DE102012202651A1 - Transmission e.g. dual clutch transmission for motor car, has wheel planes which are arranged on major axis, and jackshafts trained as sleeve shafts are arranged on minor axis so that one wheel plane is arranged adjacent to other plane - Google Patents

Abstract

The transmission (1) has an upper switching device (SE1) which is arranged on the main axis (2) and the lower switching device (SE2) is arranged on minor axis (3). One of the three switching devices (SE1-SE3) comprises two switching elements and another of the three switching devices comprises a single switching element. One of the wheel planes (I,II,III,IV,V,VI) of transmission elements are arranged on the major axis, and the jackshafts (VW2) trained as sleeve shafts (H2,H3) are arranged on the minor axis. The wheel plane (III) is arranged directly adjacent to the wheel plane (II).

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 at least one switching device is arranged on the main axis and at least one switching device is arranged on the minor axis, one of the at least three switching devices comprises two switching elements and another of the at least three switching devices comprises a single switching element, and wherein one of the at least two wheel planes has transmission elements on the main axis and on has the minor axis, which are each connected to a shaft formed as a hollow shaft and wherein the one gear plane is arranged directly adjacent to at least one further gear plane.

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 21.

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 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 one wheel plane can be actuated by means of the switching device, with which at least one of the input shafts can be connected to the output shaft. One of the advantages achieved is that thus the switching device is arranged at the torque downstream end of the at least one input shaft, so that a short path of the torque flow over the one gear plane on the countershaft and on the output shaft allows and thus a reliable force and torque transmission of the at least one input shaft is ultimately reached on the output shaft.

Advantageously, 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.

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

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

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, 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.

Expediently, at least two, in particular at least three wheel planes can be connected to at least one of the input shafts by means of at least one switching element on the main shaft. 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 stage is actuated by means of at least one of the N switching devices, wherein the at least one switching device is arranged adjacent to the side of the drive in the transmission. In this way, a direct and extremely reliable transmission of power and torque from one of the input shafts to the reverse gear stage is possible.

Advantageously, the reverse gear is arranged as a first gear plane downstream of the drive side. One of the advantages achieved with this is that the reverse gear stage can interact directly with one of the input shafts, thus enabling extremely reliable transmission of power and torque by means of the reverse gear to the countershaft and further to the output shaft. In addition, the drive-side arrangement of the reverse gear has the advantage that it is easier to access during maintenance.

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

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

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

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 arrangement or coupling of the electric machine to the transmission and thus a reliable transmission of force and torque from the electric machine to the transmission, in particular ultimately to the output shaft, possible.

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 are arranged so that at least six forward gears and at least three 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.

Conveniently, at least two wheel planes can be coupled to the output shaft. In this way, the flexibility of the transmission and thus the number of possible connections or couplings between the three countershafts and the output shaft is further increased, without significantly increasing the space of the transmission.

Advantageously, the reverse gear is arranged between two switching elements. The advantage thus achieved is that thus, for example, when the reverse gear is actuated by the two switching elements, so if one of the switching elements on the main axis and the other switching element is arranged on the minor axis, the reverse gear in each case completely from the input, countershaft and output shaft can be decoupled, the reverse gear so can be made completely load-free, which reduces the overall wear of transmission elements of the reverse gear.

Conveniently, the two switching elements are arranged on the minor axis. In this way, the transmission element of the reverse gear on one of the input shafts is fixedly arranged with this, thus enabling a very reliable transmission of power and torque from one of the input shafts on the reverse gear stage to the countershaft. In addition, several reverse gears can be represented by the transmission in this way.

Advantageously, two switching elements for actuating at least one gear plane are each arranged downstream of the at least one gear plane. Although such an arrangement generally requires a larger distance between the main axis and the minor axis, the space for the adjacent to the at least one wheel plane wheel planes can thereby be significantly reduced.

