EP2979006A1

EP2979006A1 - Transmission for a motor vehicle

Info

Publication number: EP2979006A1
Application number: EP14708513.8A
Authority: EP
Inventors: Stefan Beck; Christian Sibla; Wolfgang Rieger
Original assignee: ZF Friedrichshafen AG
Current assignee: ZF Friedrichshafen AG
Priority date: 2013-03-27
Filing date: 2014-02-25
Publication date: 2016-02-03
Also published as: JP2016517934A; US20160040756A1; WO2014154418A1; CN105051420A; DE102013205380A1

Abstract

The invention relates to a transmission, in particular multi-stage transmission, for a motor vehicle, comprising a housing, a drive input shaft, a drive output shaft, at least four planetary gear sets and six shift elements in the form of at least three clutches and at least two brakes, the planetary gear sets each comprising a sun gear, at least one planet gear, a planet gear carrier and an internal gear, wherein the drive input shaft can be connected by means of the second clutch to the planet gear carrier of the first planetary gear set, and the planet gear carrier of the first planetary gear set can be connected to the second brake, and the drive input shaft can be connected by means of the third clutch to the first brake, and the drive input shaft can be connected by means of the third clutch to the sun gear of the first planetary gear set.

Description

Transmission for a motor vehicle

The invention relates to a transmission, in particular multi-speed transmission, for a motor vehicle, comprising a housing, a drive shaft, an output shaft, at least four planetary gear sets, wherein the Planentenradsätze each comprise a sun gear, at least one planet, a planet carrier and a ring gear, and six switching elements in shape of at least three clutches and at least two brakes.

Such transmissions are known, for example, from WO 2012/052284 A1. In WO 2012/052284 A1 a multistage transmission with six forward gears and one reverse gear is shown, which comprises four planetary gear sets, seven rotatable shafts and five shift elements, wherein the sun gear of the first planetary gear set is connected to the sixth shaft, which via a first brake to the Housing of the transmission can be coupled, wherein the web of the first planetary gear set is connected to the fifth shaft, which is connected to the sun gear of the second planetary gear set and coupled via a second brake to the housing, wherein the drive shaft with the ring gear of the first planetary gear set and the sun gear connected to the third planetary gear set and via a clutch with the connected to the web of the third planetary and the ring gear of the fourth planetary gear seventh shaft is detachably connected, wherein the fourth shaft connected to the ring gear of the third planetary gear set and the web of the second planetary gear set and a third brake is coupled to the housing, wherein the output shaft is connected to the ring gear of the second planetary and the web of the fourth planetary gear set and wherein the sun gear of the fourth planetary gear set is connected to the third shaft, which is coupled via a fourth brake to the housing ,

The disadvantage here is that internal switching elements such as multi-plate clutches or brakes are hydraulically actuated. This hydraulic actuation leads to high hydraulic losses. In order to circumvent these actuation losses, it has been proposed to provide electromechanical or electrohydraulic actuations. The disadvantage here again is that the switching elements, especially the couplings are difficult to access, especially when good Verzah- tion efficiency and low component loads at low construction costs are sought.

An object of the present invention is therefore to provide a transmission for a motor vehicle, which has a good efficiency, low component load and low construction costs. Moreover, it is an object of the present invention to provide a transmission for a motor vehicle, which has good accessibility of its switching elements from the outside. 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 multi-speed transmission, for a motor vehicle comprising a housing, a drive shaft, an output shaft, at least four planetary gear sets, wherein the planetary gear sets each comprise a sun gear, at least one planet, a planet carrier and a ring gear, and six switching elements in the form of at least three clutches and at least two brakes, characterized in that the drive shaft via the second clutch with the planet carrier of the first planetary gear set and the planet carrier of the first planetary gear set with the second brake and the drive shaft via the third clutch with the first brake and the drive shaft via the third clutch with the sun gear of the first planetary gear set is connectable.

The invention solves the tasks also in a motor vehicle, in particular in a passenger or truck with a transmission according to one of claims 1 to 7.

The invention also achieves the objects with a method for operating a transmission, in particular according to one of claims 1 to 7, with three brakes and three clutches, characterized in that a first gear by means of open first brake, closed second brake, open third brake, closed a second gear is formed by means of a closed first brake, a closed second brake, an open third brake, a closed first clutch, an open second clutch and an open third clutch, and a third gear by means of open first brake, closed second brake, closed third brake, closed first clutch, open second clutch and open third clutch, and that a fourth gear by means of closed first brake, open second brake, closed third brake, closed first clutch, more open second clutch and open third clutch is formed and that a fifth gear by means of open first brake, open second brake, closed third brake, closed first clutch, open second clutch and closed third clutch is formed, and that a sixth gear by means of open first brake, open second brake, closed third brake, closed first clutch, closed second clutch and open third clutch is formed, and that a seventh gear by means of open first brake, open second brake, open third brake, closed first clutch, closed second An eighth gear is formed by means of an open first brake, an open second brake, a closed third brake, an open first clutch, a closed second clutch and a closed third clutch, and a ninth gear by means of a closed first brake, open second brake, open third brake, open first clutch, closed second clutch and third open clutch is formed and that a reverse gear formed by open first brake, closed second brake, closed third brake, open first clutch, open second clutch and closed third clutch becomes.

