DE102012203065A1 - Transmission i.e. dual clutch transmission, for e.g. passenger car, has shifting arrangements arranged in region of output of transmission and adjacent to plane, and jackshafts connected together by one of arrangements on secondary axis - Google Patents

Abstract

The transmission (1) has input shafts (EW1, EW2) arranged on a main axis (2) that is arranged parallel to a secondary axis (3). Jackshafts (VW1, VW2, VW3a) are arranged on the secondary axis. The input shafts are connected with a driven shaft (AW) by wheel planes (I-VI) and shifting elements (S1-S7), and shifting arrangements (SE1, SE2, SE3, SE4) are arranged on the main and secondary axes. The arrangements are arranged in a region of an output (AB) of the transmission and adjacent to one of the planes. The jackshafts are connected together by one of the arrangements on the secondary axis. The wheel plane is designed as a reverse gear stage.

Description

The invention relates to a transmission, in particular dual-clutch transmission, for a motor vehicle, comprising at least two partial transmissions, wherein each of the partial transmission comprises at least one input shaft, and wherein an output shaft is arranged as the output shaft of both partial transmission, wherein the at least one input shaft on a main axis and the output shaft the at least one countershaft is arranged on the minor axis, and wherein at least one of the input shafts by means of at least two gear planes and / or at least a switching element with the output shaft is connectable.

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

By alternately splitting the gears on the two partial transmissions, it is possible to already select a subsequent gear when driving in a gear assigned to a sub-gear in the other sub-transmission by appropriate actuation of the switching devices, with a final change in the subsequent gear by opening the Power shift element of a partial transmission and a subsequent subsequent closing of the load switching element of the other sub-transmission is made possible. In this way, the gears or gear ratios of the transmission can be switched under load, which improves an acceleration capacity of the motor vehicle due to a substantially traction-free gear change and allows more comfortable switching operations for a driver.

Such dual-clutch transmissions can in this case also be designed with a countershaft additionally arranged for input and output, so that a compact construction is made possible in the axial direction.

From the DE 10 2006 054 281 A1 Such a transmission for a motor vehicle in the form of a dual-clutch transmission has become known. The dual-clutch transmission comprises two partial transmissions, each with an input shaft. By connecting the respective input shaft via a respective load switching element, the two partial transmissions can each be alternately incorporated into a force or torque flow from a drive to an output, wherein the input shaft of the first subtransmission is designed as Getriebzentral- and the input shaft of the second subtransmission as a hollow shaft transmission. Furthermore, an output shaft is arranged, which is designed as an output of both partial transmissions, wherein a rotational movement of the drive can be translated over several translation stages to the output, in which the force and torque flow is guided via a countershaft. In this case, at least two wheel planes are switched by means of actuation of associated switching elements in the force and torque flux, wherein a plurality of gear ratios can be represented by combining the actuation of the switching elements and the force and torque flow over corresponding wheel plane. Likewise, an untranslated transmission of the rotational movement of the drive to an output shaft of the output by operating corresponding switching elements is possible.

It is therefore an object of the present invention to provide improved power shifting capability and improved hybridization capability of the transmission. Moreover, it is an object of the present invention to provide a transmission for a motor vehicle, which is simple and inexpensive to produce and at the same time allows reliable transmission of torque between the drive and output. Moreover, it is an object of the present invention to provide an alternative transmission for a motor vehicle.

The present invention solves the problems in a transmission, in particular dual-clutch transmission, for a motor vehicle comprising at least two partial transmissions, each of the partial transmissions comprises at least one input shaft, and wherein an output shaft is arranged as the output shaft of both partial transmissions, wherein the at least one input shaft on a main axis and the output shaft is arranged on the main axis or on a, in particular parallel to the main axis, minor axis and wherein a countershaft with at least one countershaft is arranged, wherein the at least one countershaft on the minor axis is arranged, and wherein at least one of the input shafts by means of at least two gear planes and / or at least one switching element with the output shaft is connectable, characterized in that N switching means are arranged, wherein N is a positive integer greater than or equal to two, wherein at least one of the N switching means are arranged on the main axis and on the minor axis, and that one of the at least one switching device is arranged on the minor axis in the region of the output of the transmission, in particular adjacent to at least one torque downstream arranged wheel plane, and that by means of a switching device on the minor axis second countershaft with the first countershaft can be coupled.

The invention solves the problem also in a motor vehicle, in particular a passenger or a truck, with a transmission according to one of claims 1 to 16.

One of the advantages achieved thereby is that it allows a reduction of the mechanical spread by winding the first forward gear of the transmission. Likewise, the transmission also offers improved load shifting capability and good hybridizability.

