Transmission for a motor vehicle

The invention relates to a transmission, in particular a multi-speed transmission for a motor vehicle, including a housing, a drive shaft, an output shaft, at least four planetary gear sets, whereas each of the planetary gear sets includes one sun gear, at least one planet, one planetary carrier and one ring gear, along with several shift elements in the form of at least four clutches and at least two brakes.

Such transmissions are known, for example, from WO 2012/052284 A1. In WO 2012/052284 A1, a multi-speed transmission with six forward gears and one reverse gear is shown, which comprises four planetary gear sets, seven rotatable shafts and five shift elements, whereas the sun gear of the first planetary gear set is connected to the sixth shaft, which is attachable through a first brake to the housing of the transmission, whereas the bar 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 is attachable through a second brake to the housing, whereas the drive shaft is connected to the ring gear of the first planetary gear set and to the sun gear of the third planetary gear set and is detachably connectable through a clutch to the seventh shaft connected to the bar of the third planetary gear set and the ring gear of the fourth planetary gear set, whereas the fourth shaft is connected to the ring gear of the third planetary gear set and to the bar of the second planetary gear set and is connectable through a third brake to the housing, whereas the output shaft is connected to the ring gear of the second planetary gear set and to the bar of the fourth planetary gear set and whereas the sun gear of the fourth planetary gear set is connected to the third shaft, which is attachable through a fourth brake to the housing.

The disadvantage here is that internal shift elements, such as multi-disk clutches or brakes, are hydraulically actuated. This hydraulic actuation leads to high hydraulic losses. In order to avoid such actuation losses, providing electro-mechanical or electro-hydraulic actuation has been proposed. In turn, the disadvantage here is that the shift elements, primarily clutches, are difficult to access, in particular if good gearing efficiency and low component stresses with low construction costs are desired.

As such, a task of the present invention is to provide a transmission for a motor vehicle, which has a high degree of efficiency, low component stress and low construction costs. Moreover, it is a task of the present invention to provide a transmission for a motor vehicle that features easy accessibility for its shift elements from the outside. An additional task of the present invention is to provide an alternative transmission for a motor vehicle. Additional objects and advantages of the invention will be set forth in part in the following description, or may be obvious from the description, or may be learned through practice of the invention.

The present invention solves the tasks for a transmission, in particular a multi-clutch transmission for a motor vehicle, and includes a housing, a drive shaft, an output shaft, at least four planetary gear sets, whereas each of the planetary gear sets comprises one sun gear, at least one planet, one planetary carrier and one ring gear, along with several shift elements in the form of at least four clutches and at least two brakes. The sun gear of the fourth planetary gear set is connected to the housing. The planetary carrier of the fourth planetary gear set is connectable through the fourth clutch to the drive shaft. The second brake is connected to the sun gear of the first planetary gear set. The first brake is connected to the ring gear of the first planetary gear set and to the planetary carrier of the first planetary gear set. The first brake is connectable through the third clutch to the drive shaft.

The invention also solves the task for a motor vehicle, in particular for a passenger car or a truck, with a transmission in accordance with the invention.

