DE102012202814A1 - Gear box e.g. dual clutch transmission for e.g. passenger car, has shift element of switch device that is connected with shift element of another switch device by hollow shaft, and switching arrangements arranged on major axis - Google Patents

Abstract

The gear box has a reduction gear (4) that is arranged with a countershaft (VW1,VW2) which is arranged on minor axis (3). An input shaft (EW1,EW2) is connected with a driven shaft by two wheel planes (I-VII) and shift element (S1-S8). Switching arrangements (SE1-SE4) are arranged on major axis, and shift element (S1) of main switch device is connected with shift element (S2) of auxiliary switch device by a hollow shaft (H12). The main switch device and auxiliary switch device are arranged adjacent to each other.

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 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 gear planes and / or at least one Switching element is connectable to the output shaft.

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

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

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

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

It is therefore an object of the present invention to provide a transmission for a motor vehicle which enables flexible power sharing and has improved power switching capability and hybridization capability. Moreover, it is an object of the present invention to provide a transmission for a motor vehicle, which is easier and cheaper to produce and at the same time allows reliable transmission of torque between the drive and output. Moreover, it is an object of the present invention to provide an alternative transmission for a motor vehicle.

The present invention solves the problems in a transmission, in particular dual-clutch transmission, for a motor vehicle comprising at least two partial transmissions, each of the partial transmissions comprises at least one input shaft, and wherein an output shaft is arranged as the output shaft of both partial transmissions, wherein the at least one input shaft on a main axis and the output shaft is arranged on the main axis or on a, in particular parallel to the main axis, minor axis, and wherein a countershaft with at least one Countershaft is arranged, wherein the at least one countershaft is arranged on the minor axis, and wherein at least one of the input shafts by means of at least two gear planes and / or by means of at least one switching element with the output shaft is connectable, characterized in that N switching means are arranged, wherein N is a whole Number is greater than or equal to 2 and that at least N-1 switching devices are arranged on the main axis, and that a first switching element of a first switching device with a second switching element of a second switching device by means of a, preferably designed as a hollow shaft, are connected, and that the first and second switching means are arranged adjacent to each other.

The invention solves the tasks also in a motor vehicle, in particular a passenger or a truck, by a transmission according to one of claims 1 to 15.

One of the advantages achieved here is that a vast majority of switching elements and / or switching devices, in particular all on the main axis, which acts as the central axis of the transmission, are arranged. This allows a comfortable and flexible power sharing by means of the Vorgeleges. Likewise, larger torques can be transmitted from the drive side to the output side of the transmission 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 an improved load shifting capability and a good hybridizability, since an electric machine can be coupled to the transmission in a simple 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, all of the N switching devices are arranged on the main axis. In this way, the power division can be further improved by using one or more countershafts. At the same time a number of switching devices for a desired number of possible forward gear ratios and reverse gear ratios is kept low.

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

Conveniently, the number N is equal to four. In this way, on the one hand a compact construction of the transmission can be achieved, on the other hand, a sufficient number of Switching devices for a variety of gears respectively gear ratios are represented by the transmission.

Advantageously, at least one of the input shafts and / or at least one of the countershafts is designed as a hollow shaft and the respective other shaft as a solid shaft. One of the advantages of forming a shaft as a hollow shaft is that it can be arranged coaxially with other shafts so that the most compact possible arrangement of the two input shafts and / or the countershafts can be achieved. If, for example, transmission elements are arranged on the respective shaft, the respective solid shaft or hollow shaft can be produced in one piece with the respective transmission elements, which further reduces the overall cost. A production of the respective shaft as a solid shaft is also particularly easy.

Conveniently, at least three, in particular at least four 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. The transmission can thus be made overall cost.

Advantageously, at least one wheel plane is designed as a reverse gear. By means of the at least one reverse gear stage, it is thus possible to reverse the direction of rotation of the output shaft relative to one of the input shafts, so that at least one reverse gear can be made available for a vehicle, which substantially increases the flexibility with regard to the use of the transmission in the various vehicles.

