DE102012202494A1 - Transmission i.e. dual clutch transmission, for e.g. passenger car, has switching element arranged on main axis, switching device arranged on auxiliary axis adjacent to drive, and input shaft connected with countershafts by switching device - Google Patents

Abstract

The transmission (1) has countershafts (VW1-VW3) e.g. hollow shafts, arranged on an auxiliary axis (3). One of input shafts (EW1, EW2) e.g. solid shafts, of a sub transmission is connected with an output shaft (AW) by wheel planes (I-VI) e.g. reverse gear stages, and/or switching elements (S1-S7). One of the two switching elements (S2, S3) is arranged on a main axis (2). A switching device (SE1) is arranged on the auxiliary axis adjacent to a drive (AN). One of the input shafts is connected with the countershafts by the switching device.

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 ash and the output shaft is arranged on the main axis or on a, in particular to the main axis parallel, minor axis, and wherein a countershaft is arranged with at least one countershaft, and wherein 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 one switching element with the output shaft is connectable.

The invention also relates to a motor vehicle with a transmission. 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 a transmission for a motor vehicle which enables flexible power sharing and has improved power switching capability and hybridization capability. It is also an object of the present invention to provide a transmission for a motor vehicle, which is simpler and less expensive 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 a 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 Hauptasche and the output shaft is arranged on the main axis or on a, in particular to the main axis parallel minor axis, and wherein a countershaft is arranged with at least one countershaft, and wherein 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 wheel 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 an integer greater than or equal to two, and that at least a second countershaft is arranged, and that at least one of the N switching means on the main axis and at least one of the N switching devices is arranged on the minor axis and wherein one of the input shafts is connectable by means of at least one of the arranged on the minor axis switching means with the at least two countershafts, and wherein at least one of the switching devices arranged on the minor axis adjacent to the drive is.

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

One of the advantages achieved thereby is that, in particular, by the arrangement of at least one switching device on the minor axis, the number of switching devices on the main axis is reduced and so the transmission can be made more compact in terms of its axial extent along the major and minor axis. In addition, a reduction of the mechanical spread by winding the first forward gear of the transmission is possible in this way. Finally, the transmission also offers improved load shifting capability and good hybridization capability.

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.

Conveniently, a switching means is arranged on the minor axis adjacent to the output. One of the advantages achieved thereby is that at least two switching devices are arranged on the minor axis, which further reduces the number of switching devices on the main axis. The axial extent of the transmission along the main and minor axis can thus be further reduced.

Advantageously, at least two of the input shafts are arranged coaxially with one another and / or at least 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, several countershafts can thereby be provided, which allows a representation of a plurality of gears or 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 gear stages can be represented by the transmission, wherein at the same time the transmission can be made compact and can be used in a variety of different vehicles.

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

Conveniently, at least three wheel planes by means of at least one switching element, in particular arranged on the main axis, connectable to the output shaft. Thus, the number of gears or grades that can be represented by the transmission, be further increased without the space for the transmission must be significantly increased and without high costs.

Advantageously, at least one wheel plane is designed as a reverse gear. By means of the at least one reverse gear, a reversal of the direction of rotation of the output shaft with respect to one of the input shafts is possible, so that at least one 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 stage is actuated by means of at least one of the N switching devices, wherein the at least one switching device is arranged furthest downstream in the transmission in the region of the output. One advantage is that the reverse gear is easier to access from the output side, for example for maintenance purposes. On the other hand, an extremely reliable transmission of force and torques from one of the input shafts to the output shaft can thereby be provided, in particular in conjunction with a gear plane designed as a drive constant.

Advantageously, the reverse gear is arranged between two switching devices on the main and / or minor axis. Thus, multiple reverse gears can be easily represented by the transmission, without the space for the transmission must be significantly increased.

Conveniently, an electric machine is arranged on at least one wheel plane and / or on at least one countershaft and / or on 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 so that a so-called stand-charge capability 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 the combustion engine is also on the planetary gear to the coupled 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 the wheel planes, which are connected to a countershaft, designed as a hollow shaft. In this way, a particularly simple connection or coupling of the electric machine to the transmission and thus a reliable transmission of force and torque from the electric machine, in particular ultimately to the output shaft possible.