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

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

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

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

In each case show in a schematic form

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

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

3a . 3b Schaltmatrizen for a transmission according to the first and second embodiments of the 1 and the 2 ;

4a a transmission according to a third embodiment of the present invention;

4b a transmission according to a fourth embodiment of the present invention;

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

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

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

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

7b a transmission according to a ninth embodiment of the present invention;

7c a transmission according to a tenth embodiment of the present invention; such as

8th a transmission according to an eleventh 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 sixth gear plane VI in the form of a reverse gear, a second gear plane II , a third wheel plane III , a fourth switching element S4, 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 the mentioned wheel planes I . II . III . IV . V and VI has transmission elements, in particular in the form of gears, which each with a shaft of the transmission 1 are connected. The first wheel plane I , the third wheel plane III and the sixth wheel plane VI are coupled by means of a respective switching element of the switching elements S1, S2 and S4 to one of the input shafts EW1, EW2. The fourth wheel plane IV is by means of the sixth switching element S6 and the fifth gear plane V by means of the seventh switching element S7 to an output shaft AW of the transmission 1 can be coupled or connected to this. The output shaft AW is designed as a solid shaft and on the main axis 2 arranged parallel to the two input shafts EW1, EW2. The first input shaft EW1, which is designed as a solid shaft, can be coupled to the output shaft AW by means of the fifth switching element S5.

Parallel to the main axis 2 is a minor axis 3 for a counterfeit 4 arranged. The counterpart 4 comprises a first countershaft VW1, which is designed as a solid shaft and a thereto, arranged in a portion of the first countershaft VW1 and formed as a hollow shaft second countershaft VW2. The second countershaft VW2 is arranged coaxially and parallel to the first countershaft VW1 on the radial outer side. On the radial outer side of the second countershaft VW2 are transmission elements for the second wheel plane II and the third wheel plane III arranged. Between the minor axis 3 and the main axis 2 indicates the sixth wheel plane VI formed in the form of a reverse gear, an intermediate ZR for reversing the direction of rotation, so that by means of the output shaft AW in the same direction of rotation of the input shafts EW1, EW2 a reverse direction of rotation is provided for providing at least one reverse gear. Starting from the side of the drive AN has the minor axis 3 first the first wheel plane I on and on the sixth wheel plane VI , a third switching element S3, the second wheel plane II , the third wheel plane III , the fourth wheel plane IV , as well as the fifth wheel 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. On the first hollow shaft H1 a transmission element is arranged, which with a transmission element on the first countershaft VW1 to form the first gear plane I interacts. 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 with an intermediate ZR between the main axis 2 and minor axis 3 and a transmission element on the first countershaft VW1 to form the sixth gear plane VI cooperates in the form of the reverse gear.

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 a second to the first countershaft VW1 coaxial and parallel and formed as a hollow shaft countershaft VW2 and provides upon actuation a connection for the transmission of force and torque between the first countershaft VW1 and the second countershaft VW2 ago , On the second countershaft VW2 a transmission element is arranged, which with a transmission element on the second input shaft EW2 to form the second gear plane II interacts. The fourth switching element S4 is on the main axis 2 arranged and connected on the one hand with the first input shaft EW1, on the other hand with a third hollow shaft H3. The third hollow shaft H3 is arranged coaxially and parallel to the first input shaft EW1. The fourth switching element S4, when actuated, establishes a connection for transmission of force and torques between the first input shaft EW1 and the third hollow shaft H3. On the third hollow shaft H3, a transmission element is arranged, which with a transmission element on the second countershaft VW2 to form the third gear plane III interacts.

The fifth switching element S5 is on the one hand with the first input shaft EW1, on the other hand with the Connected output shaft AW and, when actuated, establishes a connection for transmission of force and torque between the first input shaft EW1 and the output shaft AW. The sixth switching element S6 is connected on the one hand to the output shaft AW, on the other hand connected to a coaxial to the output shaft AW and arranged in parallel fourth hollow shaft H4. The sixth switching element S6, when actuated, establishes a connection for transmission of force and torques between the output shaft AW and the fourth hollow shaft H4. On the fourth hollow shaft H4, a transmission element is arranged, which with a transmission element on the first countershaft VW1 on the minor axis 3 to form the fourth wheel plane IV interacts.

The seventh switching element S7 is connected on the one hand to the output shaft AW, on the other hand to a coaxial to the output shaft AW and arranged fifth hollow shaft H5. The seventh switching element S7, when actuated, establishes a connection for the transmission of force and torques between the output shaft AW and the fifth hollow shaft H5. On the fifth hollow shaft H5, a transmission element is arranged, which with a transmission element on the first countershaft VW1 to form the fifth gear plane V interacts.