The invention also solves the task with a method for operating a transmission with two brakes and four clutches. A first gear is formed by means of an open first brake, a locked second brake, an open first clutch, a locked second clutch, an open third clutch and a locked fourth clutch. A second gear is formed by means of an open first brake, a locked second brake, an open first clutch, an open second clutch, a locked third clutch and a locked fourth clutch. A third gear is formed by means of an open first brake, an open second brake, an open first clutch, a locked second clutch, a locked third clutch and a locked fourth clutch. A fourth gear is formed by means of an open first brake, an open second brake, a locked first clutch, a locked second clutch, an open third clutch and a locked fourth clutch; or by means of an open first brake, a locked second brake, a locked first clutch, an open second clutch, an open third clutch and a locked fourth clutch; or is formed by means of a locked first brake, an open second brake, a locked first clutch, an open second clutch, an open third clutch and a locked fourth clutch; or by means of an open first brake, an open second brake, a locked first clutch, an open second clutch, a locked third clutch and a locked fourth clutch. A fifth gear is formed by means of an open first brake, an open second brake, a locked first clutch, a locked second clutch, a locked third clutch and an open fourth clutch. A sixth gear is formed by means of an open first brake, a locked second brake, a locked first clutch, an open second clutch, a locked third clutch and an open fourth clutch. A seventh gear is formed by means of an open first brake, a locked second brake, a locked first clutch, a locked second clutch, an open third clutch and an open fourth clutch. An eighth gear is formed by means of a locked first brake, a locked second brake, a locked first clutch, an open second clutch, an open third clutch and an open fourth clutch. A ninth gear is formed by means of a locked first brake, an open second brake, a locked first clutch, a locked second clutch, an open third clutch and an open fourth clutch and that a reverse gear is formed by means of a locked first brake, an open second brake, an open first clutch, a locked second clutch, an open third clutch and a locked fourth clutch.

One of the advantages obtained thereby is that, in this manner, good accessibility of all shift elements is ensured. In addition, the construction costs are low, which means lower costs and weight of the transmission.

It is particularly preferable that, through the drive shaft, a torque or a rotational movement of a drive shaft, for example an internal combustion engine, is introduced into the transmission. In a preferred manner, a start-up element, such as a hydrodynamic torque converter or a fluid clutch, is located between the drive shaft and the output shaft.

In the following, a “shaft” is not solely understood as an exemplary cylindrical, rotatably mounted machine element for the transfer of torques, but is also understood as a general connection element, which connects individual components or elements to each other, in particular connection elements that connect several elements to each other in a torque-proof manner.

In particular, two elements are described as connected to each other if there is a fixed (in particular, a torque-proof) connection between the elements. In particular, such connected elements rotate with the same rotational speed.

Furthermore, two elements are described as connectable if there is a detachable connection between such elements. In particular, such elements rotate with the same rotational speed if the connection exists.

The various components and elements of the specified invention may be connected to each other through a shaft or a connection element, or also directly, for example by means of a welded connection, crimping connection or another connection.

In the description, in particular in the claims, a “clutch” is preferably understood as a shift element that, depending on the operating state, allows a relative movement between two components or represents a connection for transferring torque. “Relative motion” is understood (for example) as a rotation of two components, whereas the rotational speed of the first component and the rotational speed of the second component are different from one another. Moreover, the rotation of only one of the two components is possible, while the other component is at a standstill or is rotating in the opposite direction.

In the following, a “non-actuated clutch” is understood as an open clutch. This means that a relative movement between the two components is possible. With an actuated or locked clutch, the two components rotate accordingly at the same rotational speed in the same direction.

In the description, in particular in the claims, a “brake” is understood as a shift element that is connected on one side to a stationary element, such as a housing, and on the other side to a rotatable element.

In the following, a “non-actuated brake” is understood as an open brake. This means that the rotating component is freely rotatable; that is, the brake preferably has no influence on the rotational speed of the rotating component. With an actuated or locked brake, there is a reduction in the rotational speed of the rotatable component up to a standstill; that is, a firm connection between the rotatable element and the stationary element can be produced. In this context, “element” and “component” are equivalent.

As a general rule, the use of shift elements that are locked in a non-actuated state and open in an actuated state is also possible. Accordingly, the allocations between function and shifting state of the shift elements described above are understood in reverse order. With the following embodiments on the basis of the figures, an arrangement in which an actuated shift element is locked and a non-actuated shift element is open is initially used as the basis.

A planetary gear set comprises one sun gear, one planetary carrier or bar, as the case may be, and one ring gear. Planetary gears or planets that mesh with the toothing of the ring gear and/or with the toothing of the sun gear are rotatably mounted on the planetary carrier or the bar, respectively.

