to each other.

The transmission also includes 1 two sub-transmissions 2nd , 3rd . The first partial transmission 2nd is with the first input shaft EW1 connected and the second sub-transmission 3rd is with the second input shaft EW2 connected. The transmission also includes 1 an input shaft axis 4th on which the two input shafts EW1 , EW2 are arranged. Torque and power flow downstream of the drive side ON starting from the two clutches K1 and K2 on the input shaft axis 4th includes the transmission 1 first a first switching element S1 in a first switching device SE1 , a first wheel plane a , a second switching element S2 and a third switching element S3 arranged in a second switching device SE2 , a second wheel plane b , a third wheel plane c , a fourth wheel plane d and a fifth wheel plane e .

The first sub-transmission 2nd are the fourth wheel plane d and the fifth wheel plane e assigned, whereas the second sub-transmission 3rd the first wheel plane a , the second wheel plane b and the third wheel plane c assigned.

Each of the wheel levels mentioned a , b , c , d , e has transmission elements, in particular in the form of gear wheels, each with a shaft of the transmission 1 are connected or connectable.

On the input shaft axis 4th is still a first hollow shaft H1 arranged, the coaxial and parallel to the second input shaft designed as a hollow shaft EW2 is arranged on the radial outside.

Parallel to the input shaft axis 4th is a countershaft axis 5 for a countershaft 6 arranged. The transmission 6 includes a first countershaft VW1 and the output shaft AW , which are each designed as solid shafts and a second countershaft VW2 , which is designed as a hollow shaft. The second countershaft designed as a hollow shaft VW2 is coaxial and parallel to the first countershaft VW1 in the area of the third wheel plane c and the fourth wheel plane d arranged.

Starting from the drive side ON and the output side lying on the same side FROM points the transmission 1 on the countershaft axis 5 first the first wheel plane a on, a fourth switching element S4 arranged in a third switching device SE3 , the second wheel plane b , a fifth switching element S5 and a sixth switching element S6 arranged in a fourth switching device SE4 , the third wheel plane c and the fourth wheel plane d , a seventh switching element S7 and an eighth switching element S8 , arranged in a fifth switching device SE5 as well as the fifth wheel level e .

Below are the eight switching elements S1 , S2 , S3 , S4 , S5 , S6 , S7 and S8 described.

The first switching element S1 is on the input shaft axis 4th arranged and on the one hand with the first hollow shaft H1 , on the other hand with the second input shaft EW2 connected and, when actuated, establishes a connection for the transmission of force and torque between these two shafts. On the first hollow shaft H1 is a transmission element of the first wheel level a firmly arranged.

The second switching element S2 is on the input shaft axis 4th arranged and on the one hand with the first hollow shaft H1 , on the other hand with a transmission element of the second wheel plane b connected and provides a connection between the first hollow shaft when actuated H1 and the second wheel plane b forth. The transmission element of the second wheel plane b on the input shaft axis 4th is freely rotatable on the second input shaft EW2 stored.

The third switching element S3 is on the input shaft axis 4th arranged and on the one hand with the transmission element of the second wheel plane b on the input shaft axis 4th connected and on the other hand to the second input shaft EW2 and establishes a connection between the second input shaft when actuated EW2 and the second wheel plane b forth.

The fourth switching element S4 is on the countershaft axis 5 arranged and connects the output shaft when actuated AW and the first countershaft VW1 , which are both designed as solid waves.

The fifth switching element S5 is on the countershaft axis 5 arranged and on the one hand with the first countershaft VW1 , on the other hand with the transmission element of the third wheel plane c on the countershaft axis 5 connected and establishes a connection between these two when actuated. The transmission element of the third wheel plane c on the countershaft axis 5 is on the second countershaft VW2 freely rotatable.

The sixth switching element S6 is on the countershaft axis 5 arranged and on the one hand with the transmission element of the third wheel plane c on the countershaft axis 5 connected, on the other hand to the second countershaft VW2 and establishes a connection between these two when actuated.

The seventh switching element S7 is on the countershaft axis 5 arranged and on the one hand with the first countershaft VW1 , on the other hand with the second countershaft VW2 connected and establishes a connection between these two when actuated.

The eighth switching element S8 is on the countershaft axis 5 arranged and is on the one hand with the first countershaft VW1 , on the other hand with the transmission element of the fifth wheel plane e on the countershaft axis 5 connected and establishes a connection between these two when actuated.

