DE102012203061A1 - Transmission i.e. dual clutch transmission, for e.g. passenger car, has jackshafts connectable with each other by one of multiple switching arrangements, and driven shaft and input shafts arranged on wheel planes - Google Patents

Abstract

The transmission (1) has switching arrangements (SE1-SE4) comprising two shift elements (S3, S4) i.e. dual clutches, which are arranged on a minor axis (3), where a number of the switching arrangements is greater than or equal to two. The switching arrangements are arranged on a major axis (2). A driven shaft (AW) and input shafts (EW1, EW2) are arranged on wheel planes (III, IV) with respect to respective axial positions on the major axis and the minor axis. Two of three jackshafts (VW1-VW3) are connectable with each other by one of the switching arrangements. The input shafts and the jackshafts are designed sleeve shafts or solid shafts.

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 wheel planes and / or at least one 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.

An object of the present invention is therefore to provide a transmission for a motor vehicle, which has a good load switching capability and a good hybridisability. 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. Another object of the present invention is 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 is arranged with at least one countershaft, wherein the at least one countershaft is arranged on the minor axis, and wherein at least one of the input shafts is connectable to the output shaft by means of at least two gear planes and / or at least one switching element, in that N switching devices are arranged, where N is an integer greater than or equal to two, in that at least one of the N switching devices, comprising at least two switching elements, is arranged on the minor axis and wherein at least one of the N switching devices is arranged on the main axis, by means of which the output shaft and at least one of the input shafts can be connected, and wherein the at least two gear planes are axial Position on the main axis and on the minor axis between the switching device on the main axis and the switching device are arranged on the minor axis and wherein by means of at least one switching device on the minor axis in each case two of three countershafts are connected to each other.

The invention also solves the problems with a motor vehicle, in particular a passenger or truck with a transmission according to one of claims 1 to 17.

One of the advantages achieved thereby is that in this way a reduction of the mechanical spread by winding the first forward gear of the transmission is made possible. Another advantage is that the transmission has a good load shifting capability and a good hybridisability.

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 this device or 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, the number N is equal to four. Thus, if N = 4 switching devices are arranged, at least a plurality of forward gear ratios and at least a plurality of reverse gear stages can be represented by the transmission, wherein at the same time the transmission can be made compact, so that it can be used in a variety of vehicles.

Advantageously, the number N is an even number and N / 2 switching means are on the main axis and N / 2 switching means are arranged on the minor axis. In this way, the transmission can be made compact, since at least two of the N switching devices can be arranged closer together in terms of their axial distance by respective positioning on different axes.

Conveniently, that switching device which is arranged directly adjacent to the side of the drive or to the side of the output is arranged on the main axis or on the minor axis. An advantage here is that, for example, in the case that those switching devices which are arranged directly to the side of the drive and the output in the transmission are arranged on the minor axis, additional space is provided in the region of the input shafts and the output shaft, since the Next adjacent switching devices are not arranged on the main axis, but on the minor axis. On the one hand, this further increases the flexibility, in particular in the installation of the Gearboxes in different vehicles, on the other hand, the transmission can be made even more compact. Are those switching devices, which are arranged directly to the side of the drive and the output in the transmission, arranged on the main axis, an advantage that the countershaft can be performed correspondingly more compact, in particular in the radial and / or axial direction.

Advantageously, at least two of the input shafts are arranged coaxially with one another and / or at least two of the countershafts are arranged coaxially with one another. This reduces the space for the at least two input shafts and the at least 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.

The switching devices are expediently arranged symmetrically and / or periodically alternately with respect to their position along the main axis and the minor axis between the side of the drive and the side of the output. For example, an arrangement along the major and minor axes from the drive side to the output side is possible as follows: the first switching device is arranged on the minor axis, the second and third switching device are arranged on the main axis and the fourth switching device is in turn arranged on the minor axis. Likewise, the first switching device may be arranged on the minor axis, the second switching device on the main axis, the third switching device in turn on the minor axis and the fourth switching device in turn on the main axis. In this way, the switching devices are at least partially arranged alternately on different axes and can thus be arranged with respect to their axial positions in each case at a shorter distance from each other.

