DE102012202492A1 - Gear box for e.g. truck, has reduction gear having jackshafts arranged along minor axis, while input shafts, driven shafts and switching arrangements are arranged along major axis - Google Patents

Abstract

The gear box (1) has two partial gear boxes each of which comprises input shafts (EW1,EW2), and driven shaft (AW) that are arranged along a major axis (2). A reduction gear (4) is provided with jackshafts (VW1,VW2) that are arranged along the minor axis (3). The input shafts are connected to driven shafts via wheel planes (I-VII) and/or shift elements (S1-S7). The switching arrangements (SE1-SE4) arranged on major axis. The number of wheel planes (I,II) connected to input shafts is smaller than the number of wheel planes (III-VII) connected to driven shaft.

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.

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. Moreover, it is an object of the present invention to provide a transmission for a motor vehicle, which is easier and cheaper to produce and at the same time allows reliable transmission of torque between the drive and output. Moreover, it is an object of the present invention to provide an alternative transmission for a motor vehicle.

The present invention solves the problems in a transmission, in particular dual-clutch transmission, for a motor vehicle comprising at least two partial transmissions, each of the partial transmissions comprises at least one input shaft, and wherein an output shaft is arranged as the output shaft of both partial transmissions, wherein the at least one input shaft on a main axis and the output shaft is arranged on the main axis or on a, in particular parallel to the main axis, minor axis, and wherein a countershaft with at least one Countershaft is arranged, wherein the at least one countershaft 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, characterized in that at least N switching means are arranged, wherein the at least N Switching devices are arranged on the main axis, and that the number M of the wheel planes, which are arranged on at least one of the input shafts, is smaller than the number P of the wheel planes, which are arranged on the output shaft, where N, M and P are natural numbers , and where N is greater than or equal to 2.

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

One of the advantages achieved with this is that all the switching devices and thus also switching elements on the main axis, which acts as the central axis of the transmission, are arranged therewith. This allows a comfortable and flexible power sharing by means of the countershaft, in particular by arranging multiple countershafts in the countershaft. Likewise, larger torques can be transmitted from the drive to the output side in this way. 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 provides improved load shifting 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.

Expediently, in each case one of the two input shafts can be connected to at least one countershaft by means of a respective gear plane. One of the advantages achieved with this is that the input shafts can thus be made relatively short with regard to their extension along the main axis of the transmission, so that their production can be carried out inexpensively. In addition, a reliable transmission of power and torque from the input shafts on the at least one countershaft is possible.

Advantageously, M is less than 3, in particular less than 2. In this way, a particularly short extension of the two input shafts along the main axis of the transmission is possible. At the same time a particularly reliable transmission of power and torque of at least one of the input shafts on the countershaft is possible. If, in particular, M = 2 wheel planes are arranged, one of the two wheel planes can be assigned to one of the two input shafts, so that only one wheel plane transmits force and torques to the countershaft for each input shaft. Finally, the rotating masses, which are arranged on the two input shafts, substantially reduced.

Conveniently, P is greater than 4, in particular greater than 5. In this way, a variety of possible gears and gears on the basis of gear planes, which force and torques of the countershafts transmitted to the output shaft, are provided.

Advantageously, at least two of the input shafts are arranged coaxially with one another and / or at least one 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 makes a variety of gears respectively gear ratios representable by means of the transmission.

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

Advantageously, at least one of the input shafts 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. 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 the respective transmission elements on the corresponding shaft can thus be dispensed with.

Conveniently, two wheel planes are connected to each other by means of at least one switching element on the main axis. This is avoided on the one hand that a switching element must be arranged on the minor axis, which would significantly increase the radial structure of the transmission. On the other hand, by the coupling of at least two wheel planes, a force and torque transmission first from the countershaft to the main axis and by coupling the two wheel planes on the main axis back to the countershaft possible, so that more gears or grades are represented by the transmission.