The transmission element of the third wheel plane c on the input shaft axis 4th is in the sense of a fixed gear for the second input shaft EW2 trained and the transmission elements of the fourth wheel plane d and the fifth wheel plane e are in the sense of fixed wheels for the first input shaft EW1 educated. The transmission element of the first wheel plane a on the countershaft axis 5 is in the sense of a fixed gear for the output shaft AW trained and the transmission element of the second wheel plane b on the countershaft axis 5 is in the sense of a fixed gear for the first countershaft VW1 educated. The transmission element of the fourth wheel plane d on the countershaft axis 5 is in the sense of a fixed gear for the second countershaft VW2 trained and the transmission element of the fifth wheel plane e in the sense of an idler gear for the first countershaft VW1 .

The sequence of the waves on the countershaft axis 5 is starting from the drive side ON , what a 1 is shown on the left as follows: output shaft AW , first countershaft VW1 , and in a portion of the first countershaft VW1 , d .H. in the area of the two wheel planes c , d , the countershaft VW2 coaxial and parallel to the first countershaft VW1 .

The switching devices SE2 , SE4 and SE5 can be designed as double synchronizations, the switching devices SE1 and SE3 as Simple synchronizations. If two switching elements are arranged together in one switching device, they can be actuated by means of a common switching element actuating device.

Overall, the transmission shows 1 according to 1 two input shafts EW1 , EW2 on the input shaft axis 4th on, the second input shaft EW2 as a hollow shaft and the first input shaft EW1 is designed as a solid shaft. On the input shaft axis 4th parallel countershaft axis 5 are two countershaft axes VW1 , VW2 arranged, the first countershaft VW1 as a hollow shaft and the other countershaft VW2 is arranged coaxially and parallel to and in a partial area thereof and is designed as a hollow shaft. The countershaft axis also has 5 the output shaft AW on, which is designed as a solid shaft.

The gear 1 according to 1 comprises five wheel levels a , b , c , d and e . The wheel planes ae are designed in particular as standard gear stages with discrete gear ratios. Per wheel level ae are two transmission elements, in particular in the form of gears. A total of ten transmission elements are thus arranged, in particular in the form of gear wheels.

Overall, the embodiment of the 1 at least nine forward gears are provided.

2nd shows a switching matrix for a transmission according to 1 .

In 2nd is a shift matrix for a transmission 1 according to the 1 shown. Columns are horizontal for each switching element S1-S8 as well as for the two clutches K1 and K2 shown. The nine forward gears, designated by the reference numerals, are perpendicular to this downwards V1-V9 , shown. Another column, labeled "Wheels", shows that for the respective forward gear V1-V9 integrated wheel planes ae .

The entries left blank in the shift matrix, for example in the forward gear stage V1 at the clutch K1 as well as the switching elements S1 , S3 , S4 , S5 , S7 indicate that the corresponding shift element or clutch is open, ie that the shift element or clutch does not have any forces or torque from the shaft or transmission element connected to the shift element or clutch or to the respective shaft or transmission element transmits. An entry with a dot in the shift matrix designates a correspondingly actuated or closed shift element or clutch, that is to say in the shift matrix for the forward gear stage V1 , with the clutch K2 and the switching elements S2 , S6 and S8 . In the "Wheels" column are the forward gear V1 the wheel planes c , d , b , a listed, that is, on the one hand, all wheel planes to represent the forward gear V1 secondly, the sequence shows the torque flow, ie that initially only the second input shaft EW2 that over the clutch K2 is pressed and then the third wheel level c is acted upon and then further by actuating the sixth switching element S6 the fourth wheel plane d and then the fifth wheel level e . Then by pressing the eighth switching element S8 then becomes the first countershaft VW1 loaded with force and torque. In the further course, the first countershaft VW1 then the second wheel plane b acted upon with force and torque, which by actuation of the second switching element S2 with the first wheel plane a is connected, which in turn is connected to the output shaft AW connected is. This way the first forward gear V1 shown.

Overall, the switching matrix according to 2nd at least nine forward gears V1-V9 by means of the transmission 1 according to 1 to provide.

3rd shows a transmission according to a second embodiment of the present invention.