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 input shaft or countershaft formed as a hollow shaft coaxial and can be arranged parallel to the solid shaft formed as input shaft or countershaft. When training as a solid shaft or as a hollow shaft respective transmission elements, if they are to be 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 shaft can thus be omitted.

Conveniently, at least two wheel planes are connectable by means of at least one switching element on the main axis with at least one of the input shafts. 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 by the transmission, without requiring a large number of components 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 at least one reverse gear can be provided for a vehicle, 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 a switching device on the main axis or on the minor axis. If the reverse gear stage can be actuated, for example, with a switching device on the minor axis, further switching devices on the main axis can be arranged closer to the switching device on the minor axis with respect to their axial position, which overall reduces the installation space of the transmission along the main axis and the minor axis. If the shifting device is arranged on the main axle for actuating the reverse gear, larger torques can be transmitted from the input side to the output side of the transmission by means of the reverse gear step.

Advantageously, 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 hybridization of 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 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.

Conveniently, the electric machine is arranged on at least one of the wheel planes, which are connected to a countershaft, designed as a solid shaft. In this way, a particularly simple arrangement or coupling of the electric machine to the transmission and thus a reliable transmission of force and torque from the electric machine to the transmission, in particular ultimately to the output shaft, possible.

Advantageously, at least two wheel planes can be connected to the output shaft by means of at least one switching element. One of the advantages achieved thereby is that on the one hand, the flexibility of the transmission is further increased, since a large number of possible connections or couplings between the shafts of the countershaft by means of at least two wheel planes and the output shaft is made possible. Another advantage is that at the same time a compact construction of the transmission is made possible.

Conveniently, the N switching devices and the at least two wheel planes, in particular six wheel planes, arranged so that at least six forward gears and at least five reverse gears are represented by the transmission. In this way, the transmission can provide a sufficient number of forward gear ratios and reverse gear ratios for a variety of vehicles, particularly for both passenger cars and trucks.

Advantageously, at least two wheel planes can be coupled by means of two switching elements on the minor axis to two countershafts, wherein one of the two countershafts is designed as a solid shaft and the other of the two countershafts as a hollow shaft. In this way, the flexibility of the transmission is further increased, are made possible in the further connections by means of the wheel planes between waves on the main axis and the countershaft on the minor axis without the space of the transmission is substantially increased.

Conveniently, the N / 2 switching means, which are arranged adjacent to the side of the drive, arranged on the minor axis. In this way, the at least one input shaft, for example, connected to load switching elements in the form of clutches easier be arranged because in the region of the side of the drive on the main axis no switching elements are arranged, which need space.

Advantageously, the reverse gear is arranged directly adjacent to the side of the output. An advantage of this is that it allows a direct transmission of power and torque by means of the reverse gear from the countershaft to the output shaft, and thus large torques can be transmitted when operating the switching device for the reverse gear. In addition, by the arrangement of the reverse gear in the region of the side of the output easier accessibility, for example in the case of maintenance, the reverse gear stage possible.

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 features mentioned above and those yet to be explained below can be used not only in the particular combination given, 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 transmission according to a second embodiment of the present invention;

3 a shift matrix for a transmission according to the first and second embodiments of the 1 and the 2 ;

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;

4d a transmission according to a sixth embodiment of the present invention;

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

5b a transmission according to an eighth embodiment of the present invention;

5c a transmission according to a ninth embodiment of the present invention; such as

6 a transmission according to a tenth 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 or connected 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 which, starting from the two clutches K1 and K2, initially has a first wheel plane I and a first shift element S1, downstream of the drive AN, and further comprises a second shift element S2, a second wheel plane II, a third wheel plane III, a fourth wheel 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. Each of the said gear 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.