Conveniently, the reverse gear stage is actuated by means of at least one of the N switching devices, wherein the at least one switching device is arranged furthest downstream in the transmission in the region of the output side. One advantage here is, inter alia, that in the gearbox essentially the wheel stages without intermediate wheel are arranged in a first subarea and the reverse gear is endwise, that is to say in the region of the output in the gearbox, in a second area. This is also a simple production and improved accessibility, especially for the intermediate gear of the reverse gear, possible.

Advantageously, the at least one switching device is arranged on the minor axis and, in particular, the reverse gear stage is arranged on the output side of the at least one switching device. One of the advantages achieved with this is that the reverse gear is thus arranged directly at an output of the transmission on the output side, which allows a further improved accessibility, for example in the case of maintenance. On the other hand, a complete separation of gear planes without idler gear and the reverse gear is possible along the main and minor axis, which allows an even easier production of the transmission as a whole.

Conveniently, an electric machine is arranged on at least one wheel plane and / or on at least one countershaft and / or on one of the input shafts for hybridizing the transmission.

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

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

A second connection possibility of the electric machine to the transmission is possible by arranging a planetary gear in the transmission: To a first input shaft can via a corresponding switching element, in particular in the form of a clutch, an internal combustion engine be coupled. 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 interacts with the internal combustion engine and the electric machine so that the planet carrier engages 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 a countershaft, designed as a solid shaft. In this way, a particularly simple connection or coupling of the electric machine to the transmission and thus a reliable transmission of force and torque from the electric machine to the transmission, in particular to the output shaft, possible.

Conveniently, transmission elements of at least two, in particular at least three wheel planes on the minor axis with a countershaft designed as a hollow shaft, in particular fixed, connected. Transmission elements can be produced inexpensively in this way together with the corresponding countershaft, in particular by a one-piece design of transmission elements together with the countershaft. Likewise, a connection or coupling of an electrical machine to the transmission elements in a highly 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. At least six forward speeds and at least two reverse speeds provide a sufficient number of forward and reverse speeds for a variety of vehicles so that the transmission can be used in both passenger cars and trucks.

Conveniently, at least one wheel plane can be coupled to the two input shafts. In this way, a particularly reliable transmission of force and torque from the two input shafts by means of at least one wheel plane on the countershaft, more precisely on one of the countershafts, possible.

Advantageously, at least two wheel planes can be coupled to the output shaft. This allows more representable by the transmission gears at the same time compact overall space of the transmission.

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

It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

Preferred embodiments and embodiments of the invention are illustrated in the drawings and will be described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components or elements.

In each case show in a schematic form

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

2 a shift matrix 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 has two power shift elements in the form of clutches K1, K2. By means of the double clutch K1, K2, the side of the drive AN can be coupled to the side of the output AB for the transmission of force and torques. For this purpose, the first clutch K1 is connected to a first input shaft EW1 and the second clutch K2 is connected to a second input shaft EW2. The second input shaft EW2 is designed as a hollow shaft, whereas the first input shaft EW1 is formed as a solid shaft. The two input shafts EW1, EW2 are arranged parallel and coaxial with each other. Furthermore, the transmission includes 1 a major axis 2 , the torque and power downstream of the drive AN starting from the two clutches K1, K2 first a first gear plane I , a first switching element S1, a second switching element S2 and a second gear plane II and further comprises a third switching element S3, a fourth switching element S4, a third gear plane III , a fourth wheel plane IV , a fifth switching element S5, a sixth switching element S6, a fifth gear plane V , a sixth wheel plane VI , a seventh switching element S7, an eighth switching element S8 and a seventh gear plane VII , Each of the mentioned wheel planes I . II . III . IV . V . VI and VII each has a transmission element on the main and minor axis 2 . 3 on, which are each connected to a shaft of the transmission. The seventh wheel plane VII is designed as a reverse gear and in addition to the transmission elements comprises an intermediate gear ZR for reversing the direction of rotation.