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

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

Overall, the gearbox has 1 according to 1 two input shafts EW1, EW2 on the main axis 2 on, one formed as a solid shaft and the other coaxial and parallel to this and formed as a hollow shaft. On the to the main axis 2 parallel minor axis 3 are two countershafts VW1, VW2 arranged, wherein the first countershaft VW1 is arranged as a solid shaft and the second countershaft VW2 coaxial and parallel to this and is designed 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 levels I . II . III . IV . V and VI , where the sixth wheel plane VI is designed as a reverse gear. All wheel levels I to VI are designed in particular as spur gears with discrete ratios. Per wheel level 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 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 three reverse gears are provided.

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

In 2 is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 is at the transmission 1 according to 2 the second switching element S2 instead of in the first switching device SE1 on the main axis 2 now in the second switching device SE2 on the minor axis 3 arranged. The second switching element S2 on the minor axis 3 is now on the one hand connected to the first countershaft VW1, on the other hand with a coaxial and parallel to this and designed as a hollow shaft third countershaft VW3. On the third countershaft VW3, a transmission element is arranged, which with the intermediate gear ZR and a transmission element on the second input shaft EW2 to form the sixth gear plane VI cooperates in the form of the reverse gear. The second switching element S2 and the third switching element S3 are combined in the second switching device SE2 and actuated by means of the second switching element actuation device SB2.

3a . 3b show switching matrices for a transmission according to the first and second embodiments of the 1 and the 2 ,

In 3a is a switching matrix for a transmission 1 according to 1 or 2 shown. Horizontal are columns for each switching element S1 to S7 and for the two clutches K1 and K2 shown. Perpendicular to this down are initially the six forward gears, called with the numbers 1 to 6 represented as well as three reverse gear stages, designated R1 to R3. The released in the switching matrix entries, so for example in the forward gear 1 in the switching elements S2, S3, S5 and S6 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, S4 and S7.

To the first gear by means of the transmission 1 according to 1 or 2 represent, the clutch K1 are closed and the clutch K2 open and the switching element S2, S3, S5 and S6 open and the switching elements S1, S4 and S7 closed. To illustrate the second gear, the clutch K1 are open and the clutch K2 closed and the switching elements S2, S3, S4, S5, S6 open and the switching elements S1 and S7 closed. To represent the third gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S5, S6 open and the switching elements S3, S4 and S7 closed. To illustrate the fourth gear, the clutch K1 are open and the clutch K2 closed and the switching elements S1, S2, S4, S5, S6 open and the switching elements S3 and S7 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, S6, S7 open and the switching element S5 closed. To represent the sixth gear, the clutch K1 are open and the clutch K2 closed and the switching elements S1, S2, S4, S5 and S7 open and the switching elements S3 and S6 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, S3, S5 and S6 are opened and the shifting elements S2, S4 and S7 are closed. In order to represent the second reverse gear R2, the clutch K1 are opened and the clutch K2 is closed and the shifting elements S1, S3, S4, S5 and S7 are opened and the shifting elements S2 and S6 are closed. To represent the third reverse gear R3, the clutch K1 are opened and the clutch K2 is closed and the shift elements S1, S3, S4, S5, S6 open and the shift elements S2 and S7 closed. Thus, by means of the switching matrix according to 3a at least six forward gears and at least three reverse gears by means of the transmission 1 according to the 1 or the 2 to provide.

