DE102012203067A1 - Dual clutch transmission for motor car e.g. passenger car, has input shafts that is connected with output shaft through gear planes and switching elements, to obtain drive and output - Google Patents

Abstract

The dual clutch transmission (1) has reduction gear (4) that is arranged with countershafts (VW1-VW3). The countershafts are located on minor axis (3). The N switching devices (SE1-SE4) are arranged with switching elements (S1-S7), where N is an integer greater than or equal to three. The input shafts (EW1,EW2) is connected with an output shaft (AW) through gear planes (I-VI) and switching elements, to obtain drive (AN) and output (AB). The switching device (SE3) with switching elements (S3,S4), is placed on minor axis.

Description

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

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

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

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

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

An object of the present invention is therefore to provide a transmission for a motor vehicle, which has a good load switching capability and a good hybridisability. Moreover, it is an object of the present invention to provide a transmission for a motor vehicle, which is simple and inexpensive to produce and at the same time allows reliable transmission of torque between the drive and output. Another object of the present invention is to provide an alternative transmission for a motor vehicle.

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

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 16.

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

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

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

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

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

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

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

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

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

Conveniently, that switching device which is arranged directly to the side of the drive, arranged on the main axis. One of the advantages achieved with this is that space or space in the area of the side of the drive in the transmission for the countershaft is made available. Another advantage is that it makes the countershaft easier to access, for example in the case of maintenance.

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

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

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

Conveniently, at least four wheel planes are connectable by means of at least one switching element on the main axis with at least one of the input shafts. In this way, for example, if transmission elements of a plurality of wheel planes can be connected or coupled to at least one of the input shafts, a multiplicity of possible gears or gear steps can be provided by the transmission, without requiring a large number of components for this purpose.

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

Conveniently, the reverse gear can be actuated by means of a switching device on the minor axis. In this way, the transmission can be made more compact, since the switching device for the reverse gear stage with respect to their axial distance to optionally adjacent switching devices on the main axis closer to each other can be arranged by the respective positioning on different axes. Another advantage is that this allows a particularly reliable transmission of power and torque from one of the input shafts to the reverse gear stage when the transmission element of the reverse gear is firmly connected to the corresponding input shaft.

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 hybridization of the transmission.

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

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

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

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

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

Conveniently, transmission elements of at least two wheel planes on the minor axis are firmly connected to a countershaft designed as a hollow shaft. In this way, the transmission elements can be produced inexpensively together with the countershaft, in particular by a one-piece design of transmission elements together with the corresponding 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.

Advantageously, the N switching devices and the at least two wheel planes, in particular six wheel planes, are arranged such that at least six forward gears and at least two reverse gears can be represented by the transmission.

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

Advantageously, at least one wheel plane can be connected to at least two countershafts. In this way, the flexibility of the transmission and thus the number of possible connections or couplings by means of the at least one wheel plane is further increased without significantly increasing the space of the transmission.

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

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;

2a . 2 B . 2c . 2d Schaltmatrizen for a transmission according to the first embodiment of 1 ;

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

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

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

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

In 1 denotes reference numeral 1 a transmission in the form of a dual-clutch transmission. The dual-clutch transmission 1 has two load switching elements in the form of clutches K1, K2. By means of the double clutch K1, K2, the side of the drive AN can be coupled or connected to the side of the output AB for the transmission of force and torques. For this purpose, the first clutch K1 is connected to a first input shaft EW1 and the second clutch K2 is connected to a second input shaft EW2. The second input shaft EW2 is designed as a hollow shaft, whereas the first input shaft EW1 is formed as a solid shaft. The two input shafts EW1, EW2 are arranged coaxially and parallel to each other.