One of the advantages achieved with this is that in this way a good accessibility of all switching elements is ensured. In addition, the construction cost is low, which means lower costs or weight for the transmission.

A torque or a rotational movement of a drive shaft, for example of an internal combustion engine, is preferably introduced into the transmission via the drive shaft. Preferably, between the drive shaft and the output shaft is a retraction element, such as a hydrodynamic torque converter or a fluid coupling.

A shaft below is not exclusively a, for example, cylindrical, rotatably mounted machine element for transmitting torque. Menten, but rather are to be understood by this general connection elements that connect individual components or elements together, in particular connecting elements that connect a plurality of elements rotationally fixed to each other.

Two elements are in particular referred to as interconnected when between the elements a solid, in particular rotationally fixed connection consists. In particular, such connected elements rotate at the same speed.

Two elements will be referred to as connectable if there is a detachable connection between these elements. In particular, such elements rotate at the same speed when the connection is made.

The various components and elements of said invention can be connected to one another via a shaft or a connecting element, but also directly, for example by means of a welding, pressing or other connection.

Under a clutch is preferably in the description, in particular in the claims, a switching element to understand, which, depending on the operating state, a relative movement between two components permits or represents a connection for transmitting torque. Under a relative movement, for example, to understand a rotation of two components, wherein the rotational speed of the first component and the rotational speed of the second component differ from each other. In addition, the rotation of only one of the two components is conceivable, while the other component is stationary or rotating in the opposite direction.

Hereinafter, a non-actuated clutch is understood to mean an opened clutch. This means that a relative movement between the two components is possible. When the clutch is actuated or closed, the two components accordingly rotate at the same speed in the same direction. Under a brake is preferably in the description, in particular in the claims, a switching element to understand, which is connected on one side with a fixed element, such as a housing, and on another side with a rotatable element.

Hereinafter, a non-actuated brake is understood to mean an opened brake. This means that the rotating component is freely rotatable, i.e., the brake preferably does not influence the rotational speed of the rotating component. When the brake is applied or closed, the rotational speed of the rotatable component is reduced to a standstill, that is, a firm connection can be established between the rotatable element and the stationary element. Element and component are to be equated in this context.

In principle, a use of switching elements is possible, which are closed in the non-actuated state and open in the actuated state. Accordingly, the associations between function and switching state of the switching states described above are to be understood in the reverse manner. In the following embodiments with reference to the figures, an arrangement is initially based, in which an actuated switching element is closed and a non-actuated switching element is opened.

A planetary gear set comprises a sun gear, a planet carrier respectively web and a ring gear. Rotatably mounted on the planet carrier respectively web are planet gears or planets, which mesh with the toothing of the sun gear and / or the toothing of the ring gear.

In the following, a minus planetary gearset describes a planetary gearset with a planet carrier on which the planetary gears are rotatably mounted, with a sun gear and a ring gear, wherein the toothing of at least one of the planet gears meshes both with the toothing of the sun gear and with the toothing of the ring gear, whereby the ring gear and the sun gear rotate in opposite directions of rotation when the sun gear rotates when the planet carrier is stationary. A plus planetary gear set differs from the negative planetary gear set just described in that the plus planetary gear set has inner and outer planetary gears rotatably supported on the planetary carrier. The toothing of the inner planet gears meshes on the one hand with the toothing of the sun gear and on the other hand with the teeth of the outer planetary gears. The toothing of the outer planetary gears also meshes with the teeth of the ring gear. As a result, when the planet carrier is stationary, the ring gear and the sun gear rotate in the same direction of rotation.

By using planetary gear sets particularly compact gear can be realized, whereby a large freedom in the arrangement of the transmission is achieved in the vehicle.

The elements of a planetary gear set, in particular, the sun gear, the ring gear, the planet carrier respectively web and the planet gears respectively the planet of the planetary gear understood.

Particularly preferably, the switching elements are selectively, ie individually and as needed operable, whereby different gears can be realized by different ratios between the drive shaft and the output shaft. The higher the number of gears, the finer a gear ratio can be realized at a large transmission spread and thus, for example, an internal combustion engine of a motor vehicle in an optimal speed range and thus be operated as economically as possible. At the same time this contributes to an increase in ride comfort, since the internal combustion engine is preferably operable at a low speed level. For example, noise emissions resulting from the operation of the internal combustion engine are also reduced.

The term "front-transverse arrangement" is to be understood as an arrangement in which the drive shaft, for example an internal combustion engine, is installed transversely to a direction of travel in a motor vehicle and preferably the wheels of a front axle can be driven by the drive shaft or the transmission Furthermore, the switching elements can be designed such that for a change of a Switching state of the switching elements energy, but not for maintaining the switching state itself is needed.