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. One of the advantages achieved thereby is that the transmission elements can be produced inexpensively together with the countershaft, in particular by a one-piece design of transmission elements together with the countershaft, designed as a hollow shaft. In addition, a connection or coupling of an electrical machine to the transmission respectively to the corresponding transmission elements is extremely reliable 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 three reverse gears are represented by the transmission. One of the advantages achieved with this is that a sufficient number of forward gear ratios and reverse gear ratios can be made available for a large number of vehicles, in particular for both passenger cars and lorries.

Conveniently, at least one wheel plane is designed as a drive contant. For a particularly reliable power and torque transmission from the drive via at least one of the input shafts on the output shaft and / or on at least one of the countershafts is possible.

Advantageously, one of the input shaft, in particular the input shaft designed as a solid shaft, can be connected to the output shaft by means of a switching device. This allows a direct connection of one of the input shafts with the output shaft and thus a direct and thus particularly reliable transmission of power and torque from the one input shaft to the output shaft.

Advantageously, the N switching devices are arranged alternately in the axial direction along the main axis and the minor axis. One of the advantages achieved with this is that it allows an even more compact design with regard to the axial extent of the transmission along the main axis and the minor axis. Since the switching devices are each arranged alternately on different axes in each case along the respective axis, they can be arranged with respect to their axial position in each case at a shorter distance from each other. If you move along an axis parallel to the main and minor axis from the drive side to the output side, so for example, a switching device on the Hauptaschse, then one on the minor axis, then again one on the main axis, etc. arranged.

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

Preferred embodiments and embodiments of the invention are illustrated in the drawings and will be explained in more detail in the following description, wherein the same Reference to reference 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 transmission according to a second embodiment of the present invention;

3a . 3b Shift matrices for a transmission according to the first and second embodiments;

4a a transmission according to a third embodiment of the present invention;

4b a transmission according to a fourth embodiment of the present invention;

4c a transmission according to a fifth embodiment of the present invention;

5a a transmission according to a sixth embodiment of the present invention;

5b a transmission according to a seventh embodiment of the present invention; such as

6 a transmission according to an eighth 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, the side of the drive AN can be coupled to the side of the output AB for the transmission of force and torques. 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 coaxially and parallel to 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 second wheel plane II , a third wheel plane III , a third switching element S3, a fourth switching element S4, a fourth gear plane IV , a fifth switching element S5, a sixth gear plane VI , a sixth switching element S6, a seventh switching element S7, and a fifth gear plane V having. Each of the mentioned wheel planes I . II . III . IV . V and VI has transmission elements, in particular in the form of gears, which, each with a shaft of the transmission 1 are connected. The fourth, fifth and sixth wheel levels IV . V . VI are connectable to an output shaft AW of the drive AB by means of a respective switching element, comprising the fifth, sixth and seventh switching element S5, S6, S7.

Parallel to the main axis 2 is a 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 parallel and coaxial thereto, arranged in a portion of the first countershaft VW1 and formed as a hollow shaft second countershaft VW2. On the first countershaft VW1, which is substantially completely along the input shafts EW1, EW2 and the output shaft AW parallel to the main axis 2 on the minor axis 3 extends are transmission elements for the wheel planes I . V and VI for transmitting force and torques between the main axis 2 and the minor axis 3 arranged. The second to the first countershaft VW1 coaxial countershaft VW2 includes transmission elements for the wheel planes III and IV , Between the minor axis 3 and the main axis 2 indicates the sixth wheel plane VI in the form of the reverse gear, an 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 is provided to provide at least one reverse gear.

On the minor axis 3 is between the transmission elements for the first and second wheel plane I . II a first switching element S1 and a second switching element S2 arranged.