In 3b is another switching matrix for a transmission 1 according to the 1 or the 2 shown. To the first gear by means of the transmission 1 according to 1 or 2 represent the clutch K1 are closed and the clutch K2 open and the switching elements S2, S3, S5 and S6 open and the switching elements S1, S4 and S7 closed. To illustrate the second gear, the clutch K1 are open and the clutch K2 closed and the switching elements S2, S3, S4, S5, S6 open and the switching elements S1 and S7 closed. To represent the third gear, the clutch K1 are closed and the clutch K2 is opened and the switching elements S1, S2, S5, S6 open and the switching elements S3, S4 and S7 closed. To illustrate the fourth gear, the clutch K1 are open and the clutch K2 closed and the switching elements S1, S2, S4, S5, S6 open and the switching elements S3 and S7 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, S6, S7 open and the switching element S5 closed. To represent the sixth gear, the clutch K1 are opened and the clutch K2 is closed and the switching elements S2, S3, S4, S5 and S7 open and the switching elements S1 and S6 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, S3, S5 and S6 are opened and the shifting elements S2, S4 and S7 are closed. In order to represent the second reverse gear R2, the clutch K1 are opened and the clutch K2 is closed and the shifting elements S1, S3, S4, S5 and S7 are opened and the shifting elements S2 and S6 are closed. To represent the third reverse gear, the clutch K1 are opened and the clutch K2 closed and the switching elements S1, S3, S4, S5, S6 open and the switching elements S2 and S7 closed. Thus, by means of the switching matrix according to 3b at least six forward gears and at least three reverse gears by means of the transmission 1 according to the 1 or the 2 to provide.

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

In 4a is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 are at the transmission 1 according to 4a the two wheel planes I and IV in terms of their position along the main axis 2 or the minor axis 3 arranged reversed. The transmission element of the sixth wheel plane VI on the main axis 2 is now 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 sixth wheel plane VI on the minor axis 3 is now connected to the first countershaft VW1. As before, between the two transmission elements of the sixth wheel plane VI between the main axis 2 and the minor axis 3 arranged the idler ZR. The first switching element S1 is now connected on the one hand to the second input shaft EW2, on the other hand to the second hollow shaft H2 and, when actuated, establishes a connection for transmitting force and torques between the second hollow shaft H2 and the second input shaft EW2. The transmission element of the first wheel plane I on the minor axis 3 is now connected to the first countershaft VW1.

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

In 4b is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 are at the transmission 1 according to 4b the two wheel planes IV and V in terms of their position along the main axis 2 or minor axis 3 arranged reversed. The transmission element of the fifth wheel plane V is now connected to the fourth hollow shaft H4 and coupled by means of the seventh switching element S7 with the output shaft. The sixth switching element S6 is now in contrast to the transmission 1 according to 1 connected to the fifth hollow shaft H5 instead of the fourth hollow shaft H4. The transmission element on the fifth hollow shaft H5 interacts with the corresponding transmission element on the first countershaft VW1 on the minor axis 3 to form the fourth wheel plane IV together. Furthermore, the sixth switching element S6 and the seventh switching element S7 form the fourth switching device SE4 and can also be actuated by means of the fourth switching element actuating device SB4.

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

In 5a is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 is at the transmission 1 according to 5a the first switching device SE1 instead of on the main axis 2 on the minor axis 3 arranged. The first switching element S1 is now connected on the one hand to the first countershaft VW1, on the other hand with a third countershaft VW3. The third countershaft VW3 is arranged parallel and coaxial with the first countershaft VW1 and designed as a hollow shaft. On the third countershaft VW3, a transmission element is arranged, which with a transmission element on the second input shaft EW2 on the main axis 2 to form the first wheel plane I interacts. The second switching element S2 is now connected on the one hand to the first countershaft VW1, on the other hand with a fourth countershaft VW4. The fourth countershaft VW4 is arranged parallel and coaxial with the first countershaft VW1 and formed as a hollow shaft. On the fourth countershaft VW4 a transmission element is arranged, which with a transmission element on the second input shaft EW2 and the intermediate gear ZR to form the sixth gear plane VI interacts. The first switching element S1 and the second switching element S2 can be actuated by means of the first switching element actuating device SB1 and combined in the first switching device SE1.

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

In 5b is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 is at the transmission 1 according to 5b the fourth switching device SE4 instead of on the main axis 2 now on the minor axis 3 arranged. The sixth switching element S6 is now connected on the one hand to the first countershaft VW1, on the other hand to a third countershaft VW3. The third countershaft VW3 is arranged parallel and coaxial with the first countershaft VW1 and designed as a hollow shaft. On the third countershaft VW3 a transmission element is arranged, which with a transmission element on the output shaft AW to form the fourth gear plane IV interacts. The seventh switching element S7 is now connected on the one hand to the first countershaft VW1, on the other hand to a fourth countershaft VW4. The fourth countershaft VW4 is arranged parallel and coaxial with the first countershaft VW1 and formed as a hollow shaft. On the fourth countershaft VW4 a transmission element is arranged, which with a transmission element on the output shaft AW to form the fifth gear plane V interacts. The sixth switching element S6 and the seventh switching element S7 can be actuated by means of the fourth switching element actuating device SB4 and combined in the fourth switching device SE4.