In the following, a negative planetary gear set describes a planetary gear set with a planetary carrier on which the planetary gears are rotatably mounted, with one sun gear and one ring gear, whereas the toothing of at least one of the planetary gears meshes with both the toothing of the sun gear and with the toothing of the ring gear, by which the ring gear and the sun gear rotate in opposite directions, if the sun gear rotates with a fixed planetary carrier.

A positive planetary gear set differs from the negative planetary gear set just described in that the positive planetary gear set features inner and outer planetary gears, which are rotatably mounted on the planetary carrier. Thereby, the toothing of the inner planetary gears meshes, on the one hand, with the toothing of the sun gear and, on the other hand, with the toothing of the outer planetary gears. The toothing of the outer planetary gears also meshes with the toothing of the ring gear. This has the consequence that, with a fixed planetary carrier, the ring gear and the sun gear rotate in the same direction of rotation.

A particularly compact transmission can be realized through the use of planetary gear sets, by which a high degree of freedom in the arrangement of the transmission in the vehicle is achieved.

“Elements of a planetary gear set” are understood in particular as the sun gear, the ring gear, the planetary carrier or bar, respectively, and the planetary carrier or planets, respectively, of the planetary gear set.

It is particularly preferable that the shift elements are able to be actuated selectively, thus individually and in line with demand, by which different gears can be realized through different transmission ratio relationships between the drive shaft and the output shaft. The higher the number of gears, the finer a gear shifting can be realized with a large gear spread, and thus, for example, an internal combustion engine of a motor vehicle can be operated in an optimal rotational speed range and thus as efficiently as possible. At the same time, this contributes to increased driving comfort, since the internal combustion engine preferably can be operated at a low rotational speed level. Thus, for example, noise emissions that arise through the operation of the internal combustion engine are reduced.

The term “front-transverse arrangement” is understood as an arrangement with 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, as the case may be. Furthermore, the shift elements may be formed in such a manner that energy is required for a change in the shifting state of the shift elements, but not for maintaining the shifting state itself.

For this purpose, actuated shift elements in line with demand, such as electromechanical shift elements or electromagnetic shift elements, are suitable in a particular way. Particularly when compared to conventional hydraulically actuated shift elements, they are characterized by a particularly low and efficient energy demand, since they can be operated nearly loss-free. In addition, in an advantageous manner, permanently holding a control pressure for the actuation of the (for example) conventional hydraulic shift elements, and/or permanently applying the shift element in the shifted state with the required hydraulic pressure, can be avoided. Thereby, additional components such as a hydraulic pump (for example) may be omitted, to the extent that they are solely used for the control and supply of conventional hydraulically actuated shift elements. If the additional components are supplied with lubricants by the same hydraulic pump, and not by a separate lubrication pump, at least they can be dimensioned smaller. Moreover, any leaks at the oil transfer points of the hydraulic circuit that may arise, particularly with rotating components, are eliminated. It is particularly preferable that this also contributes to increased efficiency of the transmission in the form of a higher degree of efficiency.

Upon the use of actuated shift elements in line with demand of the type specified above, it is particularly advantageous if they are easily accessible from the outside. Among other things, that has the advantage that the required shifting energy can be easily fed to the shift elements. Therefore, the shift elements are, particularly preferably, arranged so that they are easily accessible from the outside. Within the context of the shift elements, “easily accessible from the outside” means that no additional components are arranged between the housing of the transmission and the shift element, and/or that the shift elements are, particularly preferably, arranged on the output shaft or on the drive shaft.

In the description, in particular in the claims, the term “binding ability” is preferably understood such that, with a different geometrical positioning, the same connection or binding of the interfaces is ensured, without the individual connection elements or shafts crossing each other.

The term “stationary transmission ratio” is understood as that transmission ratio that is realized by the transmission ratio relationship between the sun gear and the ring gear of the respective planetary gear set if the planetary carrier or bar, as the case may be, is fixed.

Additional advantageous embodiments, characteristics and advantages of the invention are described in the subclaims.