The switching elements S1, S2, S3, S4, S5, S6 and S7 will now be described below. When actuated, the first shifting element S1 produces a transmission of force and torques between the first countershaft VW1 and the second countershaft VW2. The second switching element S2, when actuated, establishes a connection for transmitting force and torques between the second countershaft VW2 and a third countershaft VW3 designed as a hollow shaft and arranged coaxially with the second countershaft VW2. On the third countershaft VW3, a transmission element is arranged, which with a transmission element on the second input shaft EW2 to form the second gear plane II interacts. The first wheel plane I is transmitted through a transmission element on the first countershaft VW1 and a cooperating with this transmission element on the second input shaft EW2 on the main axis 2 educated.

The third switching element S3, when actuated, transmits force and torques between the first input shaft EW1 and a first hollow shaft H1 arranged coaxially and parallel thereto and designed as a hollow shaft. On the first hollow shaft H1, a transmission element is arranged, which with a transmission element on the second countershaft VW2 to form the third gear plane III interacts. The fourth switching element S4, when actuated, establishes a connection between the first input shaft EW1 and the output shaft AW for transmitting power and torques. The fifth switching element S5 is connected on the one hand to the output shaft AW, on the other hand to a second hollow shaft H2 and, when actuated, establishes a connection for transmitting force and torques between the two shafts AW, H2. The second hollow shaft H2 is arranged coaxially and parallel to the output shaft AW. On the second hollow shaft H2, a transmission element is arranged, which with a transmission element on the minor axis 3 to form the fourth wheel plane IV interacts. The sixth switching element S6 is connected to the output shaft AW on the one hand, on the other hand with a third hollow shaft H3, which is arranged coaxially and parallel to the output shaft AW.

When actuated, the sixth shifting element S6 therefore establishes a connection for transmitting force and torques between the third hollow shaft H3 and the output shaft AW. On the third hollow shaft H3 a transmission element is arranged, which with an intermediate ZR and a transmission element on the first countershaft VW1 on the minor axis 3 for the formation of the sixth wheel plane VI interacts in the form of the reverse gear. The seventh switching element S7 is connected on the one hand to the output shaft AW, on the other hand to a fourth hollow shaft H4 and, when actuated, establishes a connection for transmitting force and torques between the fourth hollow shaft H4 and the output shaft AW. The fourth hollow shaft H4 is arranged coaxially and parallel to the output shaft AW and has a transmission element, which with a transmission element on the first countershaft VW1 on the minor axis 3 to form the fifth wheel stage V interacts.

The switching element S1 and S2 are combined in a common first switching device SE1 and actuated by means of a common first switching element actuator SB1. The same also applies to the third switching element S3 and the fourth switching element S4, which are combined in a common second switching device SE2 and actuated by means of a common second switching element confirmation SB2. The fifth switching element S5 is arranged in a third switching device SE3 and actuated by means of a third switching element actuation device SB3. 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 fourth switching element actuation device SB4.

The switching element actuators SB1, SB2 and SB4 may be implemented as double synchronizers, the third switching element actuation device SB3 as a single synchronization.

The transmission elements can be either fixed or loose with the respective shaft, in particular with the input shafts EW1, EW2 and / or at least one of the countershafts VW1, VW2 and / or with the hollow shafts H1, H2, H3 and H4 arranged or connected. The transmission elements can be designed in particular 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, one formed as a solid shaft and the other coaxial with 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 three countershafts VW1, VW2, VW3, one formed as a solid shaft and the other two each coaxial with this and designed as hollow shafts. Here, the third countershaft VW3 is arranged on the radial outer side of the second countershaft VW2, the latter in turn being arranged on the radial outer side of the first countershaft VW1. Furthermore, the output shaft AW is formed as a solid shaft and coaxial with the main axis 2 arranged. 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 and VI each two transmission elements, in particular in the form of gears are arranged. The sixth wheel plane VI In the form of the reverse gear stage, this includes an additional transmission element in the form of an intermediate gear ZR for reversing the direction of rotation. Overall, 13 transmission elements, in particular in the form of gears, are thus arranged.

The transmission elements of the first wheel plane I On the one hand with the second input shaft EW2, on the other hand firmly connected to the first countershaft VW1. The first wheel plane I is thus designed as a drive constant. The transmission elements of the third and fourth wheel plane III and IV on the second countershaft VW2 are firmly connected to this.

