DE102012209333A1 - Gear box e.g. dual clutch transmission for motor car, has reduction gear with countershafts that are provided on minor axis, and gear train with input shaft is connected with output shaft by gear planes and/or switching elements - Google Patents

Abstract

The gear box (1) has a gear train with input shafts (EW1,EW2) and an output shaft. The input shaft is arranged in major axis (2) and output shaft is arranged in minor axis (3). The major axis is parallel to minor axis. A reduction gear (4) is arranged with countershafts (VW1,VW2) that are provided on minor axis. The input shaft is connected with output shaft by gear planes (I-VII) and/or switching elements (S1-S8). The switching element of switching devices (SE1-SE4) is connected with switching element of adjacent switching device through a connecting shaft (H23). An independent claim is included for a motor car.

Description

Transmission for a motor vehicle

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 on the Main axle or on a, in particular to the main axis parallel, minor axis is arranged, 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 by means of at least two wheel planes and / or at least a switching element with the output shaft is connectable.

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

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

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

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

It is therefore an object of the present invention to provide 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.

One of the advantages achieved thereby is that a vast majority of switching elements, in particular all, are arranged on the main axis, which acts as the central axis of the transmission. This allows a comfortable and flexible power sharing by means of the Vorgeleges. Likewise, larger torques can be transmitted from the drive to the output side in this way. In addition, a reduction of a mechanical spread by winding the first forward gear of the transmission is possible in this way. Finally, the transmission also offers improved load shifting capability and good hybridizability, since an electric machine can be coupled to the transmission in a simplified manner.

The present invention solves at least one of the tasks in a transmission, in particular dual-clutch transmission for a motor vehicle, comprising at least two partial transmissions, wherein each of the partial transmissions comprises at least one input shaft 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 minor axis parallel to the main 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 arranged by means of at least two Radebenen and / or by means of at least one switching element with the output shaft is connectable, characterized in that switching means of the number N are arranged, wherein N is a positive integer greater than or equal to two, and wherein at least N - 1 switching devices n are arranged on the main axis and that at least two switching devices are arranged adjacent to the main axis, wherein at least one switching element of at least two adjacent switching devices is connected via at least one first connecting shaft with at least one switching element of the other of the two switching devices.

The invention solves the objects also by 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 thereby is that a vast majority of switching elements, in particular all, are arranged on the main axis, which acts as the central axis of the transmission. This allows a comfortable and flexible power sharing by means of the Vorgeleges. Likewise, larger torques can be transmitted from the drive to the output side in this way. In addition, a reduction of a mechanical spread by winding the first forward gear of the transmission is possible in this way. Finally, the transmission also offers improved load shifting capability and good hybridizability, since an electric machine can be coupled to the transmission in a simplified manner.

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

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

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

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

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

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

Conveniently, an intermediate shaft between at least one of the input shafts and the output shaft is arranged, which is connectable by means of at least two switching elements with one of the input shafts and / or with the output shaft and / or with at least one of the countershafts. An advantage achieved with this is that the flexibility of the transmission is significantly increased, as in a simple and reliable way different wheel planes can be connected to provide gear ratios. In this way, also the number of gear ratios can be increased without significantly higher costs.

Advantageously, at least two of the input shafts are arranged coaxially with one another and / or at least two countershafts are arranged coaxially with one another. 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, exactly one gear plane is arranged on the intermediate shaft. In this way, on the one hand by the intermediate shaft, the flexibility of the transmission can be increased in terms of other grades, on the other hand, the intermediate shaft can also be made extremely compact in the transmission, so that the transmission in the axial direction, ie along the main axis, also made compact in spite of other gear ratios can be.

Advantageously, at least one first connecting shaft is formed here as a hollow shaft or a solid shaft. One of the advantages of a design as a hollow shaft is that it can be arranged coaxially with other shafts so that the most compact possible arrangement of the first connecting shaft is possible. If the at least one first connecting shaft is designed as a solid shaft, then a cost-effective and reliable connection, for example between two switching elements of the transmission connected to it, is possible for force and torque transmission.

Conveniently, the intermediate shaft is formed as a connecting shaft and in particular connected to a switching element of one of the switching devices, which is connected with its second switching element with the first connecting shaft. One of the advantages achieved with this is that on the one hand, the flexibility of the transmission is increased even further, since a large number of possible connections or couplings between different shafts and different wheel planes is made possible. Another advantage is that at the same time an extremely compact construction of connecting shafts and switching devices in the transmission is made possible.