Advantageously, at least one wheel plane is designed as a reverse gear. By means of the at least one reverse gear stage, the direction of rotation of the output shaft with respect to one of the input shafts can be reversed so that a reverse gear for a vehicle can be provided, which substantially increases the flexibility with regard to the use of the gearbox 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 connected to the output shaft. This allows a more direct and reliable transmission of torque by means of the reverse gear to the output shaft.

Advantageously, a respective transmission element of the reverse gear stage on the main axis and the minor axis is connected to a respective hollow shaft on the main axis and the minor axis. This prevents the reverse gear stage when transmitting large torques by means of a solid shaft additionally loads the solid shaft additionally by rotating the respective transmission elements on the respective axes. This increases the life of the solid shafts of the transmission as well as of the transmission as a whole.

Conveniently, an electric machine is arranged on at least one gear 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 with the first input shaft, is directly connected to a rotor of the electric machine connected to the drive. 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 aforementioned first connection possibility and the aforementioned second connection possibility by actuation of the further switching element possible.

Advantageously, the electric machine is arranged on at least one of the wheel planes, which is connected to a countershaft, designed as a solid 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 to the transmission, in particular ultimately to the output shaft, possible.

Conveniently, the electric machine is arranged by means of an additional switching device and a transmission element on the at least one gear plane. By means of the additional switching device, the electric machine can be coupled as needed to the transmission or connected to corresponding transmission elements of the transmission. At the same time enabling the registration of the electric machine by means of the additional switching device a simple and cost-effective retrofit option for existing transmission, if a hybridization of the transmission is to be made.

Advantageously, transmission elements of at least two, in particular at least three, 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 or to the corresponding transmission elements is extremely reliable possible.

Conveniently, the N switching means and the at least two wheel planes are arranged so that at least six forward gears and at least two reverse gears are represented by the transmission. One of the advantages achieved is that it can provide a sufficient number of forward gears and reverse gears for a variety of vehicles, especially for both passenger cars and trucks.

Advantageously, at least one, in particular two wheel planes are designed as drive constants. The advantage thus achieved is that it allows a particularly reliable transmission of force and torque from the drive via at least one of the input shafts to the output shaft and / or to at least one of the countershafts.

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 not only in each of the 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 described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components or elements.

In each case show in a schematic form

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

2 a shift matrix for a transmission according to the first embodiment of 1 ;

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

4 a transmission according to a third 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 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 with each other. Furthermore, the transmission includes 1 a major axis 2 , the torque and power downstream of the drive AN starting from the two clutches K1, K2 first a first gear plane I, a second gear plane II, a first switching element S1, a second switching element S2, and a third gear plane III and further has a seventh gear plane VII , a third switching element S3, a fourth switching element S4, a fourth gear plane IV, a fifth switching element S5, a fifth gear plane V, a sixth switching element S6, a seventh switching element S7, and a sixth gear plane VI. Each of the said wheel planes I, II, III, IV, V, VI and VII has transmission elements, in particular in the form of gears, which each with a shaft of the transmission 1 are connected. The third, fourth, fifth, sixth and seventh gear plane III, IV, V, VI, VII can be connected to an output shaft AW of the output AB by means of switching elements.

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, arranged in a portion of the first countershaft VW1 and formed as a hollow shaft second countershaft VW2. On the first countershaft VW1 are transmission elements for the wheel planes I, V and VI for the transmission of torque between the main axis 2 and minor axis 3 arranged. The second to the first countershaft VW1 coaxial countershaft VW2 includes transmission elements for the wheel planes II, III, IV and VII. Between the minor axis 3 and the main axis 2 the seventh wheel plane VII in the form of the reverse gear on 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 a reverse direction of rotation is provided to provide at least one reverse gear.