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

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

In 2 is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 is now the sixth switching element S6 and connected to the sixth switching element S6 third hollow shaft H3 summarized with the fifth switching element S5 in the third switching device SE3 and actuated by means of the common third switching element actuator SB3. The fourth switching device SE4 now comprises only the seventh switching element S7, which on the other hand can be connected to the fourth hollow shaft H4 on the one hand and to the output shaft AW on the other hand. The fourth switching element actuator SB4 thus serves to actuate the seventh switching element S7. Overall, this is the sequence of switching elements and wheel planes from the fourth gear plane IV along the main axis 2 as follows: Fourth wheel plane IV , fifth switching element S5, sixth switching element S6, sixth gear plane VI , seventh switching element S7, fifth wheel plane V ,

The 3a . 3b show switching matrices for a transmission according to the first and second embodiments.

In the 3a . 3b are each a switching matrix for a transmission 1 according to the 1 and 2 shown. Both in the 3a . 3b Switching matrices shown are thus on the transmission 1 according to the 1 and 2 applicable. Horizontal columns are shown for each clutch K1 and K2 and for the seven switching elements S1 to S7. Perpendicular to this down are first the six forward gear stages, designated by the numbers 1 to 6, and three reverse gear stages, designated by the reference symbols R1, R2 and R3. The released in the respective switching matrix entries, so for example in the forward gear 1 , in the clutch K2 and the switching elements S1, S4 and S6 in 3a indicate that the corresponding clutch or the corresponding switching element is open, that is, the clutch or the switching element in this case transmit no forces or no torque from the respective shafts connected to the clutches or to the switching element. An entry in the switching matrix provided with a cross designates a corresponding closed coupling or a correspondingly closed switching element, that is to say in accordance with the switching matrix 3a at the forward gear stage 1 in the switching elements S2, S3 and S7 and the clutch K1. In the closed state, the switching element or the coupling transmits forces or torques from the respective shafts connected to the coupling or to the corresponding switching element.

To the first gear by means of the transmission 1 according to one of 1 and 2 represent the clutch K1 are closed and the clutch K2 open and the switching elements S1, S4, S5 and S6 open and the switching elements S2, S3 and S7 closed. To represent the second gear, the clutch K1 are opened and the clutch K2 closed and the switching elements S1, S2, S3, S4, S5, S6 open and the switching element S7 closed. To represent the third gear, the clutch K1 are closed and the clutch 2 opened and the switching elements S1, S2, S4, S6, S7 open and the switching elements S3 and S5 closed. To represent the fourth gear, the clutch K1 are opened and the clutch K2 closed and the switching elements S2, S3, S4, S6, S7 open and the switching elements S1 and S5 closed. To illustrate the fifth gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S5, S6, S7 open and the switching element S4 closed. To illustrate the sixth gear, the clutch K1 are opened and the clutch K2 closed and the switching elements S1, S3, S4, S6, S7 open and the switching elements S2 and S5 closed. To represent the first reverse gear R1, the clutch K1 are closed and the clutch K2 is opened and the shifting elements S1, S4, S5, S7 are opened and the shifting elements S2, S3, S6 are closed. To represent the second reverse gear R2, the clutch K1 are closed and the clutch K2 is opened and the shifting elements S2, S4, S5 and S7 are opened and the shifting elements S1, S3 and S6 are closed. To represent the third reverse gear R3, the clutch K1 are opened and the clutch K2 is closed and the shifting elements S1, S2, S3, S4, S5, S7 are opened and the shifting element S6 is closed.

In total, six forward gears and three reverse gears can be achieved in this way by means of the embodiments of FIGS 1 or 2 of the transmission 1 being represented.