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

Beneficially, the drive shaft is connectable through the first clutch to the planetary carrier of the third planetary gear set, and the sun gear of the third planetary gear set is connected to the planetary carrier of the second planetary gear set, to the planetary carrier of the first planetary gear set and to the ring gear of the fourth planetary gear set, and the ring gear of the third planetary gear set is connected to the output shaft. Thus, by means of the first clutch, in a flexible manner, power and torque may be transferred from the drive shaft to the third planetary gear set and further at all other planetary gear sets through the third planetary gear set.

Advantageously, the drive shaft is connected to the planetary carrier of the third planetary gear set, and the ring gear of the third planetary gear set is connected to the planetary carrier of the second planetary gear set, to the planetary carrier of the first planetary gear set and to the ring gear of the fourth planetary gear set, and the ring gear of the third planetary gear set is connectable through the first clutch to the output shaft. Thus, for example, power and torque are transferred from the drive shaft directly to the third planetary gear set and, depending on the need, they are coupled to the output shaft in a flexible manner.

Beneficially, the drive shaft is connected to the planetary carrier of the third planetary gear set, and the sun gear of the third planetary gear set is connectable through the first clutch to the planetary carrier of the second planetary gear set, to the planetary carrier of the first planetary gear set and to the ring gear of the fourth planetary gear set, and the ring gear of the third planetary gear set is connected to the output shaft. Firstly, power and torque may thus be transferred directly from the drive shaft to the third planetary gear set, and further directly to the output shaft by means of the third planetary gear set. Other planetary gear sets may be connected by means of the first clutch to the third planetary gear set in a flexible manner.

Advantageously, the drive shaft is connectable through the second clutch to the sun gear of the second planetary gear set, and the ring gear of the second planetary gear set is connected to the second brake. The advantage of this in turn is that the drive shaft is connectable to the central element in the form of the sun gear of the second planetary gear set; at the same time, the ring gear of the planetary gear set can be coupled in a flexible manner with the housing through the second brake.

Beneficially, the drive shaft is connectable to the sun gear of the second planetary gear set, and the ring gear of the second planetary gear set is connectable through the second clutch to the second brake and to the sun gear of the first planetary gear set. The advantage thereby is that force and torque can be transferred directly from the drive shaft to the second planetary gear set. Moreover, in a flexible manner, the second planetary gear set can be connected through the second clutch to the second brake and to the first planetary gear set.

Additional important characteristics and advantages of the invention arise from the drawings, and from the associated description of the figures on the basis of the drawings.

It is understood that the characteristics specified above and the characteristics that are still to be described below are usable not only in the indicated combination, but also in other combinations or alone, without leaving the framework of the present invention.

Preferred designs and embodiments of the invention are presented in the drawings and are described more specifically in the following description, whereas the same reference signs refer to identical or similar or functionally identical components or elements.

The following are shown, each in schematic form:

FIG. 1 is a transmission in accordance with a first embodiment of the present invention;

FIG. 2 is a shifting matrix for a transmission in accordance with the first embodiment of the present invention;

FIG. 3 is a transmission in accordance with a second embodiment of the present invention;

FIG. 4 is a transmission in accordance with a third embodiment of the present invention;

FIG. 5 is a transmission in accordance with a fourth embodiment of the present invention;

FIG. 6 is a transmission in accordance with a fifth embodiment of the present invention;

FIG. 7 is a transmission in accordance with a sixth embodiment of the present invention;

FIG. 8 is a transmission in accordance with a seventh embodiment of the present invention; and

FIG. 9 is a transmission in accordance with an eighth embodiment of the present invention.

Reference will now be made to embodiments of the invention, one or more examples of which are shown in the drawings. Each embodiment is provided by way of explanation of the invention, and not as a limitation of the invention. For example features illustrated or described as part of one embodiment can be combined with another embodiment to yield still another embodiment. It is intended that the present invention include these and other modifications and variations to the embodiments described herein.

FIG. 1 shows a transmission in accordance with a first embodiment of the present invention.