The switching elements S1, S2, S3, S4, S5, S6 and S7 will now be described below. When actuated, the first shift element S1 establishes a connection for transmitting power and torques between the first input shaft EW1 and the output shaft AW. When actuated, the second switching element S2 establishes a connection for transmitting force and torques between the output shaft AW and a first hollow shaft H1, which is arranged parallel and coaxial to the output shaft AW. On the first hollow shaft H1, a transmission element is arranged which cooperates with a transmission element on the second countershaft VW2 for transmitting force and torque between the two shafts, namely the output shaft AW and the second countershaft VW2. The two transmission elements form the third wheel plane III. The two switching elements S1, S2 are further combined to form a common first switching device SE1 and can be actuated by means of a common switching element actuation device SB1, ie can be brought into an open or a closed state.

The third switching element S3 is connected to a second hollow shaft H2, which is arranged parallel and coaxial with the output shaft AW, and, when actuated, establishes a connection for transmitting force and torques between the output shaft AW and the second hollow shaft H2. The transmission element on the second hollow shaft H2 interacts with an intermediate gear ZR and a corresponding transmission element on the second countershaft VW2 to form the seventh gear plane VII in the form of the reverse gear together. The transmission element on the second hollow shaft H2, the intermediate gear ZR and the transmission element on the countershaft VW2, which interacts with the intermediate gear ZR, thus form the reverse gear VII. The fourth switching element S4 is connected to a third hollow shaft H23, which is parallel and coaxial with the output shaft AW is arranged, and when actuated, establishes a connection for transmitting power and torques between the output shaft AW and the third hollow shaft H23. On the third hollow shaft H23 a transmission element is arranged, which cooperates with a corresponding transmission element on the second countershaft VW2 to form the fourth gear plane IV. The third hollow shaft H23 is further connected to a fifth switching element S5.

When actuated, the fifth shifting element S5 establishes a connection between the third hollow shaft H23 and a fourth hollow shaft H3 connected to the fifth shifting element S5. The fourth hollow shaft H3 is also arranged in parallel and coaxial with the output shaft AW. On the fourth hollow shaft H3, a transmission element is arranged, which cooperates with a corresponding transmission element on the first countershaft VW1 to form the fifth gear plane V. The fourth hollow shaft H3 is further connected to a sixth switching element S6. When actuated, the sixth shifting element S6 establishes a connection between the fourth hollow shaft H3 and the output shaft AW. The seventh switching element S7 is connected to a fifth hollow shaft H4, which is arranged parallel to and coaxial with the output shaft AW, and, when actuated, establishes a connection for transmitting force and torques between the fifth hollow shaft H4 and the output shaft AW. On the outside of the fifth hollow shaft H4, a transmission element is arranged, which cooperates with a transmission element on the first countershaft VW1 to form the sixth gear plane VI for the transmission of force and torques.

On the formed as a hollow shaft second input shaft EW2, a transmission element is arranged, which cooperates with a transmission element on the first countershaft VW1 to form the first gear plane I. On the solid shaft formed as a first input shaft EW1, a transmission element is arranged, which cooperates with a transmission element on the second countershaft VW2 to form the second gear plane II for transmitting force and torques.

Like the switching elements S1 and S2, the switching elements S3 and S4 are combined in a second switching device S2 and actuated by means of a common second switching element actuator 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 switching elements S6 and 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, H23, 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, VI and VII 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 Among other things, two input shafts EW1, EW2 on, 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 two countershafts VW1, VW2, one formed as a solid shaft and the other coaxial with this and designed as a hollow shaft. 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 comprises seven wheel planes I, II, III, IV, V, VI, VII, wherein the seventh wheel plane VII is formed as a reverse gear. All wheel planes I to VII are designed in particular as spur gears with discrete ratios. Per gear plane I, II, III, IV, V, VI, VII are each two transmission elements, in particular in the form of gears arranged. The reverse gear VII includes an additional gear in the form of an intermediate ZR. Overall, thus 15 transmission elements, in particular in the form of gears, arranged.