3b shows a further switching matrix for a transmission 1 according to one of 1 or 2 , To the first gear by means of the transmission 1 according to 3b represent the clutch K1 are closed and the clutch K2 open and the switching elements S1, S4, S5, S6 open and the switching elements S2, S3 and S7 closed. To represent the second gear, the clutch K1 are opened and the clutch K2 closed and the switching elements S1, S2, S3, S4, S5, S6 open and the switching element S7 closed. To represent the third gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S4, S6, S7 open and the switching elements S3 and S5 closed. To illustrate the fourth gear, the clutch K1 are opened and the clutch K2 closed and the switching elements S1, S3, S4, S6, S7 open and the switching elements S2 and S5 closed. To illustrate the fifth gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S5, S6, S7 open and the switching element S4 closed. To represent the sixth gear, the clutch K1 are opened and the clutch K2 closed and the switching elements S2, S3, S4, S6, S7 open and the switching elements S1 and S5 closed. To represent the first reverse gear R1, the clutch K1 are closed and the clutch K2 is opened and the shifting elements S1, S4, S5, S7 are opened and the shifting elements S2, S3 and S6 are closed. To represent the second reverse gear R2, the clutch K1 is closed and the clutch K2 is opened and the shifting elements S2, S4, S5, S7 are opened and the shifting elements S1, S3 and S6 are closed. To represent the third reverse gear R3, the clutch K1 are opened and the clutch K2 is closed and the shifting elements S1, S2, S3, S4, S5, S7 are opened and the shifting element S6 is closed.

Also in this way are six forward gears and three reverse gears by means of the transmission 1 according to one of 1 and 2 represented.

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

In 4a is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 are at the transmission 1 according to 4a the fifth and sixth wheel plane V . VI in terms of their position along the main axis 2 or minor axis 3 arranged reversed. The same applies to the sixth switching element S6 and the seventh switching element S7. The positions of wheel planes and switching elements are now in a subsection of the main axis 2 starting from the fifth switching element S5 as follows: fifth switching element S5, fifth gear plane V , seventh switching element S7, sixth switching element S6, sixth wheel plane VI , The seventh switching element S7 is now connected on the one hand to the output shaft AW, on the other hand to the third hollow shaft H3 and, when actuated, establishes a connection between the third hollow shaft H3 and the output shaft AW. On the third hollow shaft H3, a transmission element is arranged, which with a arranged on the first countershaft VW1 transmission element for forming the fifth gear plane V interacts. The sixth switching element S6 is now connected on the one hand to the output shaft AW, on the other hand to the fourth hollow shaft H4 and, when actuated, establishes a connection for transmitting force and torques between the output shaft AW and the fourth hollow shaft H4. On the fourth hollow shaft H4, a transmission element is arranged, which with an intermediate ZR and a transmission element on the first countershaft VW1 to form the sixth gear plane VI interacts in the form of the reverse gear.

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

In 4b is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 is at the transmission 1 according to 4b the fourth switching device SE4 instead of on the main axis 2 on the minor axis 3 arranged. The fourth switching device SE4 comprises as in the transmission 1 according to 1 the sixth switching element S6 and the seventh switching element S7. However, the sixth shift element S6 is now connected to the first countershaft VW1 on the one hand, on the other hand with a fourth countershaft VW3a, which is designed as a hollow shaft and is arranged parallel and coaxial with the first countershaft VW1. Upon actuation of the sixth shifting element S6, this establishes a connection for transmission of force and torques between the first countershaft VW1 and the fourth countershaft VW3a. On the fourth countershaft VW3a a transmission element is arranged, which with the intermediate gear ZR and a transmission element on the output shaft AW to form the sixth gear plane VI cooperates in the form of the reverse gear. The seventh switching element S7 is connected on the one hand to the first countershaft VW1, on the other hand to a fifth countershaft VW3b. The fifth countershaft VW3b is formed as a hollow shaft and arranged coaxially and parallel to the first countershaft VW1. When actuated, the seventh switching element S7 establishes a connection for transmission of force and torques between the first countershaft VW1 and the fifth countershaft VW3b. On the fifth countershaft VW3b a transmission element is arranged, which with a transmission element on the output shaft AW to form the fifth wheel V interacts.