The term "wheel stage" or "wheel plane" are preferably to be understood in the description, in particular in the claims, essentially two mutually cooperating transmission elements for transmitting torques from the one transmission element to the other transmission element, preferably a sub- or translation for provide in particular with the transmission elements cooperating waves in the transmission.

The term "switching element" is preferably in the description, in particular in the claims, a device having at least one open and a closed state, wherein in the open state, the device no torque and wherein in the closed state, the device torque between two can transmit with the switching element cooperating devices.

The term "switching device" is preferably to be understood in the description, in particular in the claims, at least one switching element and at least one switching element actuation device for actuating the at least one switching element.

The term "transmission element" is preferably in the description, in particular in the claims to understand a device with which a torque is transferable. Transmission elements can preferably be designed as wheels, preferably as gears, in particular spur gears, bevel gears, worm wheels or the like.

The term "adjacent" with respect to switching elements and / or switching devices are preferably to be understood in the description, in particular in the claims switching devices and / or switching elements, which are arranged along the main axis or the minor axis of the transmission directly adjacent to each other along the respective axis and wherein each one of the switching elements of the switching means is connected by means of a shaft directly to the respective other switching element of the adjacent switching device.

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

Advantageously, the N switching devices are arranged symmetrically with respect to each other with regard to their axial position on the main axis and the minor axis. For example, an arrangement along the major and minor axes from the drive side to the output side is possible as follows: A first switching device is arranged on the minor axis, a second and third switching device are arranged on the main axis and a fourth switching device is in turn arranged on the minor axis. This allows for a simpler manufacture of the transmission, on the other hand is thus a more compact design of the transmission in terms of axial extent possible.

Advantageously, the N switching devices are arranged alternately in the axial direction along the main axis and the minor axis. The advantage thus achieved is that an even more compact design with respect to the axial extent of the transmission along the main axis and minor axis is made possible. Since the switching devices are arranged alternately on different axes along the transmission, they can each have a shorter distance in terms of their axial position be arranged to each other.

Conveniently, at least one wheel plane is designed as the output constant. The advantage thus achieved is that it enables a reliable transmission of force and torque from the drive via at least one input shaft through the transmission to the output shaft for the output. In the formation of the gear plane as the output constant, the respective transmission elements, in particular in the form of gears, are fixedly arranged on the respective shafts.

Advantageously, at least two of the input shafts are arranged coaxially with one another and / or the second countershaft is arranged coaxially with respect to the at least one countershaft. This reduces the space for the two input shafts and / or for the two countershafts and thus also of the corresponding transmission as a whole, so that the transmission can also be used in cramped conditions in a motor vehicle. Likewise, this can save space several countershafts are provided, which allows a representation of a variety of gears respectively gear ratios by means of the transmission.

Conveniently, the number N is equal to four. So are arranged N = 4 switching devices, a variety of forward and reverse gears can be represented by the transmission, while the transmission can be made compact.

Advantageously, at least one of the input shafts is designed as a hollow shaft and the respective other shaft as a solid shaft. Also, at least one of the countershafts as a solid shaft and at least one other countershaft can be formed as a hollow shaft. For a particularly space-saving arrangement of the two input shafts and / or countershafts is possible because the input shaft or countershaft formed as a hollow shaft coaxial and parallel to the solid shaft formed as input shaft or countershaft can be arranged. In the training as a solid shaft or a hollow shaft, respective transmission elements, if they are firmly connected to the hollow shaft or solid shaft, with the respective shaft can be made in one piece and thus cost. A time-consuming and therefore costly determination of the respective transmission elements on the corresponding shaft can thus be dispensed with.

Conveniently, at least three, in particular at least four wheel planes can be connected to at least one of the input shafts by means of at least one switching element. In this way, for example, if transmission elements of a plurality of wheel planes can be connected or coupled to at least one of the input shafts, a multiplicity of possible gears or gear steps can be provided, without a large number of components being required for this purpose.

Advantageously, at least one wheel plane is designed as a reverse gear. By means of the at least one reverse gear stage, the direction of rotation of the output shaft with respect to one of the input shafts can be reversed, so that a reverse gear for a vehicle can be provided, which substantially increases the flexibility with regard to the use of the transmission in different vehicles.

Conveniently, the reverse gear is disposed between two adjacent switching devices. If the two adjacent switching devices are arranged on the main axis or on the minor axis, a space-saving arrangement of the switching devices is possible, wherein in particular at least one of the two switching devices is designed to actuate the reverse gear step. Are the two switching devices arranged on separate axes, d. H. one of the switching devices is arranged on the main axis and the other switching device is arranged on the minor axis, wherein the reverse gear is then arranged between these two switching devices, a more space-saving arrangement of the reverse gear and the two switching devices is possible because these due to the axial offset at a shorter distance can be arranged to each other.