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 one, arranged in a portion of the first countershaft VW1 and formed as a hollow shaft second countershaft VW2. The counterpart 4 further comprises a third countershaft VW3, which is designed as a hollow shaft. The third countershaft VW3 is arranged coaxially and parallel to the second countershaft VW2. The second countershaft VW2 is arranged coaxially and parallel to the first countershaft VW1 on the radial outer side. On the radial Outside of the second countershaft VW2 is arranged a transmission element for the fourth gear plane IV. On the outside of the third countershaft VW3, a transmission element for the third wheel plane III is arranged. Between the minor axis 3 and the main axis 2 has the sixth gear plane VI, which is in the form of a reverse gear, an intermediate ZR to reverse 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 allows a reverse direction of rotation of the output shaft AW to provide at least one reverse gear becomes. Starting from the side of the drive AN has the minor axis 3 First, the first wheel plane I and on the second gear plane II, a third switching element S3, a fourth switching element S4, the third wheel plane III, the fourth gear plane IV, the sixth gear plane VI and the fifth gear plane V.

The seven switching elements S1, S2, S3, S4, S5, S6 and S7 will now be described below. The first switching element S1 is on the main axis 2 arranged and connected on the one hand to the second input shaft EW2, on the other hand with a first hollow shaft H1 and, when actuated, establishes a connection for transmitting force and torques between the second input shaft EW2 and the first hollow shaft H1. The first hollow shaft H1 is arranged coaxially and parallel to the second input shaft EW2 on the radial outer side. Arranged on the first hollow shaft H1 is a transmission element, which interacts with a transmission element on the first countershaft VW1 to form the first wheel plane I. The second switching element S2 is on the main axis 2 arranged and connected on the one hand to the second input shaft EW2, on the other hand with a second hollow shaft H2 and provides upon actuation a connection for the transmission of force and torque between the second input shaft EW2 and the second hollow shaft H2 ago. The second hollow shaft H2 is arranged coaxially and parallel to the second input shaft EW2 on the radial outer side. On the second hollow shaft H2, a transmission element is arranged which cooperates with a transmission element on the first countershaft VW1 to form the second wheel plane II.

The third switching element S3 is on the minor axis 3 arranged and connected on the one hand with the first countershaft VW1, on the other hand with the second to the first countershaft VW1 coaxial and parallel and as a hollow shaft countershaft VW2 and provides upon actuation a connection for the transmission of force and torque between the first countershaft VW1 and the second countershaft VW2 ago , On the second countershaft VW2 as mentioned above, a transmission element is arranged, which cooperates with a transmission element on the first input shaft EW1 to form the fourth gear plane IV. The fourth switching element S4 is on the minor axis 3 arranged and connected on the one hand to the second input shaft EW2, on the other hand with a third to the second countershaft VW2 coaxial and parallel and formed as a hollow shaft countershaft VW3 and provides upon actuation a connection for the transmission of force and torque between the second countershaft VW2 and the third countershaft VW3 ago , On the third countershaft VW3, a transmission element is arranged, which cooperates with a transmission element on the second input shaft EW2 to form the third wheel planes III.

The fifth switching element S5 is on the main axis 2 arranged and connected on the one hand with the first input shaft EW1, on the other hand with the output shaft AW and, when actuated, establishes a connection for the transmission of force and torques between the first input shaft EW1 and the output shaft AW.

The sixth switching element S6 is on the main axis 2 arranged and connected on the one hand to the output shaft AW, on the other hand with a coaxial to the output shaft AW and parallel and formed as a hollow shaft third hollow shaft H3 and provides upon actuation a connection for the transmission of force and torque between the output shaft AW and the third hollow shaft H3 ago. On the third hollow shaft H3, a transmission element is arranged, which with the intermediate gear ZR between the main axis 2 and minor axis 3 and a transmission element on the first countershaft VW1 to form the sixth gear plane VI cooperates. The seventh switching element S7 is on the main axis 2 arranged and connected on the one hand to the output shaft AW, on the other hand with a coaxial and parallel to the output shaft AW fourth hollow shaft H4 and provides upon actuation a connection for the transmission of force and torque between the output shaft AW and the fourth hollow shaft H4 ago. On the fourth hollow shaft H4, a transmission element is arranged, which cooperates with a transmission element on the first countershaft VW1 to form the fifth gear plane V.