In FIG. 1 , reference sign 1 designates a multi-speed transmission. The multi-stage transmission 1 features six shift elements in the form of four clutches K 1 , K 2 , K 3 , K 4 and two brakes B 1 , B 2 . By means of the four clutches K 1 , K 2 , K 3 , K 4 , the drive side can be coupled or connected to the output side of the transmission for transferring power and torques through shafts and/or the planetary gear sets. For this purpose, the first clutch K 1 , the second clutch K 2 and the third clutch K 3 are connected to the drive shaft ANW on the drive side. The first clutch K 1 is also connected to a first shaft W 1 , such that, when actuated, the first clutch K 1 transfers power and torque from the drive shaft ANW to the first shaft W 1 . This correspondingly applies for the second clutch K 2 and the third clutch K 3 . Upon locking the second clutch K 2 , power and torque are transferred from the drive shaft ANW to the second shaft W 2 ; upon locking the third clutch K 3 , power and torque are transferred from the drive shaft ANW to the third shaft W 3 .

In the transmission 1 , four planetary gear sets GP 1 , GP 2 , GP 3 , GP 4 and six shafts W 1 , W 2 , W 3 , W 4 , W 5 and W 6 are also arranged.

Below, the general structure of the first planetary gear set GP 1 , the second planetary gear set GP 2 , the third planetary gear set GP 3 and the fourth planetary gear set GP 4 will initially be described. The planetary gear sets GP 1 , GP 2 , GP 3 and GP 4 specified above are constructed in the usual manner, and in each case feature a central sun gear 101 , 102 , 103 , 104 , which interacts with a planet 111 , 112 , 113 , 114 for the transfer of power and torques. The planet 111 , 112 , 113 , 114 is rotatably mounted on a bar/planetary carrier 121 , 122 , 123 , 124 . On the radially outer side of the planet 111 , 112 , 113 , 114 , a ring gear 131 , 132 , 133 , 134 is arranged, in which the respective planet 111 , 112 , 113 , 114 is engaged for the transfer of power and torques. The bar or planetary carrier 121 , 122 , 123 , 124 , as the case may be, is further connected to a shaft. The individual reference signs for sun gear, planet, planetary carrier/bar and ring gear can be seen in FIG. 1 . For the sake of clarity, the reference signs have been omitted in the additional figures.

The six different shafts W 1 , W 2 , W 3 , W 4 , W 5 and W 6 will now be described.

The first shaft W 1 connects the first clutch K 1 and the bar 123 of the third planetary gear set GP 3 . The second shaft W 2 connects the second clutch K 2 to the sun gear 102 of the second planetary gear GP 2 . The third shaft W 3 connects the third clutch K 3 to the ring gear 131 of the first planetary gear set GP 1 , and can be coupled through a brake B 1 with the housing G. The fourth shaft W 4 connects the sun gear 101 of the first planetary gear set GP 1 and the ring gear 132 of the second planetary gear set GP 2 , and can be coupled through a brake B 2 with the housing G. The fifth shaft W 5 connects the bar 121 of the first planetary gear set GP 1 , the bar 122 of the second planetary gear set GP 2 , the sun gear 103 of the third planetary gear set GP 3 and the ring gear 134 of the fourth planetary gear set GP 4 . The sixth shaft W 6 is connected, on the one hand, in a torque-proof manner to the housing G, and, on the other hand, to the sun gear 104 of the fourth planetary gear set GP 4 .

The output shaft AW is connectable, on the one hand, to the ring gear 133 of the third planetary gear set GP 3 and, on the other hand, through a fourth clutch K 4 to the bar 124 of the fourth planetary gear set GP 4 .

FIG. 2 shows a shifting matrix for a transmission in accordance with the first embodiment of the present invention.