For this purpose, switching elements which can be actuated as required in a particular manner, such as, for example, electromechanical switching elements or electromagnetic switching elements, are suitable for this purpose. They are characterized, in particular in comparison to conventionally hydraulically actuated switching elements, by a particularly low and efficient energy requirements, since they are virtually lossless operable. In addition, it can be advantageously omitted to permanently maintain a control pressure for the operation of, for example, conventionally hydraulic switching elements, or to act on the respective switching element in the switched state permanently with the required hydraulic pressure. As a result, for example, other components such as a hydraulic pump can be omitted, as far as they are used exclusively for controlling and supplying the conventionally hydraulically actuated switching elements. If the supply of additional components with lubricants does not take place via a separate lubricant pump but via the same hydraulic pump, then this can be dimensioned at least to a smaller extent. Also, any leaks occurring at Olübergabestellen the hydraulic circuit, especially for rotating components, omitted. This also particularly preferably contributes to an increase in efficiency of the transmission in the form of a higher efficiency.

When using demand-actuated switching elements of the above type, it is particularly advantageous if they are easily accessible from the outside. This has the advantage, inter alia, that the required switching energy can be well supplied to the switching elements. Therefore, switching elements are particularly well preferably arranged so that they are easily accessible from the outside. Well accessible from the outside means in the sense of the switching elements, the intermediate housing of the transmission and the switching element no further components are arranged, or that the switching elements are particularly preferably arranged on the drive shaft or on the output shaft.

The term "bondability" is preferably to be understood in the description, in particular in the claims that at different geometric Position the same connection or binding of interfaces is ensured without intersecting individual fasteners or waves.

The term "stand translation" is that translation to understand that is realized by the ratio between the sun and ring gear of each planetary gear set when the planet carrier respectively web is fixed.

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

Advantageously, the planetary gear sets, in particular geometrically, are arranged behind one another in the transmission. This allows easy manufacture and easier accessibility of the planetary gear sets in the case of maintenance.

Conveniently, the drive shaft via the first clutch to the sun gear of the second planetary gear set is connectable or the planet carrier of the first planetary gear set via the first clutch to the ring gear of the second planetary gear set or the planet carrier of the second planetary gear set is via the first clutch to the ring gear of the third planetary gear set connectable or the sun gear of the third planetary gear set is connectable via the first clutch to the planet carrier of the fourth planetary gear set and to the ring gear of the first planetary gear set or the planet carrier of the third planetary gear set is connectable via the first clutch to the output shaft. In this way, on the one hand, a direct transmission of force and torque from the drive shaft to the central sun gear of the second planetary gear set possible and / or the flexibility of the transmission with respect to the representation of different gear ratios is increased, as by means of the first clutch as needed, the drive shaft with a the planetary gear sets, two planetary gear sets or a planetary gear and the output shaft are connected to each other.

Advantageously, six switching elements are arranged, wherein either three clutches and three brakes or four clutches and two brakes are arranged. This allows sufficient flexibility of the transmission in terms the coupling of various elements of the transmission to represent different gear ratios.

Conveniently, the sun gear of the fourth planetary gear set is connectable to the housing via the third brake and the planet carrier of the fourth planetary gear set is connected to the ring gear of the first planetary gear set and the ring gear of the fourth planetary gear set is connected to the output shaft. This allows on the one hand a central fixing of the fourth planetary gear set via the third brake with the housing as needed and a connection of the output shaft via the fourth planetary with the first planetary gear, which further increases the flexibility of the transmission with respect to the representation of different gear ratios.

Advantageously, the sun gear of the fourth planetary gear set is connected to the housing and the ring gear of the first planetary gear set is connectable via the fourth clutch to the planet carrier of the fourth planetary gear set and the ring gear of the fourth planetary gear set is connected to the output shaft. This allows for a central fixing of the fourth planetary gear set via the sun gear to the housing. In addition, the first planetary gear set can be coupled in an extremely flexible manner with the fourth planetary gear set or further with the output shaft.

Conveniently, the ring gear of the fourth planetary gear set via the fourth clutch to the output shaft is connectable and the planet carrier of the fourth planetary gear set is connected to the ring gear of the first planetary gear and the sun gear of the fourth planetary gear set is connected to the housing. This can be coupled in a flexible manner, the fourth planetary gear set with the output shaft as needed. In addition, the fourth planetary gear is fixedly connected via the sun gear with the housing and the next to input and output shaft next adjacent planetary gear (first and fourth planetary gear) are directly connected.

Appropriately, an additional gear by means of closed first

Brake, open second brake, open third brake, closed first clutch ment, closed second clutch and open third clutch formed. Thus, the flexibility of the transmission with respect to the use in different vehicles is further increased. At the same time an even finer transmission gradation through the additional gear is possible.

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 schematic form:

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

FIG. 2 shows a shift matrix for a transmission according to the first embodiment of the present invention; FIG.

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

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

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

7 shows a transmission according to a sixth embodiment of the present invention;

8 shows a transmission according to a seventh embodiment of the present invention;

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

FIG. 10 shows a transmission according to a ninth embodiment of the present invention; FIG.

Fig. 1 1 shows a transmission according to a tenth embodiment of the present invention;

FIG. 12 shows a transmission according to an eleventh embodiment of the present invention; FIG.

13 shows a transmission according to a twelfth embodiment of the present invention;

14 shows a transmission according to a thirteenth embodiment of the present invention;

FIG. 15 shows a transmission according to a fourteenth embodiment of the present invention; FIG. Fig. 1 6 shows a transmission according to a fifteenth embodiment of the present invention;

Fig. 17 shows a transmission according to a sixteenth embodiment of the present invention as well

Fig. 18 shows a transmission according to a seventeenth embodiment of the present invention.