Advantageously, the reverse gear is arranged directly adjacent to the side of the drive in the transmission. One of the advantages achieved with this is that the reverse gear for transmitting power and torque can be coupled in a particularly reliable manner to one of the input shafts.

Conveniently, an electric machine is arranged on at least one wheel plane and / or on at least one countershaft and / or on at least one of the input shafts for hybridizing the transmission. One of the advantages achieved is that the transmission can also be used in hybrid vehicles where both an electric machine and an internal combustion engine are to interact with the transmission to transmit forces to drive the hybrid vehicle. The connection of the at least one electric machine can be made to at least one of the input shaft or output shaft or at least one of the countershafts. The electric machine can also be connected to a transmission element in the form of a fixed wheel or idler gear of one of the wheel planes.

It is also possible to connect the electric machine to an additional fixed gear, that is to a wheel which is fixedly connected to one of the shafts of the gearbox. It is particularly advantageous to make the connection of the electric machine to the transmission by means of at least one switching element, in particular to a transmission element of a wheel plane. The advantage achieved with this first connection possibility is that thus a so-called stand-load capacity and an electric driving without drag losses in the transmission is possible. For this purpose, the disclosure content of DE 10 2010 030 569 A1 explicitly referred to by reference: In this case, a first input shaft with a load switching element can be coupled. A second input shaft, which is arranged in particular coaxially to the first input shaft, is directly connected to a rotor of the electric machine for driving it. As a result, two parallel power transmission branches can be coupled to one another on the input side.

A second connection or Ankoppelmöglichkeit the electric machine to the transmission is possible by arranging a planetary gear in the transmission: To a first input shaft can be coupled via a corresponding switching element, in particular in the form of a clutch, an internal combustion engine. The electric machine engages on the one hand on a second input shaft and on the other hand to the first input shaft of the transmission via a planetary gear. When actuated, so closed disconnect clutch of the engine is also coupled via the planetary gear to the second input shaft. The planetary gear, comprising a planetary gear, a ring gear, planetary gears and a planet carrier, is designed in this way and cooperates with the internal combustion engine and the electric machine so that the planet carrier acts on the second input shaft. The electric machine is coupled to the sun gear of the planetary gear. In addition, a further switching element may be arranged in the form of a bridging switching element, which cooperates with the planetary gear, so that when actuated lock-up switching element a rotationally fixed connection between the electric machine, the first input shaft and the second input shaft, whereas not actuated, so open, Bridging switching element, the aforementioned non-rotatable connection between the electric machine and the first and second input shaft does not exist, in particular so there is no speed equality between the two input shafts.

If a further switching element is arranged between the switching element which serves to connect the internal combustion engine to the first input shaft and bridging switching element, by means of this further switching element, in particular in the form of a double switching element, both the abovementioned first connection possibility and the aforementioned second connection possibility by actuation of the further switching element possible.

Advantageously, the electric machine is arranged on at least one of the wheel planes, which are connected to a countershaft, designed as a hollow shaft. This is a particularly simple connection or coupling of the electric machine to the transmission and thus a reliable force and torque transmission from the electric machine, ultimately, in particular to the output shaft, possible. In addition, by means of the arranged on the countershaft, designed as a hollow shaft gear planes multiple gear ratios for hybridization of the transmission can be provided, which significantly improves the flexibility in terms of the use of the transmission in various vehicles.

Expediently, transmission elements of at least two wheel planes on the minor axis are connected to a countershaft designed as a hollow shaft, in particular fixed. Thus, the transmission elements can be produced inexpensively together with the countershaft, in particular by a one-piece design of transmission elements, in particular in the form of gears, together with the corresponding countershaft. Likewise, a connection or coupling of an electrical machine to the transmission in a very reliable manner possible.

Advantageously, the N switching devices and the at least two wheel planes are arranged so that at least six forward gears and at least two reverse gears are represented by the transmission. In this way, a sufficient number of forward gears and reverse gears can be provided by the transmission for a variety of different vehicles, preferably both for passenger cars and for trucks.

Conveniently, by means of a switching device on the minor axis a countershaft with in each case one at least two other countershafts connected. In this way, by means of the switching device, a countershaft can be coupled to one and / or the other of the two countershafts. On the outside of a countershaft transmission elements of a wheel plane can then be arranged so that it can be connected via one or more wheel planes on the main axis via the countershaft, which allows a representation of a variety of possible gears or gear ratios through the transmission.