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 coaxial and parallel 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 . VI and VII for transmitting force and torques between the main axis 2 and minor axis 3 arranged. The second to the first countershaft VW1 coaxial and parallel countershaft VW2 includes transmission elements for the wheel planes III . IV and V , Between the minor axis 3 and the main axis 2 indicates the seventh wheel plane VII in the form of the reverse gear, the intermediate gear ZR already mentioned above for reversing the direction of rotation, so that by means of an output shaft AW in the same direction of rotation of one of the input shafts EW1, EW2 an inverted direction of rotation is provided for providing at least one reverse gear.

The switching elements S1, S2, S3, S4, S5, S6, S7 and S8 will now be described below. When actuated, the first switching element S1 establishes a connection for transmitting force and torques between the second input shaft EW2 and a first hollow shaft H1, which is arranged on the outside of the second input shaft EW2 in parallel and coaxial therewith. On the first hollow shaft H1 is a transmission element for transmitting force and torques between the main axis 2 and the minor axis 3 arranged. This transmission element together with a correspondingly formed transmission element on the minor axis 3 forms the above-mentioned first wheel plane I ,

When actuated, the second switching element S2 establishes a connection for transmitting force and torques between the second input shaft EW2 and a second hollow shaft H12, which is arranged coaxially and parallel to the second input shaft EW2. On the second hollow shaft H12 also a transmission element is arranged, which with a transmission element on the first countershaft VW1 for transmitting force and torque between the two shafts, namely between the second input shaft EW2 on the main axis 2 and the first countershaft VW1 on the minor axis 3 , cooperates. The two transmission elements form the second wheel plane II , The two switching elements S1, S2 are combined to form a common first switching device SE1 and can be actuated by means of a common switching element actuation device SB1, ie can be brought into an open or a closed state.

The first input shaft EW1 is also connected to the third switching element S3. The third switching element S3 is further connected to the second hollow shaft H12 and, when actuated, establishes a connection for transmitting force and torques between the first input shaft EW1 and the second hollow shaft H12.

The fourth switching element S4 is connected to a third hollow shaft H2 and, when actuated, establishes a connection for transmitting force and torques between the first input shaft EW1 and the third hollow shaft H2, which is arranged coaxially and parallel to the first input shaft EW1. On the outside of the third hollow shaft H2, a transmission element is arranged, which with a transmission element on the second countershaft VW2 to form the third wheel III interacts.

The fifth switching element S5 is connected on the one hand to the first input shaft EW1, on the other hand to a fourth hollow shaft H3, which is arranged coaxially and parallel to the first input shaft EW1. Upon actuation of the fifth switching element S5, a connection for transmitting force and torques between the first input shaft EW1 and the fourth hollow shaft H3 is made possible. On the outside of the fourth hollow shaft H3, a transmission element is arranged, which with a transmission element on the second countershaft VW2 on the minor axis 3 to form the fourth wheel IV interacts.

The sixth switching element S6 is connected on the one hand to the first input shaft EW1, on the other hand to the output shaft AW. Upon actuation of the sixth switching element S6, a connection is thus made possible 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 further arranged, which with a transmission element on the second countershaft VW2 to form the fifth wheel V interacts.

The seventh switching element S7 is connected on the one hand to the output shaft AW, on the other hand to a fifth hollow shaft H4a arranged coaxially and parallel to the output shaft AW. Upon actuation of the seventh switching element S7, a connection for the transmission of force and torque between the output shaft AW and the fifth hollow shaft H4a is produced. On the outside of the fifth hollow shaft H4a, a transmission element is arranged, which with a transmission element on the first countershaft VW1 on the minor axis 3 to form the sixth wheel VI interacts.