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

In Fig. 1, reference numeral 1 denotes a multi-stage transmission. The multistage transmission 1 has six shift elements in the form of three clutches K1, K2, K3 and three brakes B1, B2, B3. By means of the three clutches K1, K2, K3, the drive side can be coupled or connected to the output side of the transmission 1 for transmitting power and torques. For this purpose, the first clutch K1, the second clutch K2 and the third clutch K3 are connected to the drive shaft ANW on the drive side. The first clutch K1 is further connected to a first shaft W1, so that the clutch, when actuated, transmits power and torque from the drive shaft ANW to the first shaft W1. The same applies to the second clutch K2 and the third clutch K3. When the second clutch K2 is closed, power is transmitted from the drive shaft ANW to the second shaft W2, and when the third clutch K3 is closed, power and torque are transmitted from the drive shaft ANW to the third shaft W3.

In the transmission 1 further four planetary gear sets GP1, GP2, GP3 and GP4 and six waves W1, W2, W3, W4, W5 and W6 are arranged.

The general structure of the first planetary gearset GP1, the second planetary gearset GP2, the third planetary gearset GP3 and the fourth planetary gearset GP4 will now be described in the following. The aforementioned planetary gear sets GP1, GP2, GP3 and GP4 are constructed in the usual way and each have a central sun gear 101, 102, 103, 104, which with a planet 1 1 1, 1 12, 1 13, 1 14 cooperates to transmit power and torques. The planet 1 1 1, 1 12, 1 13, 1 14 is rotatably mounted on a web / planet carrier 121, 122, 123, 124. On the radial outer side of the planet 1 1 1, 1 12, 1 13, 1 14 a ring gear 131, 132, 133, 134 is arranged, in which the respective planet 1 1 1, 1 12, 1 13, 1 14 for the transmission of Force and torque engages. The web or planet carrier 121, 122, 123, 124 is further connected to a respective shaft. The individual reference numerals for sun gear, planet, planet carrier / web and ring gear can be seen in Fig. 1. For clarity, the reference numerals have been omitted in the other figures.

Next, the six different waves W1, W2, W3, W4, W5 and W6 will now be described.

The first shaft W1 connects the first clutch K1 and the sun gear 102 of the second planetary gear set GP2 for transmitting power and torques. The second shaft W2 connects the second clutch K2 to the ring gear 132 of the second planetary gearset GP2 and to the bridge 121 of the first planetary gearset GP1. This can be coupled to the housing G by means of the second brake B2 and the second shaft W2. The third shaft W3 connects the third clutch K3 with the sun gear 101 of the first planetary gear set GP1. The fourth shaft W4 connects the web 122 of the second planetary gear set GP2 with the ring gear 133 of the third planetary gear set GP3. The fifth shaft W5 connects the ring gear 131 of the first planetary gear set GP1 with the sun gear 103 of the third planetary gear set GP3 and with the web 124 of the fourth planetary gear set GP4. The sixth shaft W6 allows the sun gear 104 of the fourth planetary gear set GP4 to be connected to the housing G by means of a third brake B3. The third shaft W3 can be coupled to the housing G via the first brake B1. The output shaft AW is connected to the web 123 of the third planetary gear set GP3 and to the ring gear 134 of the fourth planetary gear set GP4.

Fig. 2 shows a shift matrix for a transmission according to the first embodiment of the present invention. FIG. 2 shows a switching matrix for a transmission 1 according to FIG. 1. To this end, downwards are first the nine forward gear stages, designated by the reference symbols V1 to V9, and a reverse gear stage, designated by R. Furthermore, an additional illustration of a forward gear stage is shown, designated by the reference character VZ. Horizontal the respective switching elements are shown, wherein first the three brakes B1, B2, B3 and then the three clutches K1, K2 and K3 are shown. Furthermore, the respective gear ratio / ratio i and the corresponding gear jump / step φ between two successive gears / ratios is shown. In that regard, the respective gear jump is shown in the switching matrix between each two adjacent gears / gears. In the additional representation of the further forward gear VZ only the translation is specified.

The entries released in the switching matrix, that is to say, for example, in the forward gear stage V1 in the first brake B1, in the third brake B3 and in the second clutch K2, indicate that the corresponding switching element or the brake or the clutch is open, i. that the switching element in this case transmits no forces or no torque from the connected to the switching element or connected to this respective shafts or elements of the transmission. An entry in the switching matrix provided with a cross designates a correspondingly actuated or closed switching element, that is to say in the switching matrix, for example in the forward gear stage V1 in the case of the brake B2 and the clutches K1 and K3. Unless otherwise described, the switching elements B1, B2, K1, K2, K3, K4 are open.

To represent the first forward gear V1 by means of the transmission 1 according to FIG. 1, the brake B2 and the clutches K1 and K3 are closed. The gear ratio i is 5.831. To represent the second forward gear V2, the brakes B1, B2 and the clutch K1 are closed. The gear ratio i is 3.834.

To represent the third forward gear V3, the brakes B2, B3 and the clutch K1 are closed. The gear ratio i is 2.827. To the represent fourth forward gear V4, the brakes B1, B3 and the clutch K1 are closed. The gear ratio i is 1, 926.