Further important features and advantages of the invention will become apparent from the subclaims, from the drawings, and from associated figure description with reference to the drawings.

It is understood that the abovementioned and those still to be explained below Characteristics can be used not only in the specified combination, but also in other combinations or in isolation, without departing from the scope of the present invention.

Preferred embodiments and embodiments of the invention are illustrated in the drawings and will be described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components or elements.

In each case show in a schematic form

1 a transmission according to a first embodiment of the present invention;

2 a shift matrix for a transmission according to the first embodiment of the present invention;

3a a transmission according to a second embodiment of the present invention;

3b a transmission according to a third embodiment of the present invention;

3c a transmission according to a fourth embodiment of the present invention; such as

4 a transmission according to a fifth embodiment of the present invention.

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

In 1 denotes reference numeral 1 a transmission in the form of a dual-clutch transmission. The dual-clutch transmission 1 has two load switching elements in the form of clutches K1, K2. By means of the double clutch K1, K2 can be one side of a drive AN with one side of an output AB of the transmission 1 be coupled for transmission of force and torque. For this purpose, the first clutch K1 is connected to a first input shaft EW1 and the second clutch K2 is connected to a second input shaft EW2. The second input shaft EW2 is designed as a hollow shaft, whereas the first input shaft EW1 is formed as a solid shaft. The two input shafts EW1, EW2 are arranged parallel and coaxial with each other. Furthermore, the transmission includes 1 a major axis 2 , the torque and power downstream of the drive AN starting from the two clutches K1, K2 first a first gear plane I , a first switching element S1, a second switching element S2 and a sixth gear plane VI and further comprises a third switching element S3, a second gear plane II , a third wheel plane III , a fourth switching element S4, a fifth switching element S5, a fourth gear plane IV and a fifth wheel plane V , Each of the mentioned wheel planes I . II . III . IV . V and VI has transmission elements, in particular in the form of gears, which are each connected to a shaft of the transmission. This sixth wheel step VI points between the transmission element on the main axis 2 and the transmission element on a minor axis 3 an idler gear ZR for reversing the direction of rotation; the sixth wheel plane VI is thus designed as a reverse gear. The fourth and fifth wheel plane IV . V are connectable to an output shaft AW of the drive AB at least one switching element.

Parallel to the main axis 2 is the minor axis 3 for a counterfeit 4 arranged. The counterpart 4 comprises a first countershaft VW1, which is designed as a solid shaft, and a, arranged in a portion of the first countershaft VW1 and formed as a hollow shaft second countershaft VW2. Furthermore, a third countershaft VW3a is arranged, which is likewise designed as a hollow shaft and is arranged coaxially and parallel to the second countershaft VW2. On the first countershaft VW1 are transmission elements for the wheel planes I . V and VI arranged to transmit force and torques between the main axis 2 and minor axis 3 , The second to the first countershaft VW1 coaxial countershaft VW2 includes transmission elements for the wheel planes II and III , The third to the second countershaft VW1 coaxially arranged countershaft VW3a comprises a transmission element for the fourth gear plane IV ,

The sequence of wheel planes and switching elements on the minor axis 3 starting on the side of the drive AN is as follows: First gear plane I , sixth wheel plane VI , second wheel plane II , third wheel plane III , fourth wheel plane IV , sixth switching element S6, seventh switching element S7 and fifth wheel plane V , Between the minor axis 3 and the main axis 2 indicates the sixth wheel plane VI in the form of the reverse gear intermediate gear ZR for reversing the direction of rotation, so that by means of the output shaft AW in the same direction of rotation of the input shafts EW1, EW2 a reverse direction of rotation to provide at least one reverse gear through the transmission 1 is possible.

The switching elements S1, S2, S3, S4, S5, S6 and S7 will now be described below. When actuated, the first switching element S1 establishes a connection for transmitting force and torques between the second input shaft EW2 and a first hollow shaft H1, which is arranged parallel and coaxial with the second input shaft EW2. On the first hollow shaft H1 a transmission element is arranged, which with a Transmission element on the first countershaft VW1 for transmitting force and torque between two waves, namely substantially the second input shaft EW2 and the first countershaft VW1, cooperates. The two transmission elements form the first wheel plane I , The second switching element S2, when actuated, establishes a connection for transmitting force and torques between the second input shaft EW2 and a second hollow shaft H2, which is arranged parallel and coaxial to the second input shaft EW2. On the second hollow shaft H2, a transmission element is arranged which cooperates with a transmission element on the first countershaft VW1 for transmitting force and torques between two shafts, namely substantially the second input shaft EW2 and the first countershaft VW1. Between the two transmission elements, an intermediate ZR is arranged to reverse the direction of rotation. The two transmission elements together with the intermediate gear ZR form the sixth gear plane VI in the form of reverse gear. The two switching elements S1, S2 are combined to form a common first switching device SE1 and can be actuated by means of a common switching element actuation device SB1, ie can be brought into an open or a closed state.

