DE20320465U1 - Automatic gearing system for a vehicle has switching elements axially arranged between two planetary wheel set - Google Patents

Abstract

Automatic gearing system has switching elements (B, E) axially arranged between two planetary wheel set (RS1, RS2). Preferred Features: The planetary wheel sets are completely penetrated in the axial direction by only one shaft. A lamella packet (500) of the switching element (E) is arranged on a larger diameter than the lamella packet (200) of the switching element (B).

Description

The The present invention relates to a multi-stage automatic transmission with at least three Individual planetary gearsets and at least five Switching elements, according to the preamble of claim 1.

Automatic transmissions with several gears that can be shifted without group shifting are widely known. From the DE 199 12 480 A1 For example, a generic automatic transmission with three single-web planetary gear sets as well as three brakes and two clutches for shifting six forward gears and one reverse gear is known, which has very well-suited ratios for motor vehicles with a high overall spread and cheap increments as well as a high starting ratio in the forward direction. The individual gears are achieved by selectively closing two of the six shift elements, so that only one shift element is opened and another shift element is closed to switch from one gear to the next higher or next lower gear from the shift elements just actuated.

there is a drive shaft of the automatic transmission with a sun gear constantly second planetary gear set connected. Furthermore, the drive shaft is over the first clutch with a sun gear of the first planetary gear set and / or about the second clutch can be connected to a web of the first planetary gear set. additionally or alternatively, the sun gear of the first planetary gear set is over the first brake with a housing of the automatic transmission and / or the web of the first planetary gear set on the second brake with the housing and / or a sun gear of the third planetary gear set via the third brake with the casing connectable.

For the kinematic coupling of the individual planetary gear sets with each other, the DE 199 12 480 A1 two different versions. In the first version it is provided that an output shaft of the automatic transmission is constantly connected to a web of the third planetary gear set and a ring gear of the first planetary gear set, and that the web of the first planetary gear set is constantly connected to a ring gear of the second planetary gear set and a web of the second planetary gear set a ring gear of the third planetary gear set is connected. The drive shaft and the output shaft can be arranged coaxially to one another on opposite sides of the gear housing, as well as axially parallel on the same side of the gear housing. In the second version it is provided that the output shaft is permanently connected to the web of the second planetary gear set and the ring gear of the first planetary gear set, that the web of the first planetary gear set is continuously connected to the ring gear of the third planetary gear set, and that the ring gear of the second planetary gear set is always connected is connected to the web of the third planetary gear set. Such a design is particularly suitable for a coaxial arrangement of input and output shafts.

With regard to the spatial arrangement of the planetary gear sets DE 199 12 480 A1 propose to coaxially arrange the three planetary gear sets next to each other, the second planetary gear set being arranged axially between the first and third planetary gear sets. With regard to the spatial arrangement of the individual switching elements relative to each other and relative to the planetary gear sets DE 199 12 480 A1 before, always arrange the first and second brakes directly next to each other, the second brake always directly axially adjacent to the first planetary gear set, and the third brake always on the side of the third planetary gear set facing away from the first planetary gear set, and always arrange the two clutches directly next to each other , In a first arrangement variant, both clutches are arranged on the side of the first planetary gear set facing away from the third planetary gear set, the first clutch being axially directly adjacent to the first brake and being arranged closer to the first planetary gear set than the second clutch. In connection with a non-coaxial position of the input and output shafts, it is proposed in a second arrangement variant that both clutches are arranged on the side of the third planetary gear set facing away from the first planetary gear set, the second clutch being arranged closer to the third planetary gear set than the first clutch and axially adjacent to an output spur gear operatively connected to the output shaft, which in turn is arranged on the side of the third brake facing away from the third planetary gear set.

The present invention is based, for which from the prior art DE 199 12 480 A1 known automatic transmissions to represent alternative component arrangements with the most compact possible gear construction. Preferably, the automatic transmission should be able to be used in a motor vehicle with a non-coaxial transmission input and transmission output shaft, but it should also be possible to use it in a motor vehicle with a standard drive and coaxial arrangement of the transmission input and transmission output shaft by means of comparatively simple modifications.

Is solved according to the invention the task through a multi-stage automatic transmission with the features of claim 1. Advantageous refinements and developments the invention emerge from the subclaims.