The first switching element S1 and the second switching element S2 on the main axis 2 are combined in a common first switching device SE1 and actuated by means of a common first switching element actuator SB1. The third switching element S3 and the fourth switching element S4 on the minor axis 3 are combined in a common second switching device SE2 and by means of a common second switching element actuation device SB2 can be actuated. The fifth switching element S5 is on the main axis 2 arranged in a third switching device SE3 and actuated by means of a third Schalelementbetätigungseinrichtung SB3. The sixth switching element S6 and the seventh switching element S7 on the main axis 2 are combined in a common fourth switching device SE4 and actuated by means of a common fourth switching element actuator SB4.

The switching element actuators SB1, SB2 and SB4 or the switching devices SE1, SE2 and SE4 can be designed as double synchronizers. The switching element actuating device SB3 or the switching device SE3 can be designed as a single synchronization.

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

Overall, by the embodiments of the 1 through the transmission 1 at least six forward gears and at least five 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 at the transmission 1 according to 2 the sixth switching element S6 on the main axis 2 instead of in the fourth switching device SE4 now arranged in the third switching device SE3. The sixth switching element S6 is further 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, the transmission element is arranged, which with the intermediate gear ZR between the main axis 2 and minor axis 3 and the corresponding transmission element on the first countershaft VW1 to form the sixth gear plane VI in the form of the reverse gear stage cooperates. The fifth switching element S5 and the sixth switching element S6 can now be actuated by means of the common third switching element actuating device SB3. The seventh switching element S7 is furthermore arranged in the fourth switching device SE4 and can be actuated by means of the fourth switching element actuating device SB4.

3 shows a switching matrix for a transmission according to the first and second embodiments of the 1 and the 2 ,

In 3 is a switching matrix for a transmission 1 according to 1 or 2 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 five reverse gear stages, designated R1 to R5. The released in the switching matrix entries, so for example in the forward gear stage 1 in the switching elements S2, S3, S5 and S6, indicate that the corresponding switching element is open, ie that the switching element in this case no forces or no torque from the on the Switching element connected respective waves transmits. An entry in the switching matrix provided with a cross designates a correspondingly actuated or closed switching element, that is, in the switching matrix in the forward gear stage 1 in the switching elements S1, S4 and S7.

To the first gear by means of the transmission 1 according to 1 or 2 represent the clutch K1 are closed and the clutch K2 open and the switching elements S2, S3, S5 and S6 open and the switching elements S1, S4 and S7 closed. To illustrate the second gear, the clutch K1 are open and the clutch K2 closed and the switching elements S2, S3, S4, S5 and S6 open and the switching elements S1 and 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, S5 and S6 open and the switching elements S3 and S7 closed. To illustrate the fourth gear, the clutch K1 are open and the clutch K2 closed and the switching elements S1, S3, S4, S5, S6 open and the switching elements S2 and S7 closed. To illustrate the fifth gear, the clutch K1 are closed and the clutch K2 open and the switching elements S1, S2, S3, S4, S6 and S7 open and the switching element S5 closed. To illustrate the sixth gear, the clutch K1 are opened and the clutch K2 is closed and the switching elements S1, S4, S6 and S7 open and the switching elements S2, S3 and S5 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 S2, S3, S5 and S7 are opened and the shifting elements S1, S4 and S6 are closed. To represent the second reverse gear R2, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S3, S5 and S7 open and the switching elements S2, S4 and S6 closed. In order to represent the third reverse gear R3, the clutch K1 are closed and the clutch K2 is opened and the shifting elements S1, S2, S4, S5 and S7 are opened and the shifting elements S3 and S6 are closed. In order to represent the fourth reverse gear R4, the clutch K1 are opened and the clutch K2 is closed and the shifting elements S1, S3, S4, S5 and S7 are opened and the shifting elements S2 and S6 are closed. In order to represent the fifth reverse gear R5, the clutch K1 are opened and the clutch K2 is closed and the shifting elements S2, S3, S4, S5 and S7 are opened and the shifting elements S1 and S6 are closed.

Thus, by means of the switching matrix according to 3 at least six forward gears and at least five reverse gears by means of the transmission 1 according to the 1 or 2 to provide.