The third switching element S3 is connected to the second input shaft EW2 and a third hollow shaft H3, which is arranged parallel and coaxial with the second input shaft EW2. When actuated, the third shift element S3 thus establishes a connection for the transmission of force and torques between the second input shaft EW2 and the third hollow shaft H3. On the third hollow shaft H3, a transmission element is arranged, which cooperates with a transmission element on the second countershaft VW2 for transmitting force and torque between two shafts, namely substantially the second input shaft EW2 and the second countershaft VW2. The two transmission elements form the second wheel plane II , The third switching element S3 is arranged in a second switching device SE2 and can be actuated by means of a second switching element actuating device SB2.

The fourth switching element S4, when actuated, establishes a connection between the first input shaft EW1 and a fourth hollow shaft H4, which is arranged parallel and coaxial to the first input shaft EW1. Arranged on the fourth hollow shaft H4 is a transmission element, which interacts with a transmission element on the second countershaft VW2 for transmitting force and torques between essentially the first input shaft EW1 and the second countershaft VW2. The two transmission elements form the third wheel plane III ,

The fifth switching element S5, when actuated, establishes a connection between the first input shaft EW1 and the output shaft AW. The fourth switching element S4 and the fifth switching element S5 are in this case combined to form a common third switching device SE3 and can be actuated by means of a common third switching element actuating device SB3.

The sixth switching element S6, when actuated, establishes a connection between the second countershaft VW2 and a third countershaft VW3a, which is arranged parallel and coaxial to the second countershaft VW2. On the radial outer side of the third countershaft VW3a, a transmission element is arranged, which with a transmission element on the output side AW on the main axis 2 to form the fourth wheel plane IV interacts. In this way, essentially the second countershaft VW2 can be coupled to the output shaft AW. The seventh switching element S7, when actuated, establishes a connection between the first countershaft VW1 and the second countershaft VW2 for the transmission of force and torques. Furthermore, directly adjacent to the side of the output AB is a fifth gear plane V arranged. The fifth wheel plane V includes a transmission element on the first countershaft VW1 and a cooperating with this transmission element transmission element on the output shaft AW. The fifth wheel plane V is thus designed as output constant. The radial arrangement of the waves is as follows. On the outside of the first input shaft EW1, the second input shaft EW2 is arranged. On the outside of the second input shaft EW2 each of the first, second and third hollow shaft H1, H2, H3 are arranged. The fourth hollow shaft H4 is arranged on the outside of the first input shaft EW1. On the radial outer side of the first countershaft VW1, the second countershaft VW2 is arranged. On the outside of the second countershaft VW2, the third countershaft VW3a is arranged.

The sixth switching element S6 and the seventh switching element S7 are combined in a fourth switching device SE4 and actuated by means of a common fourth switching element actuating device SB4. The switching element actuators SB1, SB3 and SB4 may be implemented as double synchronizers, the second switching element actuation device SB2 as a single synchronization.

The transmission elements can be both solid and loose with the respective shaft, in particular with the input shafts EW1, EW2 and / or at least one of the countershafts VW1, VW2, VW3a and / or with the hollow shafts H1, H2, H3 and H4 are arranged or connected.

The transmission elements can be designed in the form of gears, in particular as spur gears, so that the wheel planes I . II . III . IV . V and VI Represent spur gears. To provide various forward and reverse gears, that is, various ratios, the spur gears, in particular their gears, may accordingly comprise or provide different ratios to provide different forward and / or reverse gears.

Overall, the gearbox has 1 according to 1 two input shafts EW1, EW2 on, one formed as a solid shaft and the other coaxial and parallel to this and formed as a hollow shaft on the main axis 2 , On the to the main axis 2 parallel minor axis 3 are arranged two countershafts VW1, VW2, one formed as a solid shaft and the other coaxial and parallel to this and designed as a hollow shaft. Furthermore, a third countershaft VW3 is designed as a hollow shaft and arranged coaxially with the second countershaft VW2. The gear 1 according to 1 includes six wheel levels I . II . III . IV . V and VI , where the sixth wheel plane VI is designed as a reverse gear. All wheel levels I to VI are designed in particular as spur gears with discrete ratios. Per wheel level I . II . III . IV . V . VI are each two transmission elements, in particular in the form of gears arranged. The reverse gear VI includes an additional gear in the form of an intermediate ZR. Altogether there are thus 13 transmission elements, in particular in the form of gears in the transmission 1 according to 1 arranged.