Furthermore, the transmission includes 1 a major axis 2 , the torque and power downstream of the drive AN starting from the two clutches K1 and K2 first a first gear plane I and a first switching element S1 and further comprises a second switching element S2, a second gear plane II, a sixth gear plane VI in the form of a reverse gear, a third gear plane III, a fifth switching element S5, a fourth gear plane IV, a sixth switching element S6, a seventh switching element S7 and a fifth gear plane V. Each of said gear planes I, II, III, IV, V and VI has transmission elements, in particular in shape of gears, which each with a shaft of the transmission 1 are connected.

Parallel to the main axis 2 is a minor axis 3 for a counterfeit 4 arranged. The counterpart 4 comprises a first countershaft VW1, which is designed as a solid shaft and two, arranged in a portion of the first countershaft VW1 and each designed as a hollow shaft countershaft VW2, VW3. The second countershaft VW2 and the third countershaft VW3 are each coaxial and parallel to the first countershaft VW1 arranged the radial outer side. On the radial outer side of the third countershaft VW3 transmission elements for the third wheel plane III and the fourth gear plane IV are arranged. On the radial outer side of the second countershaft VW2 a transmission element for the sixth gear plane VI is arranged. Between the minor axis 3 and the main axis 2 in the region of the sixth gear plane VI, which is designed in the form of a reverse gear, this has an intermediate ZR to reverse the direction of rotation, so that by means of the output shaft AW in the same direction of rotation of the input shafts EW1, EW2 allows a reverse direction of rotation to provide at least one reverse gear becomes. Starting from the side of the drive AN has the minor axis 3 First, the first wheel plane I and on the second wheel plane II, the sixth gear plane VI in the form of the reverse gear, a third switching element S3, a fourth switching element S4, the third wheel plane III, the fourth gear plane IV and the fifth gear plane V.

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

The third switching element S3 is on the minor axis 3 arranged and connected on the one hand with the first countershaft VW1, on the other hand with the second countershaft VW2 and, when actuated, establishes a connection for transmitting force and torques between the first countershaft VW1 and the second countershaft VW2. The second countershaft VW2 is arranged coaxially and parallel to the first countershaft VW1 on the radial outer side. On the second countershaft VW2 a transmission element is arranged, which with the intermediate gear ZR between the main axis 2 and minor axis 3 and a transmission element on the second input shaft EW2 cooperating to form the sixth gear plane VI in the form of the reverse gear stage. The fourth switching element S4 is on the minor axis 3 arranged and connected on the one hand with the first countershaft VW1, on the other hand with the third countershaft VW3 and, when actuated, establishes a connection for the transmission of force and torques between the first countershaft VW1 and the third countershaft VW3. The third countershaft VW3 is arranged coaxially and parallel to the first countershaft VW1 on the radial outer side. On the third countershaft VW3 transmission elements for the third wheel plane III and the fourth gear plane IV are arranged. The transmission element on the third countershaft VW3 for the third wheel plane III acts with a transmission element on a third hollow shaft H3 on the main axis 2 to form the third wheel plane III together. The transmission element on the third countershaft VW3 on the minor axis 3 for the fourth gear plane IV acts with a transmission element on a fourth hollow shaft H4 on the main axis 2 to form the fourth wheel plane IV together.

The fifth switching element S5 is on the main axis 2 arranged and connected on the one hand to the second input shaft EW2, on the other hand, with the third hollow shaft H3 and, when actuated, establishes a connection for transmitting force and torques between the second input shaft EW2 and the third hollow shaft H3. On the third hollow shaft H3, a transmission element is arranged, which cooperates with the corresponding transmission element on the third countershaft VW3 to form the third wheel plane III. The third hollow shaft H3 is arranged coaxially and parallel to the second input shaft EW2.