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 two wheel planes I and II with respect to their position along the main axis 2 or the minor axis 3 arranged reversed. The sequence of wheel planes and shift elements on the main axle 2 starting from the side of the drive AN are now as follows: second gear plane II, second switching element S2, first switching element S1, first gear plane I, third gear plane III, fourth gear plane IV, fifth switching element S5, sixth gear plane VI, sixth switching element S6, seventh switching element S7 and fifth gear plane V. The second switching element S2 on the main axis 2 is connected on the one hand to the first hollow shaft H1, on the other hand to the second input shaft EW2 and, when actuated, establishes a connection for transmitting force and torques between the first hollow shaft H1 and the second input shaft EW2. On the first hollow shaft H1, a transmission element is arranged which cooperates with a transmission element on the first countershaft VW1 to form the second wheel plane II. The first switching element S1 is now connected on the one hand to the second input shaft EW2, on the other hand to the second hollow shaft H2 and, when actuated, establishes a connection for transmitting force and torques between the second input shaft EW2 and the second hollow shaft H2. On the second hollow shaft H2, a transmission element is arranged, which cooperates with a transmission element on the first countershaft VW1 to form the first gear plane I. The first switching element S1 and the second switching element S2 are further combined in the first switching device SE1 and actuated by means of the common first switching element actuator SB1.

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 are at the transmission 1 according to 4b the two wheel planes V and VI with respect to their position along the main axis 2 or the minor axis 3 in the transmission 1 arranged reversed. The sequence of wheel planes and shift elements on the main axle 2 is now as follows: first gear plane I, first switching element S1, second switching element S2, second gear plane II, third gear plane III, fourth gear plane IV, fifth switching element S5, fifth gear plane V, seventh switching element S7, sixth switching element S6, sixth gear 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 for transmitting force and torques between the output shaft AW 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 first countershaft VW1 to form the fifth gear plane V. The sixth switching element S6 is on the main axis 2 arranged and now on the one hand to the output shaft AW, on the other hand connected to the fourth hollow shaft H4 and provides upon actuation a connection for the transmission of force and torque between the output shaft AW and the fourth hollow shaft H4 ago. On the fourth hollow shaft H4, a transmission element is arranged, which with an intermediate ZR between the main axis 2 and minor axis 3 and a transmission element on the first countershaft VW1 to form the sixth gear plane VI in the form of the reverse gear stage cooperates.

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 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 fourth countershaft VW4. The fourth countershaft VW4 is arranged parallel and coaxial with the first countershaft VW1 and formed as a hollow shaft. On the fourth countershaft VW4 a transmission element is arranged, which with a transmission element on the second input shaft EW2 on the main axis 2 cooperates to form the first wheel plane I. The second switching element S2 is now connected on the one hand to the first countershaft VW1, on the other hand with a fifth countershaft VW5. The fifth countershaft VW5 is arranged parallel and coaxial with the first countershaft VW1 and designed as a hollow shaft. On the fifth countershaft VW5 a transmission element is arranged, which with a transmission element on the second input shaft EW2 on the main axis 2 cooperates to form the second wheel plane II. The first switching element S1 and the second switching element S2 can also be actuated by means of the first switching element actuating device SB1 and combined in the first switching device SE1. Thus, the sequence of wheel planes and shift elements is on the minor axis 3 starting from the side of the drive AN as follows: first gear plane I, first gear element S1, second gear element S2, second gear plane II, third gear element S3, fourth gear element S4, third gear plane III, fourth gear plane IV, sixth gear plane VI and fifth gear plane V.