The wheel levels I . II . III and VI are coupled in particular by means of at least one switching element with at least one of the input shafts. The fourth wheel plane IV is coupled by means of the sixth switching element S6 to the second countershaft VW2. The first input shaft EW1 designed as a solid shaft can be coupled to the output shaft AW by means of the fifth switching element S5. The transmission elements of the wheel planes II and III on the second countershaft VW2 are firmly connected to this and can be coupled by means of the switching device SE4 to the first countershaft VW1. The transmission elements of the fifth wheel plane V are firmly connected both to the output shaft AW and to the first countershaft VW1. The fifth wheel plane V is thus as the output constant, as already mentioned above, formed.

Overall, by the embodiment of the 1 through the transmission 1 at least six forward gears and at least two reverse gears are provided.

2 shows a shift matrix for a transmission according to the first embodiment of the present invention.

In 2 is a switching matrix for a transmission 1 according to 1 shown. Horizontal are columns for each switching element S1 to S7 and for the two clutches K1 and K2 shown. Perpendicular to this down are first the six forward gear stages, indicated by the numbers 1 to 6, and two reverse gear stages, designated R1 and R2. The released in the switching matrix entries, so for example in the forward gear 1 in the switching elements S2, S5, S6 and S7 indicate that the corresponding switching element or coupling is open, that is, that the switching element or clutch in this case no forces or no torque transmits from the connected to the switching element or coupling respective waves. An entry in the switching matrix provided with a cross designates a correspondingly closed switching element or coupling, that is to say, for example, in the switching matrix in the forward gear stage 1 in the switching elements S3 and S4. In the closed state, the switching element or the coupling transmits torques from the respective shafts connected to the corresponding switching element or the coupling.

To the first gear by means of the transmission 1 according to 1 represent the clutch K1 are closed and the clutch K2 open and the switching elements S2, S5, S6, S7 open and the switching elements S1, S3, S4 closed. To represent the second gear, the clutch K1 are opened and the clutch K2 closed and the switching elements S2, S3, S4, S5, S6, S7 open and the switching element S1 is closed. To illustrate the third gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S5, S7 open and the switching elements S4 and S6 closed. To represent the fourth gear, the clutch K1 are opened and the clutch K2 closed and the switching elements S1, S2, S4, S5 and S7 open and the switching elements S3 and S6 closed. To represent the fifth gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S4, S6, S7 open and the switching element S5 closed. To represent the sixth gear, the clutch K1 are opened and the clutch K2 closed and the switching elements S1, S2, S4, S5, S6 open and the switching elements S3 and S7 closed. In order to represent the first reverse gear R1, the clutch K1 are closed and the clutch K2 is opened and the shifting elements S1, S5, S6, S7 are opened and the shifting elements S2, S3, S4 closed. To represent the second reverse gear R2, the clutch K1 are opened and the clutch K2 closed and the switching elements S1, S3, S4, S5, S6, S7 open and the switching element S2 closed.

Overall, there are thus six forward gears and two reverse gears through the transmission 1 according to 1 according to the switching matrix according to 2 represented.

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

In 3a is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 are at the transmission 1 according to 3a the first and sixth wheel planes I . VI in terms of their axial position along the major axis 2 and minor axis 3 arranged reversed. The transmission element of the reverse gear VI on the main axis 2 is now connected to the first hollow shaft H1 and connectable by means of the second switching element S2 with the second input shaft EW2. The first switching element S1 is now connected on the one hand to the second hollow shaft H2, on the other hand to the second input shaft EW2 and, when actuated, establishes a connection between the second hollow shaft H2 and the second input shaft EW2. The second switching element S2 and the first switching element S1 again form the first switching device SE1. The two switching elements S1, S2 can be actuated by means of the first switching element actuating device SB1. The sixth wheel plane VI Thus, by a transmission element on the first hollow shaft H1 on the main axis 2 , an intermediate gear ZR between the main axis 2 and the minor axis 3 and a transmission element on the first countershaft VW1 on the minor axis 3 educated. The transmission element of the first wheel plane I on the main axis 2 is now connected to the second hollow shaft H2 and connected by means of the first switching element S1 with the second input shaft EW2. The first wheel plane I Thus, by a transmission element on the second hollow shaft H2 on the main axis 2 and a corresponding transmission element on the first countershaft VW1 on the minor axis 3 educated.

3b shows a transmission according to a third embodiment of the present invention.