To represent the fifth forward speed V5, the third brake B3 and the clutches K1 and K3 are closed. The gear ratio i is 1, 474. To represent the sixth forward gear V6, the third brake B3 and the clutches K1 and K2 are closed. The gear ratio i is 1, 131.

To represent the seventh forward gear V7, all brakes B1, B2, B3 are open and all clutches K1, K2, K3 closed. The gear ratio i is 1, 000. To represent the eighth forward speed V8, the third brake B3 and the clutches K2 and K3 are closed. The gear ratio i is 0.755.

To represent the ninth forward gear V9, the first brake B1 and the third brake B3 and the second clutch K2 are closed. The gear ratio i is 0.601. To represent the reverse gear R, the brakes B2, B3 and the clutch K3 are closed. The gear ratio i is -2.945. To represent the additional forward gear VZ, the brake B1 and the clutches K1, K2 are closed. The gear ratio i is 0.918.

The gear gap φ between the first forward gear V1 and the second forward gear V2 is 1, 521, between the second forward gear V2 and the third forward gear V3 1, 356th The gear gap φ between the third forward speed V3 and the fourth forward speed V4 is 1, 468, between the fourth forward speed V4 and the fifth forward speed V5 1, 306. The gear gap φ between the fifth forward speed V5 and the sixth forward speed V6 is 1, 304, between the sixth forward speed V6 and the seventh forward speed V7 1, 131. The gear jump φ between the seventh forward speed V7 and the eighth forward speed V8 is 1, 325, between the eighth forward speed V8 and the ninth forward speed V9 1, 256. The total jump is 9.703. The first planetary gear set GP1 has a stand ratio of i ₀ = -3.900, the second planetary gear GP2 a stand translation

of i ₀ = -1, 500, the third planetary gear set GP3 a stand ratio i ₀ = -1, 873 and the fourth planetary gear set GP4 a state ratio of i ₀ = -3,082.

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

In Fig. 3, a transmission 1 according to FIG. 1 is shown. In FIG. 3, four positions A, B, C and D for the first clutch K1 can be seen, in which the first clutch K1 can be arranged to have the same effect as the position according to FIG.

The first alternative position A for the first clutch K1 is located between the ring gear of the second planetary gear GP2, the clutch K2 and the web 121 of the first planetary gearset GP1 on the second shaft W2. The second alternative position B for the first clutch K1 is located between the web 122 of the second planetary gear set GP2 and the ring gear 133 of the third planetary gear set GP3 on the fourth shaft W4.

The third alternative position C for the first clutch K1 is located between the sun gear 103 of the third planetary gear set GP3 and the portion of the fifth shaft W5 which connects the land 124 of the fourth planetary gear set GP4 and the ring gear 131 of the first planetary gear set GP1. The fourth alternative position D for the first clutch K1 is located between the web 123 of the third planetary GP3 and the portion of the output shaft AW, which connects the ring gear 134 of the fourth planetary GP4 with the output shaft AW.

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

4, a transmission 1 according to FIG. 1 is shown. FIG. 4 shows two alternative positions E, F for the third brake B3, in which the third brake B3 can be arranged to have the same effect as the position according to FIG. The first alternative position E for the third brake B3 is located between the bridge 124 of the fourth planetary gear set GP4 and the section of the fifth wave W5, which connects the sun gear 103 of the third planetary gear set GP3 and the ring gear 131 of the first planetary gear set GP1. The second alternative position F for the third brake B3 is located between the ring gear 134 of the fourth planetary gear set GP4 and the portion of the output shaft AW, which connects the web 123 of the third planetary GP3 with the output shaft AW. The sun gear 102 of the second planetary GP2 is directly connected to the drive shaft ANW. The third brake B3 acts, when it is located at the alternative positions E and F, in the sense of a (fourth) clutch, since the third brake B3 no longer interacts directly with the housing G. The name as a third brake is still maintained in the other figures.

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

In Fig. 5, a transmission 1 according to FIG. 1 is shown substantially. In contrast to the transmission 1 according to FIG. 1, in the case of the transmission 1 according to FIG. 5 the first clutch K1, now denoted by reference symbol K1 ', is arranged at the first alternative position A according to FIG. The first clutch K1 'is on the second shaft W2 on the one hand between the portion of the second shaft W2, which the

Bridge 121 of the first planetary gear set GP1 connects to the second brake B2 and the ring gear 132 of the second planetary GP2 arranged and on the other hand via the second clutch K2 and the second shaft W2 with the drive shaft AW can be coupled. The sun gear 102 of the second planetary GP2 is directly connected to the drive shaft ANW.

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

FIG. 6 essentially shows a transmission 1 according to FIG. 1. In contrast to the transmission 1 according to FIG. 1, in the case of the transmission 1 according to FIG. 6, the first clutch K1, now denoted by reference symbol K1 ", on the second alternative

Position B arranged in FIG. 3. The first clutch K1 "is now on the fourth Shaft W4 between the web 122 of the second planetary GP2 and the ring gear 133 of the third planetary GP3 arranged, ie involved in the force and torque flux between the web 122 of the second planetary GP2 and the ring gear 133 of the third planetary GP3. The first wave W1 is omitted.

Fig. 7 shows a transmission according to a sixth embodiment of the present invention.