FIG. 2 presents a shifting matrix for a transmission 1 in accordance with FIG. 1 . Downwards in a vertical direction to this, nine forward gears, designated with the reference signs V 1 to V 9 , and one reverse gear designated with R, are initially shown. Furthermore, three alternative presentations of the fourth forward gear V 4 , designated with the reference signs VM I , VM I and VM III , are shown. The respective shift elements are shown horizontally, whereas the two brakes B 1 , B 2 and then the four clutches K 1 , K 2 , K 3 and K 4 are initially shown. Furthermore, the respective transmission ratio relationship/ratio i and the corresponding gear jump/step φ is shown between two consecutive gears/gear steps. In this respect, the respective gear jump is presented in the shifting matrix between two adjacent gears/gear steps. With each of the alternative presentations of the fourth forward gear V 4 , only the transmission ratios are indicated.

The entries left empty in the shifting matrix, thus, for example, with the forward gear V 1 , with the first brake B 1 along with the first clutch K 1 and the third clutch K 3 indicate that the corresponding shift element or brakes or clutch, as the case may be, is open; i.e., that the shift element thereby does not transfer any power or torque from the respective shafts or elements of the transmission attached to the shift element or connected to it. An entry in the shifting matrix provided with a cross designates a correspondingly actuated or locked shift element, thus in the shifting matrix, for example, with the forward gear V 1 , with the brake B 2 and with the clutches K 2 and K 4 . To the extent not otherwise described, the shift elements B 1 , B 2 , K 1 , K 2 , K 3 , K 4 are open.

In order to present the first forward gear V 1 by means of the transmission 1 in accordance with FIG. 1 , the brake B 2 and the clutches K 2 and K 4 are locked. The transmission ratio relationship i is 4.515. In order to present the second forward gear V 2 , the brake B 2 and the clutches K 3 and K 4 are locked. The transmission ratio relationship i is 2.593.

In order to present the third forward gear V 3 , all of the brakes are open and the clutches K 2 , K 3 and K 4 are locked. The transmission ratio relationship i is 1.667. In order to present the fourth forward gear V 4 , all of the brakes B 1 , B 2 are open and the clutches K 1 , K 2 and K 4 are locked. The transmission ratio relationship i is 1.267.

In order to present the fifth forward gear V 5 , all of the brakes are open and the clutches K 1 , K 2 , K 3 are locked. The transmission ratio relationship i is 1.000. In order to present the sixth forward gear V 6 , the brake B 2 and the clutches K 1 and K 3 are locked. The transmission ratio relationship i is 0.808.

In order to present the seventh forward gear V 7 , the brake B 2 and the clutches K 1 and K 2 are locked. The transmission ratio relationship i is 0.704. In order to present the eighth forward gear V 8 , all of the brakes B 1 , B 2 and the clutch K 1 are locked. The transmission ratio relationship i is 0.600.

In order to present the ninth forward gear V 9 , the brake B 1 and the clutches K 1 and K 2 are locked. The transmission ratio relationship i is 0.503. In order to present the reverse gear R, the brake B 1 and the clutches K 2 and K 4 are locked. The transmission ratio relationship i is −3.454.

With the first alternative presentation VM I , the brake B 2 and the clutches K 1 and K 4 are locked. The transmission ratio relationship i is 1.267. With the second alternative presentation VM II , the brake B 1 and the clutches K 1 and K 4 are locked. The transmission ratio relationship i is 1.267. With the third alternative presentation VM III , all of the brakes are open and the clutches K 1 , K 3 and K 4 are locked. The transmission ratio relationship i is 1.267.

The gear jump φ between the first forward gear V 1 and the second forward gear V 2 is 1.741, and between the second forward gear V 2 and the third forward gear V 3 is 1.556. The gear jump φ between the third forward gear V 3 and the fourth forward gear V 4 is 1.316, and between the fourth forward gear V 4 and the fifth forward gear V 5 is 1.267. The gear jump φ between the fifth forward gear V 5 and the sixth forward gear V 6 is 1.236, and between the sixth forward gear V 6 and the seventh forward gear V 7 is 1.147. The gear jump φ between the seventh forward gear V 7 and the eighth forward gear V 8 is 1.173, and between the eighth forward gear V 8 and the ninth forward gear V 9 is 1.193. The entire gear jump is 8.977.