The wheel planes I and II can be coupled or connected to one of the input shafts EW1, EW2. By means of the first switching element S1, the first input shaft EW1 with the output shaft AW coupled. The transmission elements of the first gear plane I and the second gear plane II on the second input shaft EW2 and the first input shaft EW1 are firmly connected thereto. The first and second gear plane I, II are thus formed as drive constants. The transmission elements of the wheel planes II, III, VII, IV on the minor axis 3 are fixedly connected to the coaxial with the first countershaft VW1 arranged and designed as a hollow shaft second countershaft VW2.

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

2 shows a switching matrix for a transmission according to the first embodiment of the 1 ,

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

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

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

In 3 is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 are at the transmission 1 according to 3 the two wheel planes III and VII reversed in position along the major axis 2 arranged. The transmission element of the reverse gear stage VII on the main axis 2 is now connected to the first hollow shaft H1 and connectable by means of the third switching element S3 with the output shaft AW. The first switching element S1 and the third switching element S3 now form the first switching device SE1. The two switching elements S1, S3 can be actuated by means of the first switching element actuating device SB1. The wheel plane VII is thus by a transmission element on the first hollow shaft H1 on the main axis 2 , an intermediate gear ZR between the main axis 2 and minor axis 3 and a transmission element formed on the second countershaft VW2. The transmission element of the third wheel plane III on the main axis 2 is now connected to the second hollow shaft H2 and connected by means of the second switching element S2 with the output shaft AB. The second switching element S2 and the fourth switching element S4 are now combined in the second switching device SE2 and actuated by means of the common switching element actuator SB 2. The third wheel plane III is thus by a transmission element on the second hollow shaft H2 on the main axis 2 and a corresponding transmission element on the second countershaft VW2 on the minor axis 3 educated.

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

In 4 is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 includes the gearbox 1 according to 4 an electric machine EM. The electric machine EM is connectable via a fifth switching device SE5, comprising an eighth switching element S8 with a transmission element, which with a transmission element of the transmission 1 on the first countershaft VW1 for the transmission of force and torque interacts. The transmission element on the first countershaft VW1 corresponds to the transmission element of the minor axis 3 , which is assigned to the first wheel plane I. The fifth switching device SE5 can be actuated by means of a fifth switching element actuating device SB5. When the eighth shifting element S8 is actuated by means of the fifth shifting element operating device SB5, the electric machine EM can transmit power to the transmission element on the first countershaft VW1 and thus hybridize the transmission 1 according to 4 provide. The connection of the electric machine EM to the gearbox 1 can also at the transmission elements of the fifth and sixth gear plane V, VI on the minor axis 3 take place, ie at the wheel planes or stages, which have a transmission element on the formed as a solid shaft first countershaft VW1.

Overall, the switching elements S1 to S8 in the transmission 1 according to the 1 to 4 Also referred to as coupling devices and be designed in particular as synchronizers. Here, the first switching element S1 to the input shafts EW1, EW2 and the output shaft AW are assigned, the second switching element S2 of the third wheel plane III, the third switching element S3 of the seventh wheel plane VII in the form of reverse gear, the fourth switching element S4 of the fourth gear plane IV, the fifth switching element S5 of the fourth and fifth gear plane IV, V, the sixth switching element S6 of the fifth gear plane V and the seventh switching element S7 of the sixth gear plane VI. The first and second gear plane I, II are designed as drive constants.

In summary, the present invention has the advantage that all N switching devices and thus all the switching elements or coupling devices are arranged on the main axis and thus a flexible and comfortable power sharing is possible by using one or more countershafts. Furthermore, the present invention provides the advantage of seven wheel planes and at least four switching devices, as well as at least seven switching elements to provide at least six forward gears and at least two reverse gears available. Likewise, the invention offers the advantage that only four actuators in the form of 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. Finally, the present invention also offers the advantage that a reduction of the mechanical spread by winding the first forward gear is made possible.

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

The in the 1 - 4 shown embodiments can be combined.