In Fig. 7, a transmission 1 according to FIG. 1 is shown substantially. 1, in the case of the transmission 1 according to FIG. 7, the first clutch K1, here denoted by reference symbol K1 "', is arranged at the third alternative position C according to FIG the sun gear 103 of the third planetary gear set GP3 with the portion of the fifth shaft W5, which connects the web 124 of the fourth planetary gear set GP4 with the ring gear 131 of the first planetary gear set GP1. The first wave W1 is omitted.

Fig. 8 shows a transmission according to a seventh embodiment of the present invention.

In Fig. 8, a transmission 1 according to FIG. 1 is shown substantially. In contrast to the transmission 1 according to FIG. 1, in the case of the transmission 1 according to FIG. 8, the first clutch K1, here denoted by reference symbol K1 "", is arranged at the fourth alternative position D according to FIG. The first clutch K1 "" is thus between the web 123 of the third planetary GP3 and the portion of the output shaft AW, which connects the ring gear 134 of the fourth planetary gear set GP4 with the output shaft AW arranged. The first wave W1 is omitted.

Fig. 9 shows a transmission according to an eighth embodiment of the present invention.

FIG. 9 essentially shows a transmission 1 according to FIG. 1. In contrast to the transmission 1 according to FIG. 1, the transmission 1 according to FIG. 9 is the third one Brake B3, designated here by reference symbol B3 ', is now arranged at the first alternative position E according to FIG. 4. The third brake B3 'is thus disposed between the land 124 of the fourth planetary gear set GP4 and the portion of the fifth shaft W5 connecting the sun gear 103 of the third planetary gear set GP3 and the ring gear 131 of the first planetary gear set GP1. The sun gear 104 of the fourth planetary gear set GP4 is now firmly connected to the housing G.

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

FIG. 10 essentially shows a transmission 1 according to FIG. 1. In contrast to the transmission 1 according to FIG. 1, in the case of the transmission 1 according to FIG. 10 the first clutch K1, designated here by reference symbol K1 ', is arranged at the first alternative position A according to FIG. 3 or according to FIG. 5 and the third brake B3 is arranged at the first alternative position E according to FIG. 4 or according to FIG. 9, designated here by reference symbol B3 '. The first wave W1 is omitted.

Fig. 11 shows a transmission according to a tenth embodiment of the present invention.

In Fig. 1 1, a transmission 1 according to FIG. 1 is shown substantially. In contrast to the transmission 1 according to FIG. 1, in the case of the transmission 1 according to FIG. 11 the first clutch K1, designated here by reference symbol K1 ", is arranged at the second alternative position B according to FIG. 3 or according to FIG. 6 and the third brake B3, designated here by reference symbol B3 ', is arranged at the first alternative position E according to FIG. 4 or according to FIG. 9. The first wave W1 is omitted.

Fig. 12 shows a transmission according to an eleventh embodiment of the present invention.

FIG. 12 essentially shows a transmission 1 according to FIG. 1. In contrast to the transmission 1 according to FIG. 1, the transmission 1 according to FIG. 12 is the first

Clutch K1, here denoted by reference K1 "', at the third alternative Position C according to FIG. 3 or according to FIG. 7 and the third brake B3, designated here by reference symbol B3 ", is arranged at the first alternative position E according to FIG. 4 or according to FIG. 9. The first shaft W1 is omitted ,

Fig. 13 shows a transmission according to a twelfth embodiment of the present invention.

FIG. 13 essentially shows a transmission 1 according to FIG. 1. In contrast to the transmission 1 according to FIG. 1, in the case of the transmission 1 according to FIG. 13 the first clutch K1, designated here by reference symbol K1 "", at the fourth alternative position D according to FIG. 3 or according to FIG. 8 and the third brake B3, designated here by reference symbol B3 \ is arranged at the first alternative position E according to FIG. 4 or according to FIG. 9. The first wave W1 is omitted.

Fig. 14 shows a transmission according to a thirteenth embodiment of the present invention.

In Fig. 14, a transmission 1 according to FIG. 1 is shown substantially. In contrast to the transmission 1 according to Fig. 1, in the transmission 1 according to Fig. 14 the third brake B3, here designated by reference symbol B3 ", is arranged at the second alternative position F according to Fig. 4. The third brake B3 is thus between the ring gear 104 of the fourth planetary gear set GP4 and the portion of the output shaft AW, which is connected to the web 123 of the third planetary gear set GP3 arranged.

Fig. 15 shows a transmission according to a fourteenth embodiment of the present invention.

In Fig. 15, a transmission 1 according to FIG. 1 is shown substantially. In contrast to the transmission 1 according to FIG. 1, in the case of the transmission 1 according to FIG. 15, the first clutch K1, designated here by reference symbol K1 ', is arranged at the first alternative position A according to FIG. 3 or according to FIG. 5 and the third brake B3, designated here by reference symbol B3 ", is at the second alternative position F according to FIG

Fig. 4 and FIG. 14 arranged. The first wave W1 is omitted. Fig. 1 shows a transmission according to a fifteenth embodiment of the present invention.