The sixth switching element S6 is on the main axis 2 arranged and connected on the one hand with the first input shaft EW1, on the other hand with the fourth hollow shaft H4 and, when actuated, establishes a connection for transmitting force and torques between the first input shaft EW1 and the fourth hollow shaft H4. The fourth hollow shaft H4 is arranged coaxially and parallel to the first input shaft EW1. On the fourth hollow shaft H4, a transmission element is arranged, which cooperates with the transmission element on the third countershaft VW3 to form the fourth gear plane IV. The seventh switching element S7 is on the main axis 2 arranged and connected on the one hand with the first input shaft EW1, on the other hand with the output shaft AW and, when actuated, establishes a connection for the transmission of force and torques between the first input shaft EW1 and the output shaft AW. On the output shaft AW a transmission element is arranged, which cooperates with a transmission element on the first countershaft VW1 to form the fifth gear plane V. The transmission elements of the fifth gear plane V are each firmly connected to their respective shafts. The fifth gear plane V is thus designed as output constant.

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

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

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

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

2a . 2 B . 2c and 2d show switching matrices for a transmission according to the first embodiment of 1 ,

In 2a 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 initially the six forward gears, designated by the numbers 1 to 6 and two reverse gears, designated R1 and R2. The released in the switching matrix entries, so for example in the forward gear 1 in the switching elements S2, S3, S4 and 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. An entry in the switching matrix provided with a cross designates a correspondingly actuated or closed switching element, that is, in the switching matrix in the forward gear stage 1 in the switching elements S1, S5 and S6.

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

In 2 B is another switching matrix for a transmission 1 according to 1 shown.

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

In 2c is another switching matrix for a transmission 1 according to 1 shown.

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

In 2d is another switching matrix for a transmission 1 according to 1 shown.

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

Thus, by means of the switching matrices according to the 2a . 2 B . 2c and 2d at least six forward gears and at least two reverse gears by means of the transmission 1 according to the 1 to provide.

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

In 3a is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 are at the transmission 1 according to 3a the first two wheel planes I and II with respect to their position along the main axis 2 or the minor axis 3 in the transmission 1 arranged reversed. The transmission element of the second wheel plane II on the main axis 2 is connected to the first hollow shaft H1 and coupled 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 connected to the second hollow shaft H2 and coupled by means of the first switching element S1 to the second input shaft EW2. The transmission elements of the first gear plane I and the second gear plane II on the minor axis 3 are like in 1 connected to the first countershaft VW1. As before, the first switching element S1 and the second switching element S2 are combined in the first switching device SE1 and actuated by means of the first switching element actuating device SB1.

Also, the transmission element of the first (I) and the second (II) gear plane can be fixedly connected to the second input shaft (EW2). Then, however, the corresponding transmission elements of the first (I) and second (II) gear plane via a switching element SE1 with the first countershaft (VW1) can be coupled.

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

In 3b is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 is at the transmission 1 according to 3b the third switching device SE3 instead of on the main axis 2 now on the minor axis 3 arranged. The fifth switching element S5 is now on the one hand to the third countershaft VW3, on the other hand connected to a third countershaft VW3 coaxial and parallel and formed as a hollow shaft fourth countershaft VW4 and provides a connection for transmitting force and torque between the third countershaft VW3 and the fourth countershaft VW4 ago. On the fourth countershaft VW4 is the transmission element of the third wheel plane III on the minor axis 3 arranged, which with the corresponding transmission element on the main axis 2 , which is now connected to the first input shaft EW2, cooperating to form the third wheel plane III. The sequence of switching elements and wheel planes along the minor axis 3 starting from the side of the drive AN is now as follows: first gear plane I, second gear plane II, sixth gear plane VI, third switching element S3, fourth switching element S4, third gear plane III, fifth switching element S5, fourth gear plane IV, and fifth gear plane V.

4 shows a transmission according to a fourth 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 for hybridization of the transmission 1 , The electric machine EM is connected to the transmission element on the minor axis via a shaft and a transmission element connected to the shaft 3 connected to the third wheel plane III. In this way, the electric machine EM can transmit power and torques to the transmission element of the third wheel plane III and thus to the third countershaft VW3 and further to the first countershaft VW1 and thus a hybridization of the transmission 1 according to 1 provide. The connection or coupling of the electric machine EM to the transmission 1 can also be done on the transmission elements of the fourth gear plane IV, that is to those transmission elements on the minor axis 3 which are arranged on the third countershaft VW3, which is designed as a hollow shaft.