Advantageously, at least one second countershaft, in particular coaxial with the first countershaft, arranged and the second countershaft cooperates with transmission elements at least two, in particular at least three wheel planes together. Thus, the number of gears or grades that can be represented by the transmission, be further increased without the space is significantly increased and without high costs for the arrangement of waves or wheel planes in the transmission arise.

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

Advantageously, the two adjacent to the drive side of the transmission wheel planes by means of a arranged on the minor axis switching device with one of the input shafts on the one hand and with at least one of the countershafts on the other hand connectable. In this way, on the one hand, a reliable transmission of torque directly from one of the input shafts on the countershaft allows, on the other hand allows the arrangement of the switching device on the minor axis a reduced space for the transmission, since thus the number of switching elements on the main axis and thus Overall, the extension of the transmission along the main axis and thus also the minor axis can be reduced.

Conveniently, 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.

Advantageously, the reverse gear can be connected to one of the input shafts by means of a switching element located closest to the drive side of the transmission, in particular. One of the advantages achieved thereby is that on the one hand a more direct transmission of torques on the at least one wheel plane, designed as a reverse gear, is made possible, on the other hand can be provided by the transmission several reverse gear, so that the transmission even more flexible in a variety of vehicles can be used.

Conveniently, an electrical machine on at least one wheel plane and / or at at least one countershaft and / or arranged on the intermediate shaft 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 take place on at least one of the input, intermediate or output shafts or on 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 possibility of 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 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 planet gear, a ring gear, planetary gears and a planet carrier, is designed in this way, and cooperates with the internal combustion engine and the electric machine, so that the planet carrier acts on the second input shaft. The electric machine is coupled to the sun gear of the planetary gear. In addition, a further switching element may be arranged in the form of a bridging switching element, which cooperates with the planetary gear, so that when actuated lock-up switching element a rotationally fixed connection between the electric machine, the first input shaft and the second input shaft, whereas not actuated, so open, Bridging switching element, the aforementioned non-rotatable connection between the electric machine and the first and second input shaft does not exist, in particular so there is no speed equality between the two input shafts.

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

Advantageously, the electric machine is arranged on at least one of the wheel planes, which are connected to the second countershaft. 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 ultimately, in particular to the output shaft possible.

Conveniently, a wheel plane, arranged on the first connecting shaft, can be connected to both input shafts. This allows a variety of representable gears by means of the transmission at the same time compact space, since the countershaft by means of the wheel plane in a simple manner can be coupled with both input shafts.

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

Conveniently, the transmission elements, in particular designed as gears, the wheel planes, which are connected to the second countershaft, designed as fixed wheels. One of the advantages achieved with this is that the transmission elements together with the countershaft can be produced inexpensively, in particular by a one-piece design of transmission elements together with the countershaft. In addition, a connection or coupling of an electrical machine to the transmission in a very reliable manner possible.

Advantageously, the N switching devices and the at least two wheel planes are arranged so that at least six forward gears and at least two reverse gears are represented by the transmission. One of the advantages achieved with this is that a sufficient number of forward gear ratios and reverse gear ratios can be made available for a large number of vehicles, in particular for passenger cars and for lorries.

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

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

Preferred embodiments and embodiments of the invention are illustrated in the drawings and will be 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;

3a . 3b Schaltmatrizen for a transmission according to the first embodiment of 1 ;

4a . 4b Switching matrices for a transmission according to the second embodiment according to 2 ;

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

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

6a a transmission according to a fifth embodiment of the present invention;

6b a transmission according to a sixth embodiment of the present invention;