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

wheel plane

AW

output shaft

EW1, EW2

input shaft

H1, H2, H23, H3, H4

hollow shaft

K1, K2

clutch

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

switching element

SB1, SB2, SB3, SB4, SB5

Switching element actuator

SE1, SE2, SE3, SE4, SE5

switching device

VW1, VW2

Countershaft

ZR

idler

AT

drive

FROM

output

EM

electric machine

QUOTES INCLUDE IN THE DESCRIPTION

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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), wherein the at least one countershaft (VW1, VW2) 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, VII) and / or at least one switching element (S1, S2, S3, S4, S5 , S6, S7) is connectable to the output shaft (AW), characterized in that at least N switching devices (SE1, SE2, SE3, SE4) are arranged, wherein the at least N switching devices (SE1, SE2, SE3, SE4) on the main axis ( 2 ), and that the number M of the wheel planes (I, II) arranged on at least one of the input shafts (EW1, EW2) is smaller than the number P of the wheel planes (III, IV, V, VI, VII ) disposed on the output shaft (AW), where N, M and P are natural numbers and where N is greater than or equal to two. Transmission according to claim 1, characterized in that in each case one of the two input shafts (EW1, EW2) can be connected to at least one countershaft (VW1, VW2) by means of a respective wheel plane (I, II). Transmission according to one of claims 1-2, characterized in that M is smaller than three, in particular smaller than two. Transmission according to one of claims 1-3, characterized in that P is greater than four, in particular greater than five. Transmission according to one of claims 1-4, characterized in that at least two of the input shafts (EW1, EW2) coaxially with each other and / or at least one second countershaft (VW2) coaxial with the at least one countershaft (VW1) are arranged. Transmission according to one of claims 1-5, characterized in that the number N is equal to four. Transmission according to one of claims 1-6, characterized in that at least one of the input shafts (EW1, EW2) and / or at least one of the countershafts (VW1, VW2) is designed as a hollow shaft and the respective other shaft as a solid shaft. Transmission according to one of claims 1-7, characterized in that two wheel planes (IV, V) by means of at least one switching element (S5) on the main axis ( 2 ) are connectable to each other. Transmission according to one of claims 1-8, characterized in that at least one wheel plane (VII) is designed as a reverse gear. Transmission according to claim 9, characterized in that the reverse gear (VII) by means of at least one of the N switching means (SE1, SE2, SE3, SE4) is operable, wherein the at least one switching device (SE2) is connected to the output shaft (AW). Transmission according to one of claims 9-10, characterized in that a respective transmission element of the reverse gear (VII) on the main axis ( 2 ) and the minor axis ( 3 ) each having a hollow shaft on the main axis ( 2 ) and the minor axis ( 3 ) connected is. Transmission according to one of claims 1-11, characterized in that an electric machine (EM) on at least one wheel plane (I, II, III, IV, V, VI, VII) and / or on at least one countershaft (VW1, VW2) and / or on one of the input shafts (EW1, EW2) for hybridizing the transmission ( 1 ) is arranged. Transmission according to claim 12, characterized in that the electric machine (EM) is arranged on at least one of the wheel planes (I, V, VI), which is connected to a countershaft (VW1), designed as a solid shaft. Transmission according to one of claims 12 or 13, characterized in that the electric machine (EM) by means of an additional switching device (SE5) and a transmission element on the at least one wheel plane (I, II, III, IV, V, VI, VII) is. Transmission according to one of claims 1-14, characterized in that transmission elements of at least two, in particular at least three wheel planes (II, III, VII, IV) on the minor axis ( 3 ) are connected to a formed as a hollow shaft countershaft (VW2), in particular fixed. Transmission according to one of claims 1-15, characterized in that the N switching means (SE1, SE2, SE3, SE4) and the at least two wheel planes (I, II, III, IV, V, VI, VII) are arranged so that at least six forward gears and at least two reverse gears through the transmission ( 1 ) are representable. Transmission according to one of claims 1-16, characterized in that at least one, in particular two, wheel planes (I, II) are formed as drive constant. 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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