Thereby, the first planetary gear set GP 1 features a stationary transmission ratio of i0=−1.800, the second planetary gear set GP 2 features a stationary transmission ratio of i0=−1.609, the third planetary gear set GP 3 features a stationary transmission ratio i0=−1.500 and the fourth planetary gear set GP 4 features a stationary transmission ratio of i0=−1.500.

FIG. 3 shows a transmission in accordance with a second embodiment of the present invention.

FIG. 3 shows a transmission 1 in accordance with FIG. 1 . In FIG. 3 , two alternative positions A, B for the first clutch K 1 can be viewed, with which the first clutch K 1 can be arranged in a manner effectively equal to the position in accordance with FIG. 1 .

The first alternative position A for the first clutch K 1 is located between the ring gear 133 of the third planetary gear set GP 3 and the section of the output shaft AW that is connected to the fourth clutch K 4 .

The second alternative position B for the first clutch K 1 is located between the sun gear 103 of the third planetary gear set GP 3 and the section of the fifth shaft W 5 that connects the bar 122 of the second planetary gear set GP 2 to the ring gear 134 of the fourth planetary gear set GP 4 .

FIG. 4 shows a transmission in accordance with a third embodiment of the present invention.

FIG. 4 shows a transmission 1 in accordance with FIG. 1 . In FIG. 4 . alternative positions C for the second clutch K 2 can be viewed, with which the second clutch K 2 can be arranged in a manner effectively equal to the position in accordance with FIG. 1 .

The alternative position C for the second clutch K 2 is located between the ring gear 132 of the second planetary gear GP 2 and the section of the fourth shaft W 4 that connects the sun gear 101 of the first planetary gear set GP 1 to the brake B 2 .

FIG. 5 shows a transmission in accordance with a fourth embodiment of the present invention.

FIG. 5 essentially shows a transmission 1 in accordance with FIG. 1 . In contrast to the transmission 1 in accordance with FIG. 1 , with the transmission 1 in accordance with FIG. 5 , the first clutch K 1 , here designated with the reference sign K 1 ′, is now arranged at the first alternative position A in accordance with FIG. 3 . The first shaft W 1 is omitted. The drive shaft ANW now interacts directly with the bar 123 of the third planetary gear set GP 3 .

FIG. 6 shows a transmission in accordance with a fifth embodiment of the present invention.

FIG. 6 essentially shows a transmission 1 in accordance with FIG. 1 . In contrast to the transmission 1 in accordance with FIG. 1 , with the transmission 1 in accordance with FIG. 6 , the first clutch K 1 , here designated with the reference sign K 1 ″, is now arranged at the second alternative position B in accordance with FIG. 3 . The first shaft W 1 is omitted. The drive shaft ANW interacts directly with the bar 123 of the third planetary gear set GP 3 .

FIG. 7 shows a transmission in accordance with a sixth embodiment of the present invention.

FIG. 7 essentially shows a transmission 1 in accordance with FIG. 1 . In contrast to the transmission 1 in accordance with FIG. 1 , with the transmission 1 in accordance with FIG. 7 , the second clutch K 2 , here designated with the reference sign K 2 ′, is now arranged at the alternative position C in accordance with FIG. 4 . The second shaft W 2 is omitted. The drive shaft ANW interacts directly with the sun gear 102 of the second planetary gear set GP 2 .

FIG. 8 shows a transmission in accordance with a seventh embodiment of the present invention.

FIG. 8 essentially shows a transmission 1 in accordance with FIG. 7 . In contrast to the transmission 1 in accordance with FIG. 7 , with the transmission 1 in accordance with FIG. 8 , the first clutch K 1 , here designated with the reference sign K 1 ′, is now arranged at the first alternative position A in accordance with FIG. 3 . The first shaft W 1 and the second shaft W 2 are omitted. The drive shaft ANW now interacts directly with the sun gear 102 of the second planetary gear set GP 2 and the bar 123 of the third planetary gear set GP 3 .