Overall, the switching elements S1 to S7 in the transmission 1 according to the 1 to 4 Also referred to as coupling devices and as already explained above, in particular be designed as synchronizers. The switching element actuators SB1, SB2, SB3 and SB4 and the switching devices SE1, SE2, SE3 and SE4 can be designed as double synchronizers in the case of two switching elements or in the case of a switching element as a single synchronization. The transmission elements can in particular in the transmission 1 according to the 1 to 4 Such as fixed or loose with the respective waves, in particular with the input shafts EW1, EW2 and / or arranged with at least one of the countershafts VW1, VW2, VW3, VW4 and / or with at least one of the hollow shafts H1, H2, H3 or H4 or connected become. The transmission elements can be designed in particular in the form of gears, preferably as spur gears, so that the wheel planes I, II, III, IV, V, and VI represent spur gears. To provide various forward and reverse gears, so different translations, the spur gears, in particular their gears, correspondingly comprise different translations.

Furthermore, the first gear plane I, the second gear plane II, the third gear plane III and the fourth gear plane IV can be coupled by means of at least one switching element with one of the two input shafts EW1, EW2. The sixth gear plane VI can be coupled to the first countershaft VW1 by means of the third shift element S3. The first input shaft EW1, which is designed as a solid shaft, can be coupled to the output shaft AW by means of the seventh switching element S7. The transmission elements of the third wheel plane III and the fourth wheel plane IV on the minor axis 3 are fixedly connected to the first countershaft VW1 designed as a solid shaft and a third countershaft VW3 designed as a hollow shaft and can be coupled to the first countershaft VW1 designed as a solid shaft by means of the fourth shifting element S4. The transmission elements of the fifth gear plane V are firmly connected both to the output shaft AW and to the first countershaft VW1, which is designed as a solid shaft. The fifth gear plane V is thus designed as output constant.

In the transmission 1 according to the 1 to 4 the first shift element S1 of the first wheel plane I, the second shift element S2 of the second wheel plane II, the third shift element S3 of the sixth wheel plane VI, the fourth shift element S4 of the third and fourth wheel plane III, IV, the fifth shift element S5 of the third wheel plane III, the sixth switching element S6 of the fourth gear plane IV and the seventh switching element S7 are assigned to the two input shafts EW1, EW2 and the output shaft AW.

In summary, the present invention has the advantage that a reduction of the mechanical spread by winding the first forward gear is made possible. Another advantage is that the transmission has a good load shifting capability and a good hybridisability. One Another advantage is that at a total of six wheel planes I to VI at least six forward gears and at least two reverse gears are provided with only seven switching elements and / or only four actuators in the form of switching devices SE1 to SE4 and the switching element actuators SB1 to SB4 for actuation of the seven switching elements.

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

The gear 1 according to the 1 to 4 can be transformed functionally identical by different positions of the wheel planes and / or the switching elements. For this purpose, the switching elements, in particular designed as synchronizers, as mentioned above, the wheel planes or the waves are assigned. The switching matrices according to the 2a . 2 B . 2c and 2d Thus, do 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, H3, H4

hollow shaft

K1, K2

clutch

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

switching element

SB1, SB2, SB3, SB4

Switching element actuator

SE1, SE2, SE3, SE4

switching device

VW1, VW2, VW3, VW4

Countershaft

ZR

idler

AT

drive

FROM

output

EM

electric machine

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

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

Claims (17)