Starting from the generic state of the art of DE 199 12 480 A1 , The multi-stage automatic transmission according to the invention has at least three coupled single planetary gear sets which are arranged coaxially to one another, the second planetary gear set always being spatially arranged between the first and third planetary gear sets. Furthermore, the automatic transmission according to the invention has at least five shift elements. A sun gear of the third planetary gear set can be fixed to a transmission housing of the automatic transmission via the first switching element designed as a brake. A drive shaft of the automatic transmission is permanently connected to a sun gear of the second planetary gear set. Furthermore, the drive shaft can be connected to a sun gear of the first planetary gear set via the second switching element designed as a clutch and additionally or alternatively via the fifth switching element designed as a clutch to a web of the first planetary gear set. Alternatively, the sun gear of the first planetary gear set can be fixed to the transmission housing via the third switching element designed as a brake and / or the web of the first planetary gear set can be fixed via the fourth switching element designed as a brake. If the second and fifth switching elements are actuated simultaneously, then the sun gear and the web of the first planetary gear set are connected to one another.

A The output shaft of the multi-stage automatic transmission is always with a ring gear of the first planetary gear set, wherein the ring gear of the first planetary gear set additionally either with a web of the third planetary gear set or a web of the second planetary gear set is.

As with the generic DE 199 12 480 A1 , the web of the first planetary gear set (depending on the gear set concept) is either either permanently connected to the ring gear of the second planetary gear set or permanently to the ring gear of the third planetary gear set. If the ring gear of the first planetary gear set and the web of the third planetary gear set and the output shaft are coupled to one another, the web of the second planetary gear set is continuously connected to a ring gear of the third planetary gear set and the web of the first planetary gear set is continuously connected to a ring gear of the second planetary gear set. If the ring gear of the first planetary gear set and the web of the second planetary gear set and the output shaft are coupled to one another, the web of the third planetary gear set is constantly connected to the ring gear of the second planetary gear set and the web of the first planetary gear set is continuously connected to the ring gear of the third planetary gear set.

In contrast to the generic DE 199 12 480 A1 According to the invention, both the fifth shift element, via which the drive shaft can be connected to the web of the first planetary gear set, and the second shift element, via which the drive shaft can be connected to the sun gear of the first planetary gear set, are seen spatially axially between the first and second planetary gear sets arranged. The second and third planetary gear sets are arranged axially next to one another. Preferably, a disk pack of the fifth switching element is arranged on a larger diameter than a disk pack of the second switching element.

The first planetary gear set is only in the axial direction of at most a wave - in particular the drive shaft of the automatic transmission - fully penetrated centrally. Accordingly, the second, middle planetary gear set is at most of a wave - in particular the drive shaft - in axial Pass through direction centrally.

In an advantageous embodiment of the invention form the second and fifth Switching element a preassembled module, which the respective Plate packs and the respective servo devices of these two Switching elements (clutches) and one for these two switching elements (Couplings) common plate carrier comprises. The servo device of the second switching element can be spatially seen both on the side facing the first planetary gear set of the plate pack assigned to it (the second switching element) be arranged, as well as on the second planetary gear set Side of the slat package assigned to it. The servo device too the fifth Switching element can be spatially seen both on the side facing the first planetary gear set the plate pack assigned to it (the fifth switching element) be, as well as on the side facing the second planetary gear set of the plate pack assigned to it.

In a further, length-saving embodiment of the invention, which is particularly advantageous in the case of a non-coaxial arrangement of the input and output shafts of the automatic transmission, it is proposed that the fourth switching element, via which the web of the first planetary gear set can be fixed, and the third switching element, via which the Sun gear of the first planetary gear set can be fixed, spatially arranged in an area radially above the planetary gear sets. Advantageously, the third and fourth switching elements can form a preassembled assembly with an outer disk carrier common to these two switching elements (brakes), which receives the disk packs of these two switching elements (brakes) and in the at least parts of the servo devices of these two switching elements (brakes) are tegrated. Of course, the outer disk carriers of the third and / or fourth switching element can also be integrated directly into the gear housing.

ever according to the radial installation space that is available in the motor vehicle for the automatic transmission the third switching element but also on the side of the first planetary gear set be arranged, which is opposite the second planetary gear set, in particular immediately adjacent to an outer wall of the gear housing.