The eighth switching element S8 is connected on the one hand to the output shaft AW, on the other hand to a coaxial and parallel to the output shaft AW arranged sixth hollow shaft H4b. Upon actuation of the eighth switching element S8, a connection for transmitting force and torques between the output shaft AW and the sixth hollow shaft H4b is produced. On the outside of the sixth hollow shaft H4b, a transmission element is arranged, which with an intermediate ZR and a transmission element on the first countershaft VW1 on the minor axis 3 cooperates to form the reverse gear.

Overall, the third switching element S3 and the fourth switching element S4 is combined in a second switching device SE2, which are actuated by means of a common second switching element actuator 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 designed as double synchronizers.

The transmission elements can be arranged either fixed or loose with the respective shaft, in particular with the input shafts EW1, EW2 and / or with at least one of the countershafts VW1, VW2 and / or with the hollow shafts H1, H12, H2, H3, H4a, H4b or get 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, wherein the first input shaft EW1 is formed as a solid shaft and the second input shaft EW2 coaxial and arranged parallel to this and is formed as a hollow shaft. Both input shafts EW1, EW2 are on the main axis 2 arranged. On the to the main axis 2 parallel minor axis 3 are two countershafts VW1, VW2 arranged, one formed as a solid shaft and the other coaxial with this arranged and designed as a hollow shaft. Furthermore, an 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 seven wheel levels I . II . III . IV . V . VI and VII , where the wheel plane VII is designed as a reverse gear. All wheel levels I to VII are designed in particular as spur gears with discrete ratios. Per wheel level I . II . III . IV . V . VI and VII each 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, therefore 15 Transmission elements, in particular in the form of gears arranged.

The wheel levels I . II . III . IV can be coupled to one of the input shafts EW1, EW2. By means of the sixth switching element S6, the first input shaft EW1 can be coupled to the output shaft AW. A transmission element of the fifth wheel plane V is firmly connected to the output shaft AW. The Transmission elements of the wheel planes III . IV and 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 means of the embodiment of the 1 through the transmission 1 at least six forward gears and at least two reverse gears are provided.

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

In 2 is a switching matrix for a transmission 1 according to 1 shown. Horizontal each column for each switching element S1 to S8 and for the two clutches K1 and K2 are shown. Perpendicular to this down are first the six forward gear stages, indicated by the numbers 1 to 6 and two reverse gear stages, designated R1 and R2. The released in the switching matrix entries, so for example in the forward gear in the switching elements S2, S4, S6, S7 and S8 indicate that the corresponding switching element is open, ie that the switching element in this case no forces or no torque from the to the switching element connected respective waves transmits. An entry in the switching matrix provided with a cross designates a corresponding closed switching element, that is, for example, in the case of the first forward gear step, the switching elements S1, S3 and S5. When closed, the switching element transmits forces or torques from the respective shafts connected to the corresponding switching elements.

To the first gear by means of the transmission 1 according to 2 represent the clutch K1 are open and the clutch K2 closed and the switching elements S2, S4, S6, S7, S8 open and the switching elements S1, S3, S5 closed. To represent the second gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S4, S6, S7, S8 opened and the switching element S5 closed. To represent the third gear, the clutch K1 are opened and the clutch K2 closed and the switching elements S2, S3, S4, S5, S6, S8 opened and the switching elements S1 and S7 closed. To represent the fourth gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S3, S5, S6, S7, S8 opened and the switching element S4 closed. To illustrate the fifth gear, the clutch K1 are opened and the clutch K2 closed and the switching elements S1, S3, S4, S5, S6, S8 open and the switching elements S2 and S7 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, S7, S8 opened and the switching element S6 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 S2, S3, S4, S5, S6, S7 are opened and the shifting elements S1 and S8 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, S3, S4, S5, S6, S7 are opened and the shifting elements S2 and S8 are closed.

Overall, in this way by means of the transmission 1 according to 1 and the switching matrix according to 2 six forward gears and two reverse gears representable.