In Fig. 1 6, a transmission 1 according to FIG. 1 is shown substantially. In contrast to the transmission 1 according to FIG. 1, in the case of the transmission 1 according to FIG. 16 the first clutch K1, designated here by reference symbol K1 ", is arranged at the second alternative position B according to FIG. 3 or according to FIG. 6 and the third one Brake B3, designated here by reference symbol B3 ", is arranged at the second alternative position F according to FIG. 4 or according to FIG. 14. The first wave W1 is omitted.

Fig. 17 shows a transmission according to a sixteenth embodiment of the present invention.

In Fig. 17, a transmission 1 according to FIG. 1 is shown substantially. In contrast to the transmission 1 according to FIG. 1, in the case of the transmission 1 according to FIG. 17 the first clutch K1, here denoted by reference symbol K1 "', is arranged at the third alternative position C according to FIG. 3 or according to FIG. 7 and the third one Brake B3, designated here by reference symbol B3 ", is arranged at the second alternative position F according to FIG. 4 or according to FIG. 14. The first wave W1 is omitted.

FIG. 18 essentially shows a transmission 1 according to FIG. 1. In contrast to the transmission 1 according to FIG. 1, in the case of the transmission 1 according to FIG. 18, the first clutch K1, designated here by reference symbol K1 "", is arranged at the fourth alternative position D according to FIG. 3 or according to FIG. 8 and the third one Brake B3, designated here by reference symbol B3 ", is arranged at the second alternative position F according to FIG. 4 or according to FIG. 14.

Overall, the transmission 1 according to FIGS. 1 to 18 comprises four planetary gear sets GP1, GP2, GP3, GP4, six switching elements B1, B2, B3, K1, K2, K3, wherein the

Switching elements in the form of at least three clutches and at least two brake sen are formed. Furthermore, a maximum of a fixed housing coupling is available. Finally, two switching elements to be switched at the same time are arranged.

As a starting element for the transmission 1, a hydrodynamic torque converter, a hydrodynamic clutch, an additional starting clutch, an integrated starting clutch or brake and / or an additional electric machine can be arranged. On each of the eight shafts W1 to W6, an electric machine or other power / power source can be arranged. Moreover, on each of the shafts W1 to W6 or each link, a freewheel may be arranged to the housing G or to another shaft W1, W2, W3, W4, W5, W6. The transmission 1 can preferably be installed in standard drive construction or in front / transverse design in a motor vehicle. As switching elements frictional and / or positive switching elements are possible. In particular, the second brake B2 and the first clutch K1 can be designed as a form-fitting, in particular as claw switching elements, which leads to significant fuel consumption advantages of a provided with the transmission motor vehicle with internal combustion engine.

The transmission offers a total of at least nine forward gears and at least one reverse gear.

In summary, the present invention has the advantage that a low construction cost for the transmission is required, which results in lower manufacturing costs and lower weight of the transmission. Furthermore, the transmission offers a good gear ratio, low absolute and relative speeds as well as low planetary gearset and shift element torques. In addition, the present invention provides good gearing efficiencies and a very good accessibility of all switching elements, in particular for their maintenance.

Although the present invention has been described above with reference to preferred embodiments, it is not limited thereto, but modifiable in many ways. Thus, for example, the geometric position / sequence of the individual planetary gear sets GP1, GP2, GP3, GP4 and the individual switching elements K1, K2, K3, B1, B2, B3, K1 ', K1 ", K1"', K1 "", Β3 ' Taking into account the binding ability of the respective transmission elements, B3 "can be freely selected among one another, whereby individual transmission elements can be displaced as desired in their position within the transmission 1.

Furthermore, taking into account the bondability, it is possible to convert one or more planetary gear sets designed as minus planetary gear sets into plus planetary gear sets with simultaneous interchange of web and hollow wheel connection and an increase in stand ratio by one.

REFERENCE CHARACTERS

1 gearbox

GP1, GP2, GP3, GP4 planetary gear set 101, 102, 103, 104 sun gear 111, 112, 113, 114 planet gear 121, 122, 123, 124 bridge

131, 132, 133, 134 ring gear

ANW drive shaft AW output shaft

B1, B2, B3, Β3 ', B3 "Brake

K1, K2, K3, K1 ', K1 ", K1'", K1 coupling

G housing

V1, V2, V3, V4, V5, V6, V7,

V8, V9, VZ forward

R reverse gear

W1, W2, W3, W4, W5, W6 shaft

I Translation / Ratio

Φ transition / step

A, B, C, D position coupling

Position brake

Claims

claims

1 . Transmission (1), in particular multi-speed transmission, for a motor vehicle, comprising a housing (G), a drive shaft (ANW), an output shaft (AW), at least four planetary gear sets (GP1, GP2, GP3, GP4), wherein the planetary gear sets (GP1, GP2, GP3, GP4) in each case a sun gear (101, 102, 103, 104), at least one planet (1 1 1, 1 12.1 13.1 14), a planet carrier (121, 122, 123, 124) and a Ring gear (131, 132, 133, 134) include, as well as six switching elements (K1, K2, K3, B1, B2, B3) in the form of at least three clutches (K1, K2, K3) and at least two brakes (B1, B2) , characterized in that the drive shaft (ANW) via the second clutch (K2) with the planet carrier (121) of the first planetary gear set (GP3) and the planet carrier (121) of the first planetary gear set (GP1) with the second brake (B2) and the Drive shaft (ANW) via the third clutch (K3) with the first brake (B1) and the drive shaft (ANW) via the third clutch (K3) with the sun gear (1 01) of the first planetary gear set (GP1) is connectable.