FIG. 9 shows a transmission in accordance with an eighth embodiment of the present invention.

FIG. 9 essentially shows a transmission 1 in accordance with FIG. 7 . In contrast to the transmission 1 in accordance with FIG. 7 , the first clutch K 1 , here designated with the reference sign K 1 ″, is now arranged at the second alternative position B in accordance with FIG. 3 . The first shaft W 1 and the second shaft W 2 are omitted. The drive shaft ANW now interacts directly with the sun gear 102 of the second planetary gear set GP 2 and the bar 123 of the third planetary gear set GP 3 .

Overall, the transmission 1 in accordance with FIGS. 1 to 9 comprises four planetary gear sets GP 1 , GP 2 , GP 3 , GP 4 , six shift elements B 1 , B 2 , K 1 , K 2 , K 3 , K 4 , whereas the shift elements are designed in the form of at least four clutches and at least two brakes. Furthermore, a maximum of one fixed housing clutch is present. Finally, two shift elements to be shifted simultaneously are arranged.

As a start-up element for the transmission 1 , a hydrodynamic torque converter, a hydrodynamic clutch, an additional start-up clutch, an integrated start-up clutch or brake and/or an additional electrical motor can be arranged. An electrical motor or another power source is arranged at each of the six shafts W 1 to W 6 . Moreover, at each of the shafts W 1 to W 6 or each connection element, a freewheel is arranged for the housing G or for an additional shaft W 1 , W 2 , W 3 , W 4 , W 5 , W 6 . The transmission 1 may be preferentially incorporated into a motor vehicle in standard drive design or in front-transverse design. Frictional-locking or positive-locking shift elements are possible as shift elements. In particular, the clutch K 4 may be designed as a positive-locking shift element, in particular as a claw shift element, which leads to significant consumption advantages for a motor vehicle with an internal combustion engine provided with the transmission.

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

In summary, the present invention offers the advantage that low construction costs are required for the transmission, which results in lower manufacturing costs and a lower weight of the transmission. The transmission also provides a good transmission ratio sequence, low absolute and relative rotational speeds and low planetary set torques and shift element torques. Moreover, the present invention provides good gearing efficiency and very good accessibility of all of the shift elements, in particular regarding their maintenance.

Although the present invention was described above on the basis of preferred embodiments, it is not limited to them, but can be modified in many ways.

For example, the geometric position/order of the individual planetary gear sets GP 1 , GP 2 , GP 3 , GP 4 , and the individual shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 , K 1 ″, K 2 ′ may be freely selected under consideration of the binding ability of the respective transmission elements among each other. Individual transmission elements may be arbitrarily moved into their position within the transmission 1 .

It is also possible, taking into account binding ability, to convert individual or several planetary gear sets formed as negative planetary gear sets into positive planetary gear sets, with the simultaneous exchange of the bar connection and the ring gear connection and an increase in the stationary transmission ratio by 1.

Modifications and variations can be made to the embodiments illustrated or described herein without departing from the scope and spirit of the invention as set forth in the appended claims.

1 Transmission

GP 1 , GP 2 , GP 3 , GP 4 Planetary gear set

101 , 102 , 103 , 104 Sun gear

111 , 112 , 113 , 114 Planetary gear

121 , 122 , 123 , 124 Bar

131 , 132 , 133 , 134 Ring gear

ANW Drive shaft

AW Output shaft

B 1 , B 2 Brake

K 1 , K 2 , K 3 , K 4 , K 1 ′, K 1 ″, K 2 ′ Clutch

G Housing

V 1 , V 2 , V 3 , V 4 , V 5 , V 6 , V 7 ,

V 8 , V 9 , VM′, VM″, VM″ Forward gear

R Reverse gear

W 1 , W 2 , W 3 , W 4 , W 5 , W 6 Shaft

W 4 ″ Section of the shaft

i Transmission ratio/ratio

φ Gear jump/step

A, B, C Position of clutch