In 3rd is essentially a gearbox 1 according to 1 shown. In contrast to the transmission 1 according to 1 points the transmission 1 according to 3rd another wheel plane R on, which is used to represent at least one reverse gear. This is in the third switching device SE3 a ninth switching element S9 arranged, which is a transmission element of the reverse gear stage R to the first countershaft VW1 on the countershaft axis 5 couples. The transmission element of the reverse gear stage R on the input shaft axis 4th is a fixed gear on the hollow shaft H1 educated. The sequence of switching elements and wheel planes on the input shaft axis 4th Starting from the drive side is as follows: First switching element S1 , first wheel plane a , Reverse gear R , second switching element S2 , third switching element S3 , second wheel plane b , etc. The sequence of switching elements and gear levels on the countershaft axis 5 is then as follows: First wheel level a , fourth switching element S4 , ninth switching element S9 , Reverse gear R , second wheel plane b , etc.

4th shows a switching matrix for a transmission according to 3rd .

In 4th is a corresponding switching matrix according to 2nd shown, supplemented by four reverse gears R1-R4 . There was also a column for the ninth switching element S9 inserted. The representation of the reverse gears R1-R4 is the same as for the forward gears V1-V4 , with the reverse gears R1-R4 additionally the ninth switching element S9 is actuated. The column of wheels is used instead of the second wheel level b the reverse gear R integrated with otherwise the same sequence of the wheel planes.

In summary, the invention has the advantage that the transmission is of extremely compact construction, it being possible to implement at least nine gears with eight shift elements or nine shift elements with additional reverse gears. The first four courses V1-V4 are designed as turns. The transmission has a total of five wheel levels ae or six wheel levels ae , R and builds compact.

Reference list

1

transmission

2, 3

Partial transmission

4th

Input shaft axis

5

Countershaft axis

6

Gear

a, b, c, d, e

Wheel plane

R

Wheel level reverse gear

ON

Drive side

FROM

Output side

EW1, EW2

Input shaft

VW1, VW2

Countershaft

H1

Hollow shaft

AW

Output shaft

V1, V2, V3, V4, V5, V6, V7, V8, V9

Forward gear

R1, R, R3, R4

Reverse gear

S1, S2, S3, S4, S5, S6, S7, S8, S9

Switching element

SE1, SE2, SE3, SE4, SE5

Switching device

Claims (24)