In 3b is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 is at the transmission 1 according to 3b the first switching device SE1 instead of on the main axis 2 now on the minor axis 3 arranged. The first switching element S1 is now connected on the one hand to the first countershaft VW1, on the other hand with a coaxially and parallel thereto arranged fourth countershaft VW1a. On the outside of the fourth countershaft VW1a a transmission element is arranged, which with a transmission element on the second input shaft EW2 to form the first wheel I interacts. The second switching element S2 is now connected on the one hand to a fifth countershaft VW1b, which is arranged parallel and coaxial with the first countershaft VW1 and on the other hand connected to the first countershaft VW1. When actuated, the second shift element S2 thus establishes a connection between the fifth countershaft VW1b and the first countershaft VW1. On the outside of the fifth countershaft VW1b a transmission element is arranged, which with an intermediate ZR between the minor axis 3 and the main axis 2 and a transmission element on the second input shaft EW2 on the main axis 2 for the formation of the sixth wheel plane VI interacts in the form of the reverse gear.

3c shows a transmission according to a fourth embodiment of the present invention.

In 3c is essentially a transmission 1 according to 1 shown. In contrast to the gearbox 1 according to 1 is at the transmission 1 according to 3c the second switching device SE2 instead of on the main axis 2 on the minor axis 3 arranged. The third switching element S3 is now connected on the one hand to the second countershaft VW2, on the other hand with a fourth to the second countershaft VW2 coaxial and parallel countershaft VW3b. The fourth countershaft VW3b is arranged on the radial outer side of the second countershaft VW2 and has a transmission element, which with a transmission element on the second input shaft EW2 on the main axis 2 to form the second wheel plane II interacts. The third switching element S3 is arranged in the second switching device SE2 and can be actuated by means of the second switching element actuating device SB2.

4 shows a transmission according to a fifth embodiment of the present invention.

In 4 is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 includes the gearbox 1 according to 4 an electric machine EM. The electric machine EM is via a shaft and a transmission element with the transmission element of the second wheel plane II , which is arranged on the second countershaft VW2, for hybridizing the transmission 1 connected. The connection or coupling of the electric machine EM to the transmission 1 can also do this on the third wheel plane III take place, ie in general in particular at the wheel planes or stages, which a transmission element on the minor axis 3 have on the outside of the second countershaft VW2.

Overall, the switching elements S1 to S7 in the transmission 1 according to the 1 to 4 Also referred to as coupling devices and be designed in particular as synchronizers. In this case, the first switching element S1 of the first wheel plane I , the second switching element S2 of the sixth gear plane VI in the form of the reverse gear, the third switching element S3 of the second gear plane II , the fourth switching element S4 of the third wheel plane III , the fifth switching element S5 the input shafts EW1, EW2 and the output shaft AW, the sixth switching element S6 of the fourth gear plane IV and the seventh switching element S7 of the second and third wheel planes II . III be assigned. The fifth wheel plane V at the transmission 1 according to the 1 to 4 is designed as an output constant.

In summary, the present invention provides the advantage of six wheel planes, at least six forward gears and at least two reverse gears by means of at least four switching devices, as well as at least seven switching elements to provide. Likewise, the invention offers the advantage that only four actuators in the form of the switching devices or switching element actuation devices for actuating the seven switching elements must be provided. Another advantage of the present invention is that the transmission has good load shifting capability and good hybridisability. Finally, the invention also offers, inter alia, the advantage that a reduction of the mechanical spread is made possible by winding the first forward gear.

Although the present invention has been described above with reference to preferred embodiments, it is not limited thereto, but modifiable in many ways.

The gear 1 of the 1 to 4 can be transformed functionally identical by different positions of the wheel planes and / or the switching elements. For this purpose, the switching elements, in particular designed as synchronizers, as mentioned above, the wheel planes or the waves are assigned. The switching matrix according to the 2 thus does not change by a rearrangement of the wheel planes and / or the switching elements.

LIST OF REFERENCE NUMBERS

1

transmission

2

main axis

3

minor axis

4

countershaft

I, II, III, IV, V, VI

wheel plane

AW

output shaft

EW1, EW2

input shaft

H1, H2, H3, H4

hollow shaft

K1, K2

clutch

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

switching element

SB1, SB2, SB3, SB4

Switching element actuator

SE1, SE2, SE3, SE4

switching device

VW1, VW2, VW3a, VW1a, VW1b

Countershaft

ZR

idler

AT

drive

FROM

output

EM

electric machine

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 102006054281 A1 [0005]
• DE 102010030569 A1 [0027]

Claims (17)