6c a transmission according to a seventh embodiment of the present invention and

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

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

In 1 denotes reference numeral 1 a transmission in the form of a dual-clutch transmission. The dual-clutch transmission 1 has two load switching elements in the form of clutches K1, K2. By means of the double clutch K1, K2, the drive side AN can be coupled with the output side AB for transmitting torque. For this purpose, the first clutch K1 is connected to a first input shaft EW1 and the second clutch K2 is connected to a second input shaft EW2. The second input shaft EW2 is designed as a hollow shaft, whereas the first input shaft EW1 is formed as a solid shaft. The two input shafts EW1, EW2 are arranged coaxially with each other. Furthermore, the transmission includes 1 a major axis 2 which, starting from the two clutches K1, K2, initially has a first wheel plane I, a first shift element S1, a second shift element S2 and a second wheel plane II, downstream of the drive AN, and further comprises a seventh wheel plane VII, a third shift element S3, a fourth shift element S4, a third wheel plane III, a fifth shift element S5, a sixth shift element S6, a fourth wheel plane IV, a seventh shift element S7, an eighth shift element S8, a fifth wheel plane V. and a sixth wheel plane VI. Each of the said wheel planes I, II, III, IV, V, VI and VII has transmission elements, each having a shaft of the transmission 1 are connected. The sixth wheel plane VI is thus connected to an output shaft AW of the output AB.

Parallel to the main axis 2 is a minor axis 3 for a counterfeit 4 arranged. The counterpart 4 in this case comprises a first countershaft VW1, designed as a solid shaft and a thereto, 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, II and VI. arranged to transmit torques. The second to the first countershaft VW1 coaxial countershaft VW2 includes transmission elements for the wheel planes III, IV, V and VII. Between the minor axis 3 and the main axis 2 has 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 at the same Direction of rotation of one of the input shafts EW1, EW2 an inverted direction of rotation to provide at least one reverse gear is possible.

In the following, the switching elements S1, S2, S3, S4, S5, S6, S7, S8 are described: The first switching element S1, when actuated, transmits torques from the second input shaft EW2 and a first hollow shaft H1a, which on the outside of the second input shaft EW2 is arranged coaxially to this, forth. On the first hollow shaft H1a is a transmission element for transmitting torques from the main axis 2 on the minor axis 3 arranged. This transmission element together with a correspondingly formed transmission element on the minor axis 3 forms the above-explained wheel plane I. The second switching element S2 establishes a connection between the second input shaft EW2 and a second hollow shaft H1b. On the second hollow shaft H1b, a transmission element is also arranged, which cooperates with a transmission element on the first countershaft VW1 for transmitting forces and torques between the two shafts, namely the second input shaft EW2 and the first countershaft VW1. The two transmission elements in this case form the second wheel plane II. The two switching elements S1, S2 are further combined to form a first common switching device SE1 and can be actuated by means of a common switching device actuation element SB1, ie can be brought into an open or in a closed state. The second input shaft EW2 is also connected to the third switching element S3. The third switching element S3 is further connected to a third hollow shaft H2a, which is arranged coaxially with the second input shaft EW2, and has a transmission element which cooperates with an intermediate gear ZR and a transmission element on the second countershaft VW2 for transmitting torques. The intermediate gear ZR and the two transmission elements on the third hollow shaft H2a and the second countershaft VW2 thereby form the seventh wheel plane VII in the form of a reverse gear. The second input shaft EW2 is further connected to the fourth switching element S4. The fourth switching element S4 is further connected to a connecting shaft H23 in the form of a further hollow shaft, which allows a transmission element for transmitting torques from the second input shaft EW2 to the second countershaft VW2. For this purpose, corresponding transmission elements of the second countershaft VW2 cooperate with the transmission element on the connecting shaft H23. These form the third wheel plane III.

The connection shaft H23 is further connected to the fifth switching element S5. The fifth switching element S5 is further connected to the first input shaft EW1 and allows transmission of forces and torques from the first input shaft EW1 to the connecting shaft H23.

The sixth switching element S6 is connected to an intermediate shaft ZW. The intermediate shaft ZW is in the axial direction of the transmission 1 along the main axis 2 arranged between the input shafts EW1, EW2 and the output shaft AW. At the intermediate shaft ZW a transmission element for transmitting torque from the intermediate shaft ZW is arranged on the second countershaft VW2. On the second countershaft VW2 a corresponding transmission element is arranged, which cooperates with the transmission element on the intermediate shaft ZW for transmitting torques. The two transmission elements on the intermediate shaft ZW and on the second countershaft VW2 thereby form the fourth gear plane IV.