Transmission (1), in particular double clutch transmission, for a motor vehicle, comprising at least two partial transmissions (2, 3), each of the partial transmissions (2, 3) comprising at least one input shaft (EW1, EW2) and one output shaft as the output shaft (AW) of both Sub-transmission (2, 3) is arranged and the at least two input shafts (EW1, EW2) are arranged on an input shaft axis (4) and the output shaft (AW) on the input shaft axis (4) or on one, in particular parallel to the input shaft axis (4) Countershaft axis (5) or output shaft axis is arranged, and wherein a countershaft (6) is arranged with at least one countershaft (VW1, VW2), the at least one countershaft (VW1, VW2) being arranged on said countershaft axis (5) and at least one the input shafts (EW1, EW2) by means of at least one wheel plane (a, b, c, d, e) and / or at least one switching element (S1, S2, S3, S4, S5, S6, S7, S8) with the output shaft (AW ) connect dbar, characterized in that a maximum of five wheel planes (a, b, c, d, e) and a maximum of five shifting devices (SE1, SE2, SE3, SE4, SE5) are arranged such that at least nine forward gears (V1, V2, V3 , V4, V5, V6, V7, V8, V9) can be represented by the transmission (1). Gearbox according to Claim 1 , characterized in that exactly five wheel planes (a, b, c, d, e) are arranged. Gearbox according to one of the Claims 1 - 2nd , characterized in that the plurality of switching devices (SE2, SE4, SE5) each comprise two switching elements (S2, S3; S5, S6; S7, S8). Gearbox according to one of the Claims 1 - 3rd , characterized in that the plurality of switching devices (SE3, SE4, SE5) and / or the plurality of switching elements (S4, S5, S6, S7, S8) is arranged on the countershaft axis. Gearbox according to one of the Claims 1 - 4th , characterized in that all switching devices (SE3, SE4, SE5) on the countershaft axis (5) each comprise two switching elements (S4, S9; S5, S6; S7, S8). Gearbox according to one of the Claims 1 - 5 , characterized in that at least one switching device (SE2, SE4) is designed so that by means of this a transmission element of a wheel plane (b; c) on an axis (4; 5) of the transmission (1) with different shafts (H1, EW2 ; VW1, VW2) on the same axis (4, 5) of the transmission (1) can be connected. Gearbox according to Claim 6 , characterized in that at least two, in particular exactly two of said switching devices (SE2, SE4) are arranged. Gearbox according to Claim 7 , characterized in that the at least two said switching devices (SE2, SE4) are arranged on different axes (4, 5) of the transmission (1). Gearbox according to one of the Claims 6 - 8th , characterized in that by means of one of said switching devices (SE2) only transmission elements in the sense of idler gears on the different shafts (EW2, H1) can be connected. Gearbox according to one of the Claims 7 - 9 , characterized in that said switching devices (SE2, SE4) are each arranged between two wheel planes (a, b; b, c). Gearbox according to one of the Claims 1 - 10th , characterized in that at least one switching device (SE1), in particular comprising only one switching element (S1), is arranged between the drive side (AN) and the first wheel plane (a). Gearbox according to one of the Claims 1 - 11 , characterized in that the output takes place via the countershaft (6), in particular with input shafts (EW1, EW2) and output shaft (AW) being arranged on the same side of the transmission (1). Gearbox according to one of the Claims 1 - 12th , characterized in that at least one reverse gear (R1, R2, R3, R4) can be represented by means of at least one wheel plane (R). Gearbox according to Claim 13 , characterized in that the reverse gear stage (R) can be completely decoupled from the force and torque flow. Gearbox according to one of the Claims 13 - 14 , characterized in that at least 4 reverse gears (R1, R2, R3, R4) can be represented by means of said wheel plane (R). Gearbox according to one of the Claims 1 - 15 , characterized in that at least one wheel plane (a) can be actuated by means of two different switching devices (SE1, SE2). Gearbox according to one of the Claims 1 - 16 , characterized in that at least one space between two adjacent wheel planes (c, d) is free of switching devices and / or at least one switching device (SE2, SE3) is arranged between two adjacent wheel planes (a, b) on different axes (4, 5) . Gearbox according to one of the Claims 1 - 17th , characterized in that the transmission elements in the sense of fixed wheels of wheel planes (c, d, e) on the input shaft axis (4) are arranged furthest away from the drive side (AN) in the transmission (1). Gearbox according to one of the Claims 1 - 18th , characterized in that to represent the forward (V1, V2, V3, V4, V5, V6, V7, V8, V9) and / or reverse gears (R1, R2, R3, R4) an odd number of wheel planes (a , b, c, d, e, R) can be integrated into the power and torque flow from the drive side (AN) to the output side (AB). Gearbox according to one of the Claims 1 - 19th , characterized in that the lowest two, in particular the lowest four forward gears (V1, V2, V3, V4) can be represented as winding gears. Gearbox according to one of the Claims 1 - 20 , characterized in that a switching device (SE1; SE3) is arranged on the input shaft axis (4) and countershaft axis (5), which comprises only one switching element (S1; S4), in particular wherein the respective switching element (S1; S4) for driving next to the input shaft axis (4) and for output on the countershaft axis (5) with respect to further switching elements (S2, S3; S5, S6) on the same axis (4, 5). Method for operating a transmission (1) according to one of the Claims 1 - 21 , characterized in that a first gear (V1) is represented by means of actuated second, sixth and eighth shift elements (S2, S6, S8) and in that a second gear (V2) is represented by means of actuated second and eighth shift elements (S2, S8), and that a third gear (V3) is represented by actuated second and fifth shift elements (S2, S5) and that a fourth gear (V4) is represented by actuated second and seventh shift elements (S2, S7), and that a fifth gear (V5 ) is represented by actuated first shift element (S1), and that a sixth gear (V6) is represented by actuated fourth and eighth shift element (S4, S8), and that a seventh gear (V7) is actuated by actuated fourth and fifth shift element (S4, S5) is shown, and that an eighth gear (V8) is actuated by means of actuated fourth and seventh shift elements (S4, S7), and that a ninth gear (V9) is actuated by means of actuated third and fourth shift elements (S3, S4) is set, whereby the other shift elements are open or are in neutral position and a first clutch (K1) is engaged in the even gears (V2, V4, V6, V8) and a second clutch (K2) in the odd gears ( V1, V3, V5, V7, V9) is closed and the other clutch (K2, K1) is open. Procedure according to Claim 22 , characterized in that four reverse gears (R1, R2, R3, R4) are represented by actuating the shift elements corresponding to the first four gears (V1, V2, V3, V4) and actuating a ninth shift element (S9). Motor vehicle, in particular a passenger or a truck, with a transmission (1) according to one of the Claims 1 to 21 and / or operated with a method according to one of the Claims 22 - 23 .

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