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

In 6 is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 is at the transmission 1 according to 6 the second switching device SE2 between the transmission elements of the wheel planes III and IV on the minor axis 3 arranged instead of between the transmission elements of the wheel planes VI and II , The sequence of switching elements and wheel planes along the minor axis 3 is now as follows: first wheel plane I, sixth wheel plane VI , second wheel plane II , third wheel plane III , third switching element S3, fourth gear plane IV and fifth wheel plane V ,

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

In 7a is essentially a transmission 1 according to 2 shown. Unlike the gearbox 1 according to 2 are at the transmission 1 according to 7 the two wheel planes IV and V in terms of their position along the main axis 2 or minor axis 3 arranged reversed. The transmission element of the fifth wheel plane V is now connected to the third hollow shaft H3 and coupled by means of the seventh switching element S7 with the output shaft AW. The sixth switching element S6 is now in contrast to the transmission 1 according to 2 connected to the fourth hollow shaft H4 instead of the third hollow shaft H3. The transmission element of the fourth hollow shaft H4 interacts with the transmission element on the first countershaft VW1 to form the fourth gear plane IV together. The transmission element on the third hollow shaft H3 interacts with the transmission element on the first countershaft VW1 to form the fifth gear plane V together. Furthermore, the sixth switching element S6 and the seventh switching element S7 form the fourth switching device SE4 and can also be actuated by means of the fourth switching element actuating device SB4.

7b shows a transmission according to a ninth embodiment of the present invention.

In 7b is essentially a transmission 1 according to 2 shown. Unlike gearbox 1 according to 2 is at the transmission 1 according to 7b the first switching device SE1 instead of on the main axis 2 now on the minor axis 3 arranged. The first switching element S1 is now connected on the one hand to the first countershaft VW1, on the other hand with a fourth countershaft VW4. The fourth countershaft VW4 is arranged coaxially and parallel to the first countershaft VW1 and formed as a hollow shaft. On the fourth countershaft VW4 a transmission element is arranged, which with a transmission element on the second input shaft EW2 to form the first gear plane I interacts. The sequence of wheel planes and switching elements on the minor axis 3 is now as follows: first wheel plane I , first switching element S1, sixth wheel plane VI second switching element S2 third switching element S3, second gear plane II , third wheel plane III , fourth wheel plane IV , and fifth wheel plane V ,

7c shows a transmission according to a tenth embodiment of the present invention.

In 7c is essentially a transmission 1 according to 2 shown. Unlike the gearbox 1 according to 2 is at the transmission 1 according to 7c the fourth switching device SE4 instead of on the main axis 2 now on the minor axis 3 arranged. The sixth shifting element S6 is now connected to a fourth countershaft VW4 on the one hand and to the first countershaft VW1 on the other hand. The fourth countershaft VW4 is arranged coaxially and parallel to the first countershaft VW1 and formed as a hollow shaft. The sixth switching element S6, when actuated, establishes a connection for transmitting power and torques between the first countershaft VW1 and the fourth countershaft VW4. On the fourth countershaft VW4 a transmission element is arranged, which with a transmission element on the output shaft AW to form the fourth gear plane IV interacts. The seventh switching element S7 is now in contrast to the transmission 1 according to 2 on the one hand with the first countershaft VW1, on the other hand connected to a fifth countershaft VW5. The fifth countershaft VW5 is formed as a hollow shaft and arranged coaxially and parallel to the first countershaft VW1. The seventh switching element S7, when actuated, establishes a connection for the transmission of force and torques between the first countershaft VW1 and the fifth countershaft VW5. On the fifth countershaft VW5 a transmission element is arranged, which with a transmission element on the output shaft AW on the main axis 2 to form the fifth wheel plane V interacts.

8th shows a transmission according to an eleventh embodiment of the present invention.