The intermediate shaft ZW is also connected to a seventh switching element S7. Upon actuation of the seventh switching element S7, a transmission of force and torque between the intermediate shaft ZW and the output shaft AW is possible. Furthermore, an eighth switching element S8 is arranged. The eighth switching element S8 enables transmission of torques between the output shaft AW and a fourth hollow shaft H4. On the outside of the hollow shaft H4, which is arranged coaxially to the output shaft AW, a transmission element for transmitting torque between the fourth hollow shaft H4 and the second countershaft VW2 is arranged. The second countershaft VW2 also has a corresponding transmission element for this purpose. The two transmission elements on the fourth hollow shaft H4 and the second countershaft VW2 thereby form the fifth gear plane V. Finally, the output shaft AW has a further transmission element, which cooperates with a transmission element on the first countershaft VW1. These two transmission elements form the sixth wheel plane VI. According to 1 the sixth wheel plane VI is designed as an output constant.

Overall, the third switching element S3 and the fourth switching element S4 are combined in a second switching device SE2, which can be actuated by means of a common second switching element actuation device SB2. The same applies accordingly to the fifth switching element S5 and the sixth switching element S6, which are combined to form a third switching device SE3. The two switching elements S5, S6 are correspondingly actuated by means of a third switching element actuator SB3. The Switching device SE4 comprises the switching elements S7 and S8, which can be actuated by means of a fourth switching element actuating device SB4. The switching element actuators SB1, SB2, SB3, SB4 can be embodied as double synchronizers.

The transmission elements can be both fixed and 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 the intermediate shaft ZW and / or the hollow shafts H1a, H1b, H2a, H23 and H4 be arranged or connected. The transmission elements can be designed in particular in the form of gears, in particular 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 different ratios to provide different forward and / or reverse gears.

Overall, the gearbox has 1 according to 1 two input shafts EW1, EW2 on, one formed as a full and the other 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 intermediate shaft ZW and the output shaft AW are 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 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, in each case two transmission elements, in particular in the form of gears are 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, II, VII, and III can be coupled to one of the input shafts EW1, EW2. By means of the sixth switching element S6, the intermediate shaft ZW can be coupled to the first input shaft EW1. By means of the seventh switching element S7, the intermediate shaft ZW can be coupled to the output shaft AW. A transmission element of the wheel plane VI is fixedly connected to the output shaft AW and to a corresponding transmission element of the first countershaft VW1. The sixth wheel plane VI is thus formed output constant. The transmission elements of the wheel planes VII, III, IV, V 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 transmission according to a second embodiment of the present invention.

In 2 is essentially a transmission 1 according to 1 shown. In contrast to 1 has the gearbox 1 another sequence of the first three wheel levels I, II and VII. Instead of the first wheel plane I the 1 is now the wheel plane VII, comprising the idler gear ZR and formed arranged as a reverse gear and connectable by means of the switching element S3 with the second input shaft EW2. The first switching device SE1 is formed by the switching elements S3, S1. Furthermore, in contrast to 1 is the transmission element of the seventh wheel stage VII on the minor axis 3 not connected to the second countershaft VW2, but to the first countershaft VW1. Instead of the second wheel plane II of 1 is now the first wheel I arranged. The transmission element of the first wheel stage I on the main axis 2 is connected to the first switching element S1 of the first switching device SE1 by means of the second hollow shaft H1b. Instead of the seventh wheel plane VII according to 1 now the second wheel plane II is arranged. The transmission elements of the second gear plane II are connected on the one hand to the third hollow shaft H2a and on the other hand to the first countershaft VW1. The third hollow shaft H2a can be connected to the second input shaft EW2 by means of the second switching element S2. The second countershaft VW2 according to 2 extends in contrast to the second countershaft VW2 according to 1 only in the area of the wheel planes III, IV and V on the minor axis 3 , unlike the second countershaft VW2 in the 1 in which the second countershaft VW2 extends in the area of the wheel planes VII, III, IV and V.

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

3a shows a first shift matrix for a transmission according to the first embodiment of the 1 ,