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

In 4d is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 is at the transmission 1 according to 4d the fourth switching device SE4 instead of on the main axis 2 now on the minor axis 3 arranged. The sixth switching element S6 is now connected on the one hand to the first countershaft VW1, on the other hand to a fourth countershaft VW4. The fourth countershaft VW4 is arranged parallel and coaxial with the first countershaft VW1 and formed as a hollow shaft. On the fourth countershaft VW4 a transmission element is arranged, which with the intermediate gear ZR between the main axis 2 and minor axis 3 and a transmission element on the output shaft AW to form the sixth gear plane VI in the form of the reverse gear stage cooperates. The seventh switching element S7 is now connected on the one hand to the first countershaft VW1, on the other hand to a fifth countershaft VW5. The fifth countershaft VW5 is arranged parallel and coaxial with the first countershaft VW1 and designed as a hollow shaft. On the fifth countershaft VW5 a transmission element is arranged, which cooperates with a transmission element on the output shaft AW to form the fifth gear plane V. The sixth switching element S6, when actuated, establishes a connection for transmitting power and torques between the first countershaft VW1 and the fourth countershaft VW4. The seventh switching element S7, when actuated, establishes a connection for the transmission of force and torques between the first countershaft VW1 and the fifth countershaft VW5. The sixth switching element S6 and the seventh switching element S7 on the minor axis 3 are further summarized in the fourth switching device SE4 and actuated by means of the fourth switching element actuator SB4.

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

In 5a is essentially a transmission 1 according to 2 shown. Unlike the gearbox 1 according to 2 are at the transmission 1 according to 5a the two wheel planes I and II with respect to their position along the main axis 2 or the minor axis 3 arranged reversed. The sequence of wheel planes and shift elements on the main axle 2 starting from the side of the drive ON are as follows: second gear plane II, second switching element S2, first switching element S1, first gear plane I, third gear plane III, fourth gear plane IV, fifth switching element S5, sixth switching element S6, sixth gear plane VI, seventh switching element S7 and fifth gear plane V. The second switching element S2 on the main axis 2 is connected on the one hand to the first hollow shaft H1, on the other hand to the second input shaft EW2 and, when actuated, establishes a connection for transmitting force and torques between the first hollow shaft H1 and the second input shaft EW2. On the first hollow shaft H1, a transmission element is arranged which cooperates with a transmission element on the first countershaft VW1 to form the second wheel plane II. The first switching element S1 is now connected on the one hand to the second input shaft EW2, on the other hand to the second hollow shaft H2 and, when actuated, establishes a connection for the transmission of force and torque between the second input shaft EW2 and the second hollow shaft H2. On the second hollow shaft H2, a transmission element is arranged, which cooperates with a transmission element on the first countershaft VW1 to form the first gear plane I. The first switching element S1 and the second switching element S2 are further combined in the first switching device SE1 and actuated by means of the common first switching element actuator SB1.

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

In 5b is essentially a transmission 1 according to 2 shown. Unlike the gearbox 1 according to 2 is at the transmission 1 according to 5b the first switching device SE1 instead of on the main axis 2 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 fourth countershaft VW4. The fourth countershaft VW4 is arranged parallel and coaxial with the first countershaft VW1 and formed as a hollow shaft. On the fourth countershaft VW4 a transmission element is arranged, which with a transmission element on the second input shaft EW2 on the main axis 2 cooperates to form the first wheel plane I. The second switching element S2 is now connected on the one hand to the first countershaft VW1, on the other hand with a fifth countershaft VW5. The fifth countershaft VW5 is arranged parallel and coaxial with the first countershaft VW1 and designed as a hollow shaft. On the fifth countershaft VW5 a transmission element is arranged, which with a transmission element on the second input shaft EW2 on the main axis 2 cooperates to form the second wheel plane II. The first switching element S1 and the second switching element S2 can also be actuated by means of the first switching element actuating device SB1 and combined in the first switching device SE1. Thus, the sequence of wheel planes and shift elements is on the minor axis 3 starting from the side of the drive AN as follows: first gear plane I, first gear element S1, second gear element S2, second gear plane II, third gear element S3, fourth gear element S4, third gear plane III, fourth gear plane IV, sixth gear plane VI and fifth gear plane V.