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 sixth and seventh wheel plane VI . VII in terms of their axial position along the major axis 2 and minor axis 3 arranged reversed. The eighth switching element S8 for the seventh wheel plane VII is now connected on the one hand to the output shaft AW, on the other hand to the fifth hollow shaft H4a. The eighth switching element S8 thus establishes a connection for the transmission of force and torques between the output shaft AW and the fifth hollow shaft H4a when actuated. A partial order of the wheel planes and the shift elements on the output shaft AW is thus as follows: fifth gear plane V seventh wheel plane VII , eighth switching element S8, seventh switching element S7, sixth wheel plane VI , The seventh switching element S7 is now connected on the one hand to the output shaft AW, on the other hand to the sixth hollow shaft H4b and, when actuated, establishes a connection for transmitting force and torques between the output shaft AW and the sixth hollow shaft H4b. The sixth wheel plane VI is thus by means of a transmission element on the sixth hollow shaft H4b and a corresponding transmission element on the first countershaft VW1 on the minor axis 3 educated.

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 fourth switching device SE4 instead of on the main axis 2 on the minor axis 3 arranged. The seventh switching element S7 is now connected on the one hand to the first countershaft VW1, on the other hand with a coaxial with the first Countershaft VW1 arranged and designed as a hollow shaft third countershaft VW3a. When actuated, the seventh switching element S7 thus establishes a connection for transmission of force and torques between the first countershaft VW1 and the third countershaft VW3a. On the outside of the third countershaft VW3a, a transmission element is arranged, which with a transmission element on the output shaft AW on the main axis 2 for the formation of the sixth wheel plane VI interacts. The eighth shifting element S8 is connected, on the one hand, to the first countershaft VW1 and, on the other hand, to a fourth countershaft VW3b arranged coaxially with the first countershaft VW1 and designed as a hollow shaft. The eighth switching element S8 thus establishes a connection for transmitting force and torques between the first countershaft VW1 and the fourth countershaft VW3b when actuated. On the outside of the fourth countershaft VW3b a transmission element is arranged, which with an intermediate ZR and a transmission element on the output shaft AW on the main axis 2 to form the seventh wheel VII cooperates in the form of the reverse gear.

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. The electric machine EM is connected via a transmission element to the transmission element of the first wheel plane I , which is arranged on the first countershaft VW1, for hybridizing the transmission 1 connected. The connection of the electric machine EM to the gearbox 1 Also, especially at the wheel levels II . VI and VII take place, ie at the transmission elements of the corresponding wheel planes, which are arranged on the first countershaft VW1.

Overall, the switching elements S1 to S8 (N = 4) in the transmission 1 according to the 1 to 4 Also referred to as coupling devices and be designed in particular as synchronizers. In this case, the first 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 second wheel plane II , the fourth switching element S4 of the third wheel plane III , the fifth switching element S5 of the fourth gear plane IV , the sixth switching element S6 the input shafts EW1, EW2 and the output shaft AW, the seventh switching element S7 of the sixth wheel plane VI and the eighth switching element S8 of the seventh wheel plane VII assigned in the form of the reverse gear.

In summary, the present invention offers several advantages: One of the advantages is that all the switching devices on the main axis, which acts as the central axis of the transmission, are arranged. In this way, a flexible and comfortable power sharing by using one or more countershafts is possible. Likewise, the invention offers the advantage of having seven wheel planes and at least eight shift elements to provide at least six forward and two reverse speeds. Next, the invention offers the advantage that only four switching element actuators must be provided for the operation of eight switching elements. In addition, the invention offers the advantage that a reduction of the mechanical spread is made possible by winding the first forward gear. The present invention further provides, inter alia, the advantage of good power shifting capability and good hybridization capability when the transmission is to be deployed in a hybrid vehicle.

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

The embodiments of the transmission according to the 1 - 4 can be combined, for example, the embodiments of 3a and 3b ,

The gear 1 according to the 1 to 4 can also be reshaped functionally 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 matrix according to the 2 thus changes by a rearrangement of the wheel planes and / or the switching elements in the transmission 1 Not.