In 3a is a first switching matrix for a transmission 1 according to 1 shown. Horizontal each column for each switching element S1 to S8 are arranged. Perpendicular to this down are first the six forward gear stages, indicated by the numbers 1 to 6, and four reverse gears, labeled R1 through R4. The entries released in the matrix, so for example in the forward gear 1 in the switching elements S1, S2, S3, S5, S6, S7 indicate that the corresponding switching element is open, that is, that the switching element in this case transmits no forces or no torque from the respective shafts connected to the switching element. A cross-referenced entry in the switch matrix indicates a corresponding closed switch element. 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 3a represent, the clutch K1 are open and the clutch K2 closed and the switching elements S1, S2, S3, S5, S6, S7 open and the switching elements S4 and S8 closed. To illustrate the second gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S4, S5, S7 open and the switching elements S6 and S8 closed. To illustrate the third gear, the clutch K1 are open and the clutch K2 closed and the switching element S1 is closed and the switching elements S2, S3, S4, S5, S6, S7, S8 open. To illustrate the fourth gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S4, S6, S8 opened and the switching elements S5 and S7 closed. To illustrate the fifth gear, the clutch K1 are open and the clutch K2 closed and the switching element S2 closed and the switching elements S1, S3, S4, S5, S6, S7, S8 open. To represent the sixth gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S4, S5, S8 open and the switching elements S6 and S7 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, S5, S6, S8 are opened and the shifting elements S3 and S7 are closed. In order to represent the second reverse gear R2, the clutch K1 are opened and the clutch K2 is closed and the shifting elements S1, S2, S4, S5, S7 are opened and the shifting elements S3 and S8 are closed. To represent the third reverse gear R3, the clutch K1 are closed and the clutch K2 is opened and the shift elements S1, S4, S5, S7, S8 open and the shift elements S2, S3, S6 closed. To represent the fourth reverse gear R4, the clutch K1 are closed and the clutch K2 is opened and the shifting elements S2, S4, S5, S7, S8 are opened and the shifting elements S1, S3, S6 are closed.

3b shows a second shift matrix for a transmission according to the first embodiment of 1 ,

In 3b is a second switching matrix for a transmission 1 according to 1 shown. Here again, released entries designate the in 3b shown switching matrix a corresponding open switching element for the corresponding gear and provided with a cross entry a closed for this gear switching element. To represent the first gear, the clutch K1 are open and the clutch K2 closed and the switching elements S1, S2, S3, S5, S6, S7 open and the switching elements S4 and S8 closed. To illustrate the second gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S4, S5 and S7 open and the switching elements S6 and S8 closed. To illustrate the third gear, the clutch K1 are open and the clutch K2 closed and the switching elements S1, S3, S4, S5, S6, S7, S8 open and the switching element S2 closed. To illustrate the fourth gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S4, S6, S8 opened and the switching elements S5 and S7 closed. To represent the fifth gear, the clutch K1 are open and the clutch K2 closed and the switching elements S2, S3, S4, S5, S6, S7, S8 open and the switching element S1 is closed. To represent the sixth gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S4, S5, S8 open and the switching elements S6 and S7 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, S5, S6, S8 are opened and the shifting elements S3 and S7 are closed. In order to represent the second reverse gear R2, the clutch K1 are opened and the clutch K2 is closed and the shifting elements S1, S2, S4, S5, S7 are opened and the shifting elements S3 and S8 are closed. To represent the third reverse gear R3, the clutch K1 are closed and the clutch K2 is opened and the shift elements S1, S4, S5, S7, S8 open and the shift elements S2, S3, S6 closed. To represent the fourth reverse gear R4, the clutch K1 are closed and the clutch K2 is opened and the shifting elements S2, S4, S5, S7, S8 are opened and the shifting elements S1, S3, S6 are closed.

In this way, by means of the transmission 1 according to 1 six forward gears and four reverse gears representable.

4a shows a first shift matrix for a transmission according to the second embodiment according to 2 ,

In 4a is a first switching matrix for a transmission 1 according to 2 shown. Just like in the 3a . 3b Re-release entries in the switching matrix denote a correspondingly opened switching element for the corresponding gear and a cross-lined entry a switching element closed for this gear. To represent the first gear, the clutch K1 are open and the clutch K2 closed and the switching elements S1, S2, S3, S5, S6, S7 open and the switching elements S4 and S8 closed. To illustrate the second gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S4, S5, S7 open and the switching elements S6 and S8 closed. To represent the third gear, the clutch K1 are open and the clutch K2 closed and the switching elements S2, S3, S4, S5, S6, S7, S8 open and the switching element S1 is closed. To illustrate the fourth gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S4, S6, S8 opened and the switching elements S5 and S7 closed. To illustrate the fifth gear, the clutch K1 are open and the clutch K2 closed and the switching elements S1, S3, S4, S5, S6, S7, S8 opened and the switching element S2 closed. To represent the sixth gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S4, S5, S8 open and the switching elements S6 and S7 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, S5, S6, S7, S8 are opened and the shifting element S3 is closed. To represent the second reverse gear R2, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S5, S7, S8 open and the switching elements S3, S4, S6 closed. In this way, by means of the transmission 1 according to 2 six forward gears and two reverse gears representable.