In 8th is essentially a transmission 1 according to 1 shown. Unlike the gearbox 1 according to 1 includes the gearbox 1 according to 8th an electric machine EM for hybridization of the transmission 1 , The electric machine EM is connected to the transmission element on the minor axis via a shaft and a transmission element connected to the shaft 3 the first wheel plane I connected. In this way, the electric machine EM can apply force and torques to the transmission element of the first wheel plane I and thus transferred to the first countershaft VW1 and 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 on transmission elements of the fourth wheel plane IV and the fifth wheel plane V take place, ie at those transmission elements on the minor axis 3 which are arranged on the first countershaft VW1, which is designed as a solid shaft.

Overall, the switching elements S1 to S7 in the transmission 1 according to the 1 to 8th Also referred to as coupling devices and be designed in particular as synchronizers. The switching element actuators SE1 to 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 8th both fixed and loose with the respective shaft, in particular with the input shafts EW1, EW2 and / or at least one of the countershafts VW1, VW2, VW3, VW4 and VW5 and / or with the hollow shafts H1, H2, H3 or H4 are arranged or connected , The transmission elements can be designed in particular in the form of gears, preferably as spur gears, so that the wheel planes I . II . III . IV . V and VI Represent spur gears. To provide various forward and reverse gears, so different translations, the spur gears, in particular their gears, correspondingly comprise different translations.

Next can be the first, third and sixth wheel plane I . III and VI in the embodiments of the 1 . 4 . 5 . 6 and 8th be coupled by means of at least one switching element to at least one of the input shafts EW1, EW2. In the case of embodiments of the 2 and 7 can be the first wheel plane and the third wheel plane I . III be connected by means of at least one switching element with one of the input shafts EW1, EW2. In this case as well is the sixth wheel plane VI in the form of the reverse gear stage by means of at least one switching element to the first countershaft VW1 coupled. The fourth and fifth wheel plane IV . V are coupled by means of at least one switching element to the output shaft AW. Furthermore, the first input shaft EW1, which is designed as a solid shaft, can be coupled to the output shaft AW by means of at least one switching element. The transmission elements of the second and third wheel plane II . III on the minor axis 3 are fixedly connected to a coaxial with the first countershaft VW1 mounted hollow shaft and coupled by means of at least one switching element to the first countershaft VW1.

Overall, the switching elements S1 to S7 in the transmission 1 according to the 1 to 8th Also referred to as coupling devices and as already explained above, in particular be designed as synchronizers. In this case, the first switching element S1 of the first wheel plane I , the second switching element S2 of the sixth gear plane VI , the third switching element S3 of the second and third wheel plane II . III , the fourth switching element S4 of the third wheel plane III , the fifth switching element S5 of the output shaft AW and the two input shafts EW1, EW2, the sixth switching element S6 of the fourth gear plane IV and the seventh switching element S7 of the fifth gear plane V be assigned.

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

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

The gear 1 according to the 1 to 8th 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 3a and 3b 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, H5

hollow shaft

K1, K2

clutch

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

switching element

SB1, SB2, SB3, SB4

Switching element actuator

SE1, SE2, SE3, SE4

switching device

VW1, VW2, VW3, VW4, VW5

Countershaft

ZR

idler

AT

drive

FROM

output

EM

electric machine

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• DE 102006054281 A1 [0005]
• DE 102010030569 A1 [0028]

Claims (21)