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

In 4c is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 is at the transmission 1 according to 4c the third switching device SE3 instead of on the main axis 2 on the minor axis 3 arranged. The third switching device SE3 comprises as in the transmission 1 according to 1 the fifth switching element S5. However, the fifth switching element S5 is now connected to the second countershaft VW2 on the one hand, on the other hand with a fourth countershaft VW3a, which is designed as a hollow shaft and is arranged parallel and coaxial with the second countershaft VW2. Upon actuation of the fifth shift element S5, this establishes a connection for transmission of force and torques between the second countershaft VW2 and the fourth countershaft VW3a. On the fourth countershaft VW3a a transmission element is arranged, which with a transmission element on the output shaft AW to form the fourth gear plane IV interacts.

5a shows a transmission according to a sixth embodiment of the present invention.

In 5a is essentially a transmission 1 according to 2 shown. Analogous to 4a respectively. 1 are the fifth and sixth wheel plane V . VI in terms of their position along the main axis 2 arranged reversed. The arrangement of switching elements and wheel planes in a subsection of the main axis 2 starting from the fifth switching element S5 is now as follows: fifth switching element S5, seventh switching element S7, fifth gear plane V , sixth switching element S6, sixth wheel plane VI , The seventh switching element S7 is now combined with the fifth switching element S5 in the third switching device SE3 and actuated by means of the third switching element actuation device SB3. The seventh switching element S7 is now connected on the one hand to the output shaft AW, on the other hand to the third hollow shaft H3. On the third hollow shaft H3, a transmission element is arranged, which with a transmission element on the first countershaft VW1 on the minor axis 3 to form the fifth wheel plane V interacts. The sixth switching element S6 is now arranged in the fourth switching device SE4 and actuated by means of the fourth switching element actuating device SB4. The sixth switching element S6 is now connected on the one hand to the output shaft AW, on the other hand to the fourth hollow shaft H4 and, when actuated, establishes a connection for transmitting force and torques between the output shaft AW and the fourth hollow shaft H4. On the fourth hollow shaft H4, a transmission element is arranged, which with the intermediate gear ZR and a transmission element on the first countershaft VW1 to form the sixth gear plane VI interacts.

5b shows a transmission according to a seventh embodiment of the present invention.

In 5b is essentially a transmission 1 according to 2 shown. Unlike the gearbox 1 according to 2 and analogous to 4b respectively. 1 is now the fourth switching device SE4 instead of on the main axis 2 on the minor axis 3 arranged. The seventh switching element S7 of the fourth switching device SE4 is thus connected on the one hand to the first countershaft VW1, on the other hand to a fourth countershaft VW3a designed as a hollow shaft. The fourth countershaft VW3a is arranged coaxially and parallel to the first countershaft VW1. The seventh switching element S7 thus establishes, when actuated, a connection for the transmission of forces and torques between the first countershaft VW1 and the fourth countershaft VW3a. On the fourth countershaft VW3a a transmission element is arranged, which with a transmission element on the output shaft AW to form the fifth wheel V interacts.

6 a transmission according to an eighth embodiment of the present invention.

In 6 is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 includes the gearbox 1 according to 6 an electric machine EM. The electric machine EM is connected via a shaft to a transmission element which is connected to a transmission element of the third wheel plane III on the second countershaft VW2 cooperates to transmit power and torque. The connection of the electric machine EM to the gearbox 1 according to 6 can also do so at the fourth wheel plane IV for hybridization of the transmission 1 take place, ie 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, which is preferably fixedly connected thereto.

Overall, the switching elements S1 to S7 in the transmission 1 according to the 1 to 6 Also coupling devices are referred to, in particular be designed as synchronizers. In this case, the first switching element S1 of the third and fourth gear plane is assigned, the second switching element S2 of the second gear plane II , the third switching element S3 of the third wheel plane III , the fourth switching element of the first and second input shaft EW1, EW2 and the output shaft AW, the fifth switching element S5 of the fourth gear plane IV , the sixth switching element of the sixth wheel plane VI in the form of the reverse gear stage and the seventh switching element S7 of the fifth gear plane V , The first wheel plane I is at the transmission 1 according to the 1 to 6 designed as a drive constant.