4b shows a second shift matrix for a transmission according to the second embodiment according to 2 ,

In 4b is a second switching matrix for the transmission 1 according to 2 shown. Here again, released entries in the switching matrix designate a correspondingly opened switching element for the corresponding gear and an entry provided with a cross designates a switching element closed for this gear. To represent the first gear, the clutch K1 are open and the clutch K2 closed and the switching elements S1, S2, S3, S5, S6, S7 open and the switching elements S4 and S8 closed. To illustrate the second gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S4, S5, S7 open and the switching elements S6 and S8 closed. To illustrate the third gear, the clutch K1 are open and the clutch K2 closed and the switching elements S1, S3, S4, S5, S6, S7, S8 open and the switching element S2 closed. To illustrate the fourth gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S4, S6, S8 opened and the switching elements S5 and S7 closed. To represent the fifth gear, the clutch K1 are open and the clutch K2 closed and the switching elements S2, S3, S4, S5, S6, S7, S8 open and the switching element S1 is closed. To represent the sixth gear, the clutch K1 are closed and the clutch K2 open and the switching elements S1, S2, S3, S4, S5 and S8 open and the switching elements S6 and S7 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, S5, S6, S7, S8 are opened and the shifting element S3 is closed. To represent the second reverse gear R2, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S5, S7, S8 open and the switching elements S3, S4 and S6 closed. In this way, by means of the transmission 1 according to 2 six forward gears and two reverse gears representable.

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

In 5a is essentially a transmission 1 according to 1 shown. In contrast to 1 the two wheel planes I and II are arranged interchanged. By means of the first switching element S1 of the first switching device SE1 is thus the second input shaft EW2 connected to the first countershaft VW1 and by means of the second switching element S2 of the first switching device SE1, the second input shaft EW2 with the first countershaft VW1 connectable. The corresponding transmission element of the second wheel plane II on the main axis 2 is connected to the first hollow shaft H1a and the corresponding transmission element on the main axis 2 the first gear plane I is connected to the second hollow shaft H1b.

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

In 5b is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 are at the transmission 1 according to 5b the two switching elements S1, S2, thus the first switching device SE1 from the main axis 2 on the minor axis 3 postponed. Accordingly, now the first wheel plane I by a transmission element on the second input shaft EW2 and a transmission element on the minor axis 3 educated. The transmission element on the minor axis 3 is connected to a third countershaft VW3a, which in turn cooperates with the first switching element S1 for connecting third countershaft VW3a and first countershaft VW1. The second gear plane II is formed by a transmission element on the radial outer side of the input shaft EW2, which with a transmission element on the minor axis 3 interacts. The transmission element on the minor axis 3 the second gear plane II is arranged on a fourth countershaft VW3b, which is connected to the second switching element S2. The countershafts VW3a, VW3b are arranged coaxially with the first countershaft VW1 and designed as a hollow shaft. The switching element S2 allows for a corresponding operation a connection between the fourth countershaft VW3b with the first countershaft VW1. The first switching device SE1 in turn comprises the switching elements S1 and S2, which can be actuated by means of a switching device actuation element SB1.

6a shows a transmission according to a fifth embodiment of the present invention.

In 6a is essentially a transmission 1 according to 2 shown. Unlike the gearbox 1 according to 2 are the first gear plane I and the second gear plane II in terms of their axial position on the major and minor axis 2 . 3 arranged reversed. The transmission element on the main axis 2 The second gear plane II is now arranged on a radial outer side of the second hollow shaft H1b and connectable by means of the second switching element S2 with the second input shaft EW2. The transmission element of the first wheel plane I on the main axis 2 is now arranged on the radial outer side of the third hollow shaft H2a and connectable by means of the third switching element S3 with the second input shaft EW2.

6b shows a transmission according to a sixth embodiment of the present invention.