Transmission ( 1 ), in particular dual-clutch transmission, for a motor vehicle, comprising at least two partial transmissions, wherein each of the partial transmissions comprises at least one input shaft (EW1, EW2), and wherein an output shaft is arranged as the output shaft (AW) of both partial transmissions, wherein the at least one input shaft (EW1, EW2) on a main axis ( 2 ) and the output shaft (AW) on the main axis ( 2 ) or on one, in particular to the main axis ( 2 ) parallel, minor axis ( 3 ), and wherein a countershaft ( 4 ) is arranged with at least one countershaft (VW1, VW2, VW3, VW4), wherein the at least one countershaft (VW1, VW2, VW3, VW4) on the minor axis ( 3 ), and wherein at least one of the input shafts (EW1, EW2) by means of at least two wheel planes (I, II, III, IV, V, VI) and / or at least one switching element (S1, S2, S3, S4, S5, S6 , S7) is connectable to the output shaft (AW), characterized in that N switching devices (SE1, SE2, SE3, SE4) are arranged, wherein N is an integer greater than or equal to three, and that by means of the one side of the output (AB) adjacent switching device (SE4) the output shaft (AW) with at least one of the input shafts (EW1, EW2) is connectable and that each to the side of the output (AB) and to one side of the drive (AN) adjacent switching device (SE1, SE4) each comprise two switching elements (S1, S2, S6, S7) and that at least one of the N switching devices (SE3) on the minor axis ( 3 ) is arranged and that the at least one switching device (SE3) on the minor axis ( 3 ) comprises two switching elements (S3, S4). Transmission according to claim 1, characterized in that the number N is equal to four. Transmission according to one of claims 1-2, characterized in that a wheel plane (V) is designed as the output constant. Transmission according to one of claims 1-3, characterized in that the one switching device (SE1), which is arranged directly to the side of the drive (AN), on the main axis ( 2 ) is arranged. 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 two of the countershafts (VW1, VW2; VW1, VW3) are arranged coaxially with each other. Transmission according to one of claims 1-5, characterized in that the N switching means (SE1, SE2, SE3, SE4) symmetrically and / or periodically alternately with respect to their position along the main axis ( 2 ) and minor axis ( 3 ) are arranged between the side of the drive (AN) and the side of the output (AB). Transmission according to one of claims 1-6, characterized in that at least one of the input shafts (EW1, EW2) and / or at least one of the countershafts (VW1, VW2, VW3, VW4) 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 at least four wheel planes (I, II, III, IV) by means of at least one switching element (S1, S2, S5, S6) on the main axis ( 2 ) are connectable to at least one of the input shafts (EW1, EW2). Transmission according to one of claims 1-8, characterized in that at least one wheel plane (VI) is designed as a reverse gear. Transmission according to claim 9, characterized in that the reverse gear (VI) by means of a switching device (SE2) on the minor axis ( 3 ) is operable. Transmission according to one of claims 1-10, characterized in that an electric machine (EM) on at least one wheel plane (I, II, III, IV, V, VI) and / or on at least one countershaft (VW1, VW2, VW3, VW4) and / or on one of the input shafts (EW1, EW2) for the hybridization of the transmission ( 1 ) is arranged. Transmission according to claim 11, characterized in that the electric machine (EM) is arranged on at least one of the wheel planes (III, IV, VI) which are connected to a countershaft (VW2, VW3), designed as a hollow shaft. Transmission according to one of claims 1-12, characterized in that transmission elements of at least two wheel planes (III, IV) on the minor axis ( 3 ) are fixedly connected to a countershaft (VW2, VW3) designed as a hollow shaft. Transmission according to one of claims 1-13, characterized in that the N switching devices (SE1, SE2, SE3, SE4) and the at least two wheel planes (I, II, III, IV, V, VI), in particular six wheel planes (I, II, III, IV, V, VI), are arranged so that at least six forward gears and at least two reverse gears through the transmission ( 1 ) are representable. Transmission according to one of claims 1-14, characterized in that at least one wheel plane (III) with at least two countershafts (VW4, VW3, VW1) is connectable. A transmission according to any one of claims 1-15, characterized in that the number N is an even number and each N / 2 switching means (SE1, SE4; SE2, SE3) on the main axis ( 2 ) and on the minor axis ( 3 ) are arranged. Motor vehicle, in particular a passenger or a truck, with a transmission ( 1 ) according to any one of claims 1-16.

Images