Transmission ( 1 ), in particular dual-clutch transmission, for a motor vehicle, comprising at least two partial transmissions, wherein each of the partial transmissions comprises at least one input shaft (EW1, EW2), and wherein an output shaft is arranged as the output shaft (AW) of both partial transmissions, wherein the at least one input shaft (EW1, EW2) on a main axis ( 2 ) and the output shaft (AW) on the main axis ( 2 ) or on one, in particular to the main axis ( 2 ) parallel, minor axis ( 3 ), and wherein a countershaft ( 4 ) is arranged with at least one countershaft (VW1, VW2, VW3, VW4, VW5), wherein the at least one countershaft (VW1, VW2, VW3, VW4, VW5) on the minor axis ( 3 ) 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 ) and / or at least one switching element (S1, S2, S3, S4, S5, S6, S7) to the output shaft (AW) is connectable, characterized in that N switching means (SE1, SE2, SE3, SE4) are arranged, N is an integer greater than or equal to three, and that at least one switching device (SE1) on the main axis ( 2 ) and at least one switching device (SE2) on the minor axis ( 3 ), wherein one (SE1, SE3, SE2, SE3) of the at least three switching devices (SE1; SE2; SE3) has two switching elements and another (SE2; SE1) of the at least three switching devices (SE1, SE2, SE3) a single switching element includes, and wherein one ( III ) of the at least two wheel planes ( I . II . III . IV . V . VI ) Transmission elements on the main axis ( 2 ) and on the minor axis ( 3 ), which are each connected to a shaft (H3, VW2, H2, VW3) designed as a hollow shaft, and wherein the one ( III ) to at least one further wheel plane ( II ) is arranged directly adjacent. Transmission according to claim 1, characterized in that the one wheel plane ( III ) can be actuated by means of the switching device (SE3) with which at least one of the input shafts (EW1, EW2) can be connected to the output shaft. A transmission according to any one of claims 1-2, characterized in that the number N is an even number and each N / 2 switching means (SE1, SE2, SE3, SE4, SE1, SE3, SE2, SE4) on the main axis ( 2 ) and on the minor axis ( 3 ) are arranged. Transmission according to one of claims 1-3, characterized in that those switching devices (SE1, SE4), which directly to the side of the drive (AN) and / or the output (AB) in the transmission ( 1 ) are arranged on the minor axis ( 3 ) or on the main axis ( 2 ) are arranged. Transmission according to one of claims 1-4, characterized in that at least two of the input shafts (EW1, EW2) coaxial with each other and / or at least two of the countershafts (VW1, VW2; VW1, VW2, VW3; VW1, VW4) are arranged coaxially with each other , Transmission according to one of claims 1-5, characterized in that the number N is equal to four. Transmission according to one of claims 1-6, characterized in that at least one of the input shafts (EW1, EW2) and / or at least one of the countershafts (VW1, VW2, VW3, VW4, VW5) formed as a hollow shaft and the respective other shaft as a solid shaft is. Transmission according to one of claims 1-7, characterized in that at least two, in particular at least three, wheel planes ( I . III . VI ) by means of at least one switching element (S1, S2, S4) 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 at least one of the N switching devices (SE1, SE2, SE3, SE4), wherein the at least one switching device (SE1) adjacent to the side of the drive (AN) in the transmission ( 1 ) is arranged. Transmission according to one of claims 9-10, characterized in that the reverse gear ( VI ) is arranged as a first gear plane downstream of the drive (AN) side. Transmission according to one of claims 1-11, characterized in that an electric machine (EM) on at least one wheel plane ( I . II . III . IV . V . VI ) and / or on at least one countershaft (VW1, VW2, VW3, VW4, VW5) and / or on one of the input shafts (EW1, EW2) for hybridizing the transmission ( 1 ) is arranged. Transmission according to claim 12, characterized in that the electric machine (EM) at at least one of the wheel planes ( I . IV . V ), which are connected to a countershaft (VW1), formed as a solid shaft. Transmission according to one of claims 1-13, characterized in that transmission elements of at least two wheel planes ( II . III ) on the minor axis ( 3 ) with a hollow shaft trained countershaft (VW2, VW3, VW4) are firmly connected. Transmission according to one of claims 1-14, characterized in that the N switching devices (SE1, SE2, SE3, SE4) and the at least two wheel planes ( I . II . III . IV . V . VI ) are arranged so that at least six forward gears and at least three reverse gears through the transmission ( 1 ) are representable. Transmission according to one of claims 1-15, characterized in that at least two wheel planes ( IV . V ) can be coupled to the output shaft. Transmission according to one of claims 9-16, characterized in that the reverse gear ( VI ) is arranged between two switching elements (S2, S3). Transmission according to claim 17, characterized in that the two switching elements (S2, S3) on the minor axis ( 3 ) are arranged. Transmission according to one of claims 1-18, characterized in that two switching elements (S3, S4) for actuating at least one wheel plane ( III ) each torque down the at least one wheel plane ( III ) are arranged. Transmission according to one of claims 1-19, characterized in that the switching devices (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). Motor vehicle, in particular a passenger or a truck, with a transmission ( 1 ) according to any one of claims 1-20.

Images