In 6b is essentially a transmission 1 according to 2 shown. Unlike the gearbox 1 according to 2 are at the transmission 1 according to 6b the wheel planes I and VII along the main axis 2 or minor axis 3 arranged reversed. The first wheel plane I is now arranged substantially between the two clutches K1 and K2 and the first switching device SE1. The transmission element on the main axis 2 The first gear plane I is thus connected to a transmission element of the first hollow shaft H1a and connected by means of the first switching element S1 with the second input shaft EW2. The transmission element of the seventh wheel plane VII, designed as a reverse gear with intermediate gear ZR, which on the main axis 2 is arranged, is connected to a transmission element of the second hollow shaft H1b and connectable by means of the second switching element S2 with the second input shaft EW2.

6c shows a transmission according to a seventh embodiment of the present invention.

In 6c is essentially a transmission 1 according to 2 shown in the analogy to 5b the first switching device SE1 with the two switching elements S1 and S2 from the main axis 2 on the minor axis 3 is moved. By means of the first switching element S1 of the switching device SE1 is the third countershaft VW3a with the first Vorlagewelle VW1 connectable. The third countershaft VW3a is arranged coaxially with the first countershaft VW1 and designed as a hollow shaft. On the outside of the third leading wave VW3a a transmission element is arranged, which with the intermediate gear and a transmission element of the seventh wheel plane VII on the main axis 2 for the transmission of torque with appropriate operation of the first switching element S1 cooperates. The second switching element S2 of the first switching device SE1 on the minor axis 3 is connected to a fourth countershaft VW3b and connectable upon actuation of the second switching element S2 with the first Vorlagewelle VW1. The fourth countershaft VW3b is arranged coaxially with the first countershaft VW1 and designed as a hollow shaft. On the outside of the fourth leading wave VW3b a transmission element is arranged, which with a transmission element on the main axis 2 and arranged on the outside of the input shaft EW2 for transmitting torque between the second input shaft EW2 and the first countershaft VW1 cooperates.

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

In 7 is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 includes the gearbox 1 according to 7 an electric machine EM. The electric machine EM is connected via a transmission element with the transmission element of the third wheel plane III, which is arranged on the second countershaft VW2, for hybridizing the transmission 1 connected. The connection of the electric machine EM to the gearbox 1 can also take place at the wheel planes VII, IV and V, ie at the wheel planes or stages, which is a transmission element on the minor axis 3 have on the outside of the second countershaft VW2. In a transmission 1 according to 2 can be the connection of the electric machine EM to the gearbox 1 also with transmission elements on the second countershaft VW2 on the minor axis 3 the wheel planes III, IV and V take place.

Overall, the switching elements S1 to S8 in the transmission 1 according to 1 Also referred to as coupling devices, in particular be designed as synchronizers. In this case, the switching element S1 of the first wheel plane I, the second switching element S2 of the second wheel plane II, the third switching element S3 of the seventh wheel plane VII, the fourth and fifth switching element S4, S5 of the third wheel plane III, the sixth and seventh switching element S6, S7 the fourth gear plane IV and the eighth switching element S8 of the fifth gear plane V. The sixth gear plane VI in the transmission 1 according to 1 or 2 is designed as an output constant.

In summary, the present invention provides the advantage that, in particular, if all N switching elements or coupling devices or switching devices are arranged on the main axis, a flexible and comfortable power division is made possible by using one or more countershafts. Next, the invention offers the advantage of seven wheel planes and at least four switching devices to provide at least six forward gears and at least two, especially four reverse gears available. Likewise, the invention offers the advantage that only four actuators in the form of the switching devices for actuating the eight switching elements must be provided. Another advantage of the present invention is that the transmission has good load shifting capability and good hybridisability. Finally, the present invention also offers the advantage of a flexible and cost-effective transmission with the largest possible number of forward and / or reverse gears.

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

The gear 1 of the 1 and the gearbox 1 according to 2 can be transformed functionally identical by different positions of the wheel planes and / or the switching elements. For this purpose, the switching elements, in particular formed as synchronizers, as mentioned above, the wheel planes or waves are assigned. The switching matrices according to the 3a . 3b . 4a . 4b Thus, do not change by rearranging the wheel planes or the switching elements.