2. Transmission according to claim 1, characterized in that the planetary gear sets (GP1, GP2, GP3, GP4), in particular geometrically, one behind the other in the transmission (1) are arranged.

3. Transmission according to one of claims 1 -2, characterized in that the drive shaft (ANW) via the first clutch (K1) with the sun gear (102) of the second planetary gear set (GP2) is connectable or the planet carrier (121) of the first planetary gear set (GP1) via the first clutch (K1) with the ring gear (132) of the second planetary gear set (GP2) is connectable or the planet carrier (122) of the second planetary gear set (GP2) via the first clutch (K1) with the ring gear (133) of third planetary gear set (GP3) is connectable or the sun gear (103) of the third planetary gear set (GP3) via the first clutch (K1) with the planet carrier (124) of the fourth planetary gear set (GP4) and with the ring gear (101) of the first planetary gear set (GP1 ) is connectable or the planet carrier (123) of the third planetary gear set (GP3) via the first clutch (K1) to the output shaft (AW) is connectable.

4. Transmission according to one of claims 1 -3, characterized in that six Schalteiemente are arranged, wherein either three clutches (K1, K2, K3) and three brakes (B1, B2, B3) or four clutches (K1, K2, K3 , B3 ', K1, K2, K3, B3 ^" ) and two brakes (B1, B2) are arranged.

5. Transmission according to one of claims 1 -4, characterized in that the sun gear (104) of the fourth planetary gear set (GP4) via the third brake (B3) to the housing (G) is connectable and the planet carrier (124) of the fourth planetary gear set (GP4) is connected to the ring gear (131) of the first planetary gear set (GP1) and the ring gear (134) of the fourth planetary gear set (GP4) is connected to the output shaft (AW).

6. A transmission according to any one of claims 1-5, characterized in that the sun gear (104) of the fourth Planentenradsatzes (GP4) is connected to the housing (G) and the ring gear (131) of the first planetary gear set (GP1) via the fourth clutch (Β3 ', B3 ") to the planet carrier (124) of the fourth planetary gear set (GP4) is connectable and the ring gear (134) of the fourth planetary gear set (GP4) is connected to the output shaft (AW).

7. A transmission according to any one of claims 1-6, characterized in that the ring gear (134) of the fourth planetary gear set (GP4) via the fourth clutch (Β3 ', B3 ^" ) with the output shaft (AW) is connectable and the planet carrier (124 ) of the fourth planetary gear set (GP4) is connected to the ring gear (131) of the first planetary gear set (GP1) and the sun gear (104) of the fourth planetary gear set (GP4) is connected to the housing (G).

8. A method for operating a transmission (1), in particular according to one of claims 1-7, with three brakes (B1, B2, B3) and three clutches (K1, K2, K3), characterized in that

a first gear (V1) is formed by means of an open first brake (B1), a closed second brake (B2), an open third brake (B3), a closed first clutch (K1), an open second clutch (K2) and a closed third clutch (K3) , and that a second gear (V2) is formed by means of a closed first brake (B1), a closed second brake (B2), an open third brake (B3), a closed first clutch (K1), an open second clutch (K2) and an open third clutch (K3) , and that

a third gear (V3) is formed by means of an open first brake (B1), a closed second brake (B2), a closed third brake (B3), a closed first clutch (K1), an open second clutch (K2) and an open third clutch (K3) , and that

a fourth gear (V4) is formed by means of a closed first brake (B1), an open second brake (B2), a closed third brake (B3), a closed first clutch (K1), an open second clutch (K2) and an open third clutch (K3) and that

a fifth gear (V5) is formed by means of an open first brake (B1), an open second brake (B2), a closed third brake (B3), a closed first clutch (K1), an open second clutch (K2) and a closed third clutch (K3) , and that

a sixth gear (V6) is formed by means of an open first brake (B1), an open second brake (B2), a closed third brake (B3), a closed first clutch (K1), a closed second clutch (K2) and an open third clutch (K3) , and that

a seventh gear (V7) is formed by means of an open first brake (B1), an open second brake (B2), an open third brake (B3), a closed first clutch (K1), a closed second clutch (K2) and a closed third clutch (K3) , and that

an eighth gear (V8) is formed by an open first brake (B1), an open second brake (B2), a closed third brake (B3), an open first clutch (K1), a closed second clutch (K2) and a closed third clutch (K3) , and that

a ninth gear (V9) is formed by a closed first brake (B1), an open second brake (B2), an open third brake (B3), an open first clutch (K1), a closed second clutch (K2) and an open third clutch (K3) and that a reverse gear (R) by means of open first brake (B1), closed second brake (B2), closed third brake (B3), open first clutch ment (K1), open second clutch (K2) and closed third clutch (K3) is formed.

9. The method according to claim 8, characterized in that an additional gear (VZ) by means of closed first brake (B1), open second brake (B2), open third brake (B3), closed first clutch (K1), closed second clutch ( K2) and open third clutch (K3) is formed.

10. motor vehicle, in particular a passenger or a truck, with a transmission (1) according to any one of claims 1-7.