In summary, the present invention has the advantage that only four actuators in the form of the switching element actuation devices or the switching 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. Likewise, the invention offers the advantage of reducing the mechanical spread by winding the first forward gear of the transmission. Finally, the present invention also offers the advantage of a flexible and cost-effective transmission at least six forward gears and three reverse gears and at the same time only six wheel planes.

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 and the gearbox 1 according to 2 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 formed as synchronizers, as mentioned above, the wheel planes or waves are assigned. The switching matrices according to the 3a and 3b Thus, do not change by rearranging the wheel planes or the switching elements in the transmission.

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, VW3, VW3a, VW3b

 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 [0026]

Claims (17)

Transmission, 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 ) is arranged with at least one countershaft (VW1, VW2, VW3, VW3a, VW3b), wherein the at least one countershaft (VW1, VW2, VW3, VW3a, VW3b) 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 an integer greater than or equal to two, and that at least one second countershaft (VW2, VW3, VW3a, VW3b) is arranged, and that at least one of the N switching means (S2, S3) on the main axis ( 2 ) and at least one of the N switching devices (SE1) on the minor axis ( 3 ) and wherein one of the input shafts (EW1, EW2) by means of at least one of the on the minor axis ( 3 ) arranged switching means (SE1) with the at least two countershafts (VW1, VW2, VW3) is connectable and wherein at least one of the switching means (SE1) on the minor axis ( 3 ) is arranged adjacent to the drive (AN). Transmission according to claim 1, characterized in that one of the switching devices (SE4) on the minor axis ( 3 ) is arranged adjacent to the output (AB). Transmission according to one of claims 1-2, characterized in that at least two of the input shafts (EW1, EW2) coaxial with each other and / or at least the second countershaft (VW1, VW2, VW3, VW3a, VW3b) coaxial with the at least one countershaft (VW1 ) are arranged. Transmission according to one of claims 1-3, characterized in that the number N is equal to four. Transmission according to one of claims 1-4, characterized in that at least one of the input shafts (EW1, EW2) and / or at least one of the countershafts (VW1, VW2, VW3, VW3a, VW3b) designed as a hollow shaft and the respective other shaft as a solid shaft is. Transmission according to one of claims 1-5, characterized in that at least three wheel planes by means of ( IV . V . VI ) at least one switching element (S5, S6, S7), in particular arranged on the main axis ( 2 ), with the output shaft (AW) are connectable. Transmission according to one of claims 1-6, characterized in that at least one wheel plane ( VI ) is designed as a reverse gear. Transmission according to Claim 7, characterized in that the reverse gear stage can be actuated by means of at least one of the N shifting devices (SE4), the at least one shifting device (SE4) being furthest down the torque in the transmission ( 1 ) is arranged in the region of the output (AB). Transmission according to one of claims 7-8, characterized in that the reverse gear ( VI ) between two switching devices (SE3, SE4) on the main ( 2 ) and / or minor axis ( 3 ) is arranged. Transmission according to one of claims 1-9, 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, VW3, VW3a, VW3b) and / or on one of the input shafts (EW1, EW2) for hybridizing the transmission ( 1 ) is arranged. Transmission according to claim 10, characterized in that the electric machine (EM) at the wheel planes ( II . III . IV ), which are connected to a countershaft (VW2, VW3), designed as a hollow shaft. Transmission according to one of claims 1-11, characterized in that transmission elements of at least two wheel planes ( II . III . IV ) on the minor axis ( 3 ) are connected to a countershaft (VW2, VW3) designed as a hollow shaft, in particular fixed. Transmission according to one of claims 1-12, 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 three reverse gears through the transmission ( 1 ) are representable. Transmission according to one of claims 1-13, characterized in that at least one wheel plane ( I ) is designed as a drive constant. Transmission according to one of claims 1-14, characterized in that one of the input shafts (EW1, EW2), in particular as Solid shaft formed input shaft (EW1), by means of a switching device (SE2) with the output shaft (AW) is connectable. Transmission according to one of claims 1-15, 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. Motor vehicle, in particular a passenger or a truck, with a transmission ( 1 ) according to any one of claims 1-16.

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