LIST OF REFERENCE NUMBERS

1

transmission

2

main axis

3

minor axis

4

countershaft

I, II, III, IV, V, VI, VII

wheel plane

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

switching element

SE1, SE2, SE3, SE4

switching device

EW1, EW2

input shaft

VW1, VW2, VW3a, VW3b

Countershaft

H1a, H1b, H2a, H23, H4

hollow shaft

FROM

output

AT

drive

ZW

intermediate shaft

AW

output shaft

ZR

idler

EM

electric machine

SB1, SB2, SB3, SB4

Switching element actuator

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 [0029]

Claims (17)

Transmission ( 1 ), in particular dual-clutch transmission, for a motor vehicle, comprising at least two partial transmissions, wherein each of the partial transmissions comprises at least one input shaft (EW1, EW2), and wherein an output shaft is arranged as the output shaft of both partial transmissions, wherein the at least one input shaft (EW1, EW2) 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, VW3a, VW3b), wherein the at least one countershaft 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, S8) to the output shaft (AW) is connectable, characterized in that switching means (SE1, SE2, SE3, SE4) of the number N are arranged, where N is a positive integer greater than or equal to two and wherein at least N - 1 switching devices (SE1, SE2, SE3, SE4) on the main axis ( 2 ) and that at least two switching devices (SE1, SE2, SE3, SE4) on the main axis ( 2 ), wherein in each case at least one switching element (S4) of one of the at least two adjacent switching devices (SE1, SE2, SE3, SE4) via at least one first connecting shaft (H23) with at least one switching element (S5) of the other of the two switching devices (SE2 , SE3).  Transmission according to claim 1, characterized in that an intermediate shaft (ZW) between at least one of the input shafts (EW1, EW2) and the output shaft (AW) is arranged, which by means of at least two switching elements (S1, S2, S3, S4, S5, S6 , S7, S8) can be connected to one of the input shafts (EW1, EW2) and / or to the output shaft (AW) and / or to at least one of the countershafts (VW1, VW2, VW3a, VW3b).  Transmission according to one of claims 1-2, characterized in that at least two of the input shafts (EW1, EW2) coaxial with each other and / or at least two countershafts (VW2, VW3a, VW3b) are arranged coaxially with each other.  Transmission according to one of claims 1-3, characterized in that exactly one gear plane (IV) on the intermediate shaft (ZW) is arranged.  Transmission according to one of claims 1-4, characterized in that the at least one first connecting shaft (H23) is formed as a hollow shaft or a solid shaft.  Transmission according to one of claims 1-5, characterized in that the intermediate shaft (ZW) is formed as a second connecting shaft and in particular with a switching element (S6) one of the switching devices (SE2, SE3) is connected, which with its second switching element (S5) is connected to the first connection shaft (H23).  Transmission according to one of claims 1-6, characterized in that at least one second countershaft (VW2, VW3a, VW3b), in particular coaxial with the first countershaft (VW1), is arranged, and the second countershaft (VW2, VW3a, VW3b) with transmission elements at least two, in particular at least three, wheel planes (III, IV, V, III, IV, V, VI) cooperates.  Transmission according to one of claims 1-7, characterized in that at least two, in particular at least three, wheel planes (I, II, III) by means of at least one switching element (S1, S2, S3) with at least one of the input shafts (EW1, EW2) connectable are. Transmission according to one of claims 1-8, characterized in that the two to the drive side (AN) of the transmission ( 1 ) nearest wheel-planes (I, II) by means of one on the minor axis ( 3 ) arranged switching means (SE1) with one of the input shafts (EW1, EW2) on the one hand and with at least one of the countershafts (VW1, VW3a, VW3b) on the other hand connectable.  Transmission according to one of claims 1-9, characterized in that at least one wheel plane (VII) is designed as a reverse gear. 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, VII) and / or on at least one countershaft (VW1, VW2, VW3a, VW3b) and / or on the intermediate shaft (ZW) 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 the wheel plane (III, IV, V, VI), which are connected to the second countershaft (VW2).  Transmission according to one of claims 1-12, characterized in that a wheel plane (III), arranged on the first connecting shaft (H23), with both input shafts (EW1, EW2) is connectable. Transmission according to one of claims 1-13, characterized in that one of the wheel planes (VI) is designed as output constant.  Transmission according to one of claims 7-14, characterized in that the transmission elements, in particular designed as gears, the wheel planes (III, IV, V, VII), which are connected to the second countershaft (VW2), designed as fixed wheels. 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. Motor vehicle, in particular a passenger or a truck, with a transmission ( 1 ) according to any one of claims 1-16.

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