Transmission ( 1 ), in particular dual-clutch transmission, for a motor vehicle, comprising at least two partial transmissions, wherein each of the partial transmissions comprises at least one input shaft (EW1, EW2), and wherein an output shaft is arranged as the output shaft (AW) of both partial transmissions, wherein the at least one input shaft (EW1, EW2) on a main axis ( 2 ) and the output shaft (AW) on the main axis ( 2 ) or on one, in particular to the main axis ( 2 ) parallel, minor axis ( 3 ) and wherein a countershaft ( 4 ) with at least one countershaft (VW1, VW2, VW3a, VW3b, VW1a, VW1b) is arranged, wherein the at least one countershaft (VW1, VW2, VW3a, VW3b, VW1a, VW1b) on the minor axis ( 3 ) is arranged, and wherein at least one of the input shafts (EW1, EW2) by means of at least two wheel planes ( I . II . III . IV . V . VI ) and / or at least one switching element (S1, S2, S3, S4, S5, S6, S7) to the output shaft (AW) is connectable, characterized in that N switching means (SE1, SE2, SE3, SE4) are arranged, N is a positive integer greater than or equal to two, and wherein at least one of the N switching devices (SE1, SE2, SE3, S4) on the main axis ( 2 ) and on the minor axis ( 3 ) are arranged, and that one of the at least one switching device (SE1, SE2, SE3, SE4) on the minor axis ( 3 ) in the region of the output (AB) of the transmission ( 1 ) is arranged, in particular adjacent to at least one torque downstream wheel plane ( V ), and that by means of a switching device (SE4) on the minor axis ( 3 ) A second countershaft (VW2, VW3a) with the first countershaft (VW1) can be coupled. Transmission according to claim 1, characterized in that the N switching devices (SE1, SE2, SE3, SE4) are symmetrical to one another with respect to their axial position on the main axis ( 2 ) and the minor axis ( 3 ) are arranged. Transmission according to one of claims 1-2, characterized in that the N switching devices (SE1, SE2, SE3, SE4) in the axial direction along the main axis ( 2 ) and minor axis ( 3 ) are arranged alternately. Transmission according to one of claims 1-3, characterized in that at least one wheel plane ( V ) is designed as output constant. Transmission according to one of claims 1-4, characterized in that at least two of the input shafts (EW1, EW2) coaxial with each other and / or the second countershaft (VW2, VW3a, VW3b, VW1a, VW1b) coaxial with the at least one countershaft (VW1) are arranged. Transmission according to one of claims 1-5, characterized in that the number N is equal to four. Transmission according to one of claims 1-6, characterized in that at least one of the input shafts (EW1, EW2) is designed as a hollow shaft and the other input shaft is formed as a solid shaft and / or at least one of the countershafts (VW1, VW2, VW3a, VW3b, VW1a, VW1b) is designed as a hollow shaft and at least one of the other countershafts as a solid shaft. Transmission according to one of claims 1-7, characterized in that at least three, in particular at least four wheel planes ( I . VI . II . III ) are connectable by means of at least one switching element with at least one of the input shafts (EW1, EW2). Transmission according to one of claims 1-8, characterized in that at least one wheel plane ( VI ) is designed as a reverse gear. Transmission according to claim 9, characterized in that the reverse gear ( VI ) is arranged between two adjacent switching devices (SE1, SE2). Transmission according to one of claims 9-10, characterized in that the reverse gear ( VI ) directly adjacent to the side of the drive (AN) in the transmission ( 1 ) is arranged. Transmission according to one of claims 1-11, characterized in that an electric machine (EM) on at least one wheel plane ( I . II . III . IV . V . VI ) and / or on at least one countershaft (VW1, VW2, VW3a, VW3b, VW1a, VW1b) and / or on at least one of the input shafts (EW1, EW2) for hybridizing the transmission ( 1 ) is arranged. Transmission according to claim 12, characterized in that the electric machine (EM) at at least one of the wheel planes ( II . III ), which is connected to a countershaft (VW2) designed as a hollow shaft, is connected. Transmission according to one of claims 1-13, characterized in that transmission elements of at least two wheel planes ( II . III ) on the minor axis ( 3 ) are connected to a formed as a hollow shaft countershaft (VW2), in particular fixed. Transmission according to one of claims 1-14, characterized in that the N switching devices (SE1, SE2, SE3, SE4) and the at least two wheel planes ( I . II . III . IV . V . VI ) are arranged so that at least six forward gears and at least two reverse gears through the transmission ( 1 ) are representable. Transmission according to one of claims 1-15, characterized in that by means of a switching device (SE4) on the minor axis ( 3 ), a countershaft (VW1) with in each case one at least two further countershafts (VW2, VW3a) is connectable. Motor vehicle, in particular a passenger or a truck, with a transmission ( 1 ) according to one of claims 1 to 16.

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