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

In 5c is essentially a transmission 1 according to 2 shown. Unlike the gearbox 1 according to 2 is at the transmission 1 according to 5c the fourth switching device SE4 comprising the seventh switching element S7 instead of the main axis 2 now on the minor axis 3 arranged. The seventh switching element S7 is now connected on the one hand to the first countershaft VW1, on the other hand to a fourth countershaft VW4 and, when actuated, establishes a connection for transmitting force and torques between the first countershaft VW1 and the fourth countershaft VW4. The fourth countershaft VW4 is arranged coaxially and parallel to the first countershaft VW1 and formed as a hollow shaft. On the fourth countershaft VW4 a transmission element is arranged, which cooperates with a transmission element on the output shaft AW to form the fifth gear plane V. The sequence of wheel planes and switching elements on the minor axis 3 is now as follows: first gear plane I, second gear plane II, third switching element S3, fourth switching element S4, third gear plane III, fourth gear plane IV, sixth gear plane VI, seventh switching element S7, fifth gear plane V. The seventh switching element S7 is further in the fourth Switching device arranged SE4 and actuated by means of the fourth switching element actuator SB4.

6 shows a transmission according to a tenth 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 for hybridization of the transmission 1 , The electric machine EM is connected to the transmission element on the minor axis via a shaft and a transmission element connected to the shaft 3 the first wheel plane I connected. In this way, the electric machine EM can transmit power and torques to the transmission element of the first wheel plane I and thus to the first countershaft VW1 and to hybridize the transmission 1 according to 1 provide. The connection or coupling of the electric machine EM to the transmission 1 can also be done on transmission elements of the second wheel plane II, the fifth wheel plane V and the sixth wheel plane VI. So on those transmission elements on the minor axis 3 which are arranged on the first countershaft VW1, which is designed as a solid shaft.

Overall, the switching elements S1 to S7 in the transmission 1 according to the 1 to 6 Also referred to as coupling devices and be designed in particular as synchronizers. The switching devices SE1 to SE4 and the switching element actuators SB1 to SB4 can be designed as double synchronizers in the case of two switching elements and in the case of a switching element as a single synchronization. The transmission elements can in particular in the transmission 1 according to the 1 to 6 both fixed and loose with the respective shaft, in particular with the input shafts EW1, EW2 and / or one of the countershafts VW1, VW2, VW3, VW4 and VW5 and / or with the hollow shafts H1, H2, H3, H4 are arranged or connected. The transmission elements can be designed in particular in the form of gears, preferably as spur gears, so that the wheel planes I, II, III, IV, V and VI represent spur gears. By providing different forward and reverse gears, so different translations, the Spur gear stages, in particular their gears, correspondingly comprise different translations.

Furthermore, the first gear plane I and the second gear plane II can be coupled to one of the input shafts EW1, EW2 by means of at least one switching element. The first input shaft EW1, which is designed as a solid shaft, can be coupled to the output shaft AW by means of the fifth switching element S5. The fifth gear plane V and the sixth gear plane VI can be connected or coupled to the output shaft AW by means of at least one switching element. The transmission element of the third wheel plane III on the minor axis 3 is coupled by means of at least one switching element to the second countershaft VW2, wherein the transmission element of the third gear plane III with the second countershaft VW2 coaxially mounted or arranged third countershaft VW3 is firmly connected. The first countershaft VW1 coaxial and parallel and designed as a hollow shaft second countershaft VW2 can be coupled by means of the third switching element S3 to the first countershaft VW1.

Overall, the switching elements S1 to S7 in the transmission 1 according to the 1 to 6 Also referred to as coupling devices and as already explained above, in particular be designed as synchronizers. Here, the first switching element S1 of the first gear plane I, the second switching element S2 of the second gear plane II, the third switching element S3 of the fourth gear plane IV, the fourth switching element S4 of the third gear plane III, the fifth switching element S5 the two input shafts EW1, EW2 and the Output shaft AW, the sixth switching element S6 of the sixth gear plane VI in the form of the reverse gear and the seventh switching element S7 of the fifth gear plane V are assigned.

In summary, the present invention has the advantage that a reduction of the mechanical spread by winding the first forward gear is made possible. Another advantage is that the transmission has a good load shifting capability and a good hybridisability. A further advantage is that at a total of six wheel planes I to VI at least six forward gears and at least five reverse gears are provided with only seven switching elements and / or only four actuators in the form of switching devices SE1 to SE4 for actuating the seven switching elements.

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 according to the 1 to 6 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 3 thus does not change by a rearrangement of the wheel planes and / or the switching elements and / or the switching devices.