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, H12, H2, H3, H4a, H4b

hollow shaft

K1, K2

clutch

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

switching element

SB1, SB2, SB3, SB4

Switching element actuator

SE1, SE2, SE3, SE4

switching device

VW1, VW2, VW3a, VW3b

Countershaft

ZR

idler

AT

drive

FROM

output

EM

electric machine

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• DE 102006054281 A1 [0005]
• DE 102010030569 A1 [0026]

Claims (16)

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, VW3a, VW3b), wherein the at least one countershaft (VW1, VW2, VW3a, VW3b) on the minor axis ( 3 ) is arranged, and wherein at least one of the input shafts (EW1, EW2) by means of at least two wheel planes ( I . II . III . IV . V . VI . 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 N switching means (SE1, SE2, SE3, SE4) are arranged , where N is an integer greater than or equal to two, and that at least N-1 switching devices (SE1, SE2, SE3) on the main axis ( 2 are arranged, and that a first switching element (S2) of a first switching device (SE1) with a second switching element (S3) of a second switching device (SE2) by means of a preferably formed as a hollow shaft (H12) are connected and that the first and the second switching device (SE1, SE2) are arranged adjacent to each other. Transmission according to claim 1, characterized in that all of the N switching devices (SE1, SE2, SE3, SE4) on the main axis ( 2 ) are arranged. 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 a second countershaft (VW2, VW3a, VW3b) are arranged coaxially to the at least one countershaft (VW1). Transmission according to one of claims 1-3, characterized in that the number N is equal to four. Transmission according to one of claims 1-4, characterized in that at least one of the input shafts (EW1, EW2) and / or at least one of the countershafts (VW1, VW2, VW3a, VW3b) is designed as a hollow shaft and the respective other shaft as a solid shaft. Transmission according to one of claims 1-5, characterized in that at least three, in particular at least four wheel planes ( I . II . III . IV ) can be connected to at least one of the input shafts (EW1, EW2) by means of at least one switching element (S1, S2, S3, S4, S5). Transmission according to one of claims 1-6, characterized in that at least one wheel plane ( VII ) is designed as a reverse gear. Transmission according to claim 7, characterized in that the reverse gear ( VII ) by means of at least one of the N switching devices (SE1, SE2, SE3, SE4), wherein the at least one switching device (SE4) furthest downstream in the transmission ( 1 ) is arranged in the region of the output side (AB). Transmission according to one of claims 7-8, characterized in that the at least one switching device (SE4) on the minor axis ( 3 ) and in particular that the reverse gear ( VII ) on the output side (AB) facing side of the at least one switching device (SE4) is arranged. Transmission according to one of claims 1-9, characterized in that an electric machine (EM) on at least one wheel plane ( I . II . III . IV . V . VI . VII ) and / or on at least one countershaft (VW1, VW2, VW3a, VW3b) and / or on one of the input shafts (EW1, EW2) for hybridizing the transmission ( 1 ) is arranged. Transmission according to claim 10, characterized in that the electric machine (EM) on at least one of the wheel planes ( I . II . VI . VII ), which are connected to a countershaft (VW1), formed as a solid shaft. Transmission according to one of claims 1-11, characterized in that transmission elements of at least two, in particular at least three wheel planes ( III . IV . V ) on the minor axis ( 3 ) are connected to a countershaft (VW2, VW3a, VW3b) designed as a hollow shaft, in particular fixed. Transmission according to one of claims 1-12, characterized in that the N switching devices (SE1, SE2, SE3, SE4) and the at least two wheel planes ( I . II . III . IV . V . VI . VII ) are arranged so that at least six forward gears and at least two reverse gears through the transmission ( 1 ) are representable. Transmission according to one of claims 1-13, characterized in that at least one wheel plane ( II ) can be coupled to the two input shafts (EW1, EW2). Transmission according to one of claims 1-14, characterized in that at least two wheel planes ( VI . VII ) can be coupled to the output shaft. Motor vehicle, in particular a passenger or a truck, with a transmission ( 1 ) according to any one of claims 1-15.

Images