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, VW4, VW5

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 (18)

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 ) is arranged with at least one countershaft (VW1, VW2, VW3, VW4, VW5), wherein the at least one countershaft (VW1, VW2, VW3, VW4, VW5) on the minor axis ( 3 ), 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) is connectable to the output shaft (AW), characterized in that N switching devices (SE1, SE2, SE3, SE4) are arranged, where N is an integer greater than or equal to two, that at least one (SE2) of the N switching devices (SE1, SE2, SE3, SE4), comprising at least two switching elements (S3, S4), on the minor axis ( 3 ) and that at least one of the N switching devices (SE3) on the main axis ( 2 is arranged, by means of which the output shaft (AW) and at least one of the input shafts (EW1, EW2) is connectable and that the at least two wheel planes (III, IV) with respect to their axial position on the main axis ( 2 ) and on the minor axis ( 3 ) between the switching device (SE3) on the main axis ( 2 ) and the switching device (SE2) on the minor axis ( 3 ) and wherein by means of the at least one switching device (SE2) on the minor axis ( 3 ) are each two of three countershafts (VW1, VW2, VW3) connected to each other. Transmission according to claim 1, characterized in that the number N is equal to four. Transmission according to one of claims 1-2, characterized in that N is an even number and N / 2 switching means (SE1, SE2) on the main axis ( 2 ) and N / 2 switching devices (SE3, SE4) on the minor axis ( 3 ) are arranged. Transmission according to one of claims 1-3, characterized in that the one switching device (SE1, SE4), which is arranged directly adjacent to the side of the drive (AN) or to the side of the output (AB), on the main axis ( 2 ) or on the minor axis ( 3 ) is arranged. 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 at least two of the countershafts (VW1, VW2, VW2, VW3) are arranged coaxially with each other. Transmission according to one of claims 1-5, characterized in that the N switching means (SE1, SE2, SE3, SE4) symmetrically and / or periodically alternately with respect to their position along the main axis ( 2 ) and minor axis ( 3 ) are arranged between the side of the drive (AN) and the side of the output (AB). Transmission according to one of claims 1-6, characterized in that at least one of the input shafts (EW1, EW2) and / or at least one of the countershafts (VW1, VW2, VW3, VW4, VW5) formed as a hollow shaft and the respective other shaft as a solid shaft is. Transmission according to one of claims 1-7, characterized in that at least two wheel planes (I, II) by means of at least one switching element (S1, S2) on the main axis ( 2 ) are connectable to 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) by means of a switching device (SE4) on the main axis ( 2 ) or on the minor axis ( 3 ) is operable. Transmission according to one of claims 1-10, 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, VW4, VW5) and / or on one of the input shafts (EW1, EW2) for hybridizing the transmission ( 1 ) is arranged. Transmission according to claim 11, characterized in that the electric machine (EM) is arranged on at least one of the wheel planes (I, II, V, VI), which are connected to a countershaft (VW1), designed as a solid shaft. Transmission according to one of claims 1-12, characterized in that at least two wheel planes (V, VI) by means of at least one switching element (S6, S7) to the output shaft (AW) are connectable. Transmission according to one of claims 1-13, characterized in that the N switching devices (SE1, SE2, SE3, SE4) and the at least two wheel planes (I, II, III, IV, V, VI), in particular six wheel planes (I, II, III, IV, V, VI), are arranged so that at least six forward gears and at least five reverse gears through the transmission ( 1 ) are representable. Transmission according to one of claims 1-14, characterized in that at least two wheel planes (III, IV) by means of two switching elements (S3, S4) on the minor axis ( 3 ) can be coupled to two countershafts (VW1, VW2), wherein one of the two countershafts (VW1) as a solid shaft and the other of the two countershafts (VW2) is designed as a hollow shaft. Transmission according to one of claims 3-15, characterized in that the N / 2 switching devices (SE1, SE2), which are arranged adjacent to the side of the drive (AN), on the minor axis ( 3 ) are arranged. Transmission according to one of claims 9-16, characterized in that the reverse gear (VI) is arranged directly adjacent to the side of the output (AB). Motor vehicle, in particular a passenger or a truck, with a transmission ( 1 ) according to any one of claims 1-17.

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