In Another embodiment of the invention is the first switching element, via which the sun gear of the third planetary gear set can be fixed spatially arranged on the side of the third planetary gear set, which the second planetary gear set is opposite. But it can also be provided that the first switching element is seen spatially radially over in an area the third planetary gear set is arranged, for example together with the fourth switching element as a preassembled module that one for these two switching elements (brakes) common outer disk carrier and the disk packs of these two switching elements (brakes) and at least (integrated in the common outer disk carrier) Parts of the servo devices of these two switching elements (brakes) includes. Of course can the outer disk carrier of the first switching element also directly in the gear housing or in a housing cover, the one outer wall of the automatic transmission forms, be integrated.

For the application with mutually non-coaxial input and output shafts, in particular for applications with input and output shafts arranged axially parallel or at an angle to each other, it is proposed that the first switching element be adjacent to a outer wall of the gearbox and a spur gear or chain drive seen spatially axially between to arrange the third planetary gear set and the first switching element. Then there is a first spur gear of the spur gear or a first Sprocket of the chain drive with the ring gear of the first planetary gear set and ever according to the wheelset concept - either connected to the web of the third or the second planetary gear set. A further spur gear of the spur gear or a second sprocket of the chain drive with the output shaft of the automatic transmission connected. A servo device and / or a slat carrier of the first switching element designed as a brake in an outer wall or a housing-fixed Cover of the gearbox be integrated.

In another embodiment of the spur gear or chain drive arrangement But it can also be provided that the first switching element at least partially axially next to the third planetary gear set on the second planetary gear set opposite Side is arranged, and that the spur gear or chain drive spatially seen on the other side of the first switching element (i.e. on the opposite side of the first planetary gear set Switching element) is arranged. One then intervenes the ring gear of the first planetary gear set and the web of the third or second planetary gear connected hub of the first spur gear Spur gear or the first sprocket of the chain drive the sun gear of the third planetary gear set in the axial direction. at Such an arrangement can be the first designed as a brake Switching element spatially seen next to the fourth switching element also designed as a brake be arranged, in which case preferably the same lamella diameter for this two switching elements is provided (same parts concept).

In a further embodiment of the spur gear or chain drive arrangement can also be provided that the first switching element seen spatially at least largely radially across the third planetary gear set and that the spur gear or chain drive spatially seen on the side opposite the second planetary gear set of the third planetary gear set axially to the third planetary gear set and adjoins the first switching element.

For the application with coaxial input and output shaft it is proposed that the output shaft of the automatic transmission is arranged next to the third planetary gear set first switching element and the sun gear of the third planetary gear set passes through centrally in the axial direction and spatially seen in the axial area between the second and third planetary gear sets with the web of the third or second planetary gear set is connected.

The nesting of the five shift elements and three individual planetary gear sets according to the invention spatially results in an overall very compact transmission structure. The pressure medium supply to the servo devices of all five switching elements is comparatively simple to construct. The pressure medium for actuating the two rotating clutches (second and fifth switching element) can be introduced in a simple manner via only one rotating shaft. Correspondingly, the lubricant for dynamic pressure compensation of the two rotating clutches (second and fifth switching element) can also be introduced in a simple manner via only one rotating shaft. The essential features of the proposed automatic transmission relevant to the invention bes can be combined with a non-coaxial - in particular axially parallel or angular - arrangement of the transmission input and transmission output shaft, as well as with a coaxial arrangement of the transmission input and transmission output shaft.

Due to the described kinematic coupling of the individual gear set elements with one another and with the input and output shaft via the five switching elements, as in the prior art, the DE 199 12 480 A1 - A total of six forward gears can be switched such that when switching from one gear to the next higher or next lower gear, only one switching element is opened and another switching element is closed by the switching elements just actuated.

The The invention is explained in more detail below with reference to the figures, with similar ones Elements also with similar ones Reference numerals are provided. Show it

1 a transmission scheme according to the prior art;

2 a circuit diagram of the transmission according 1 ;

3 an exemplary first schematic component arrangement according to the invention;

4 an exemplary second schematic component arrangement according to the invention;

5 an exemplary third schematic component arrangement according to the invention;

6 an exemplary fourth schematic component arrangement according to the invention;

7 an exemplary fifth schematic component arrangement according to the invention;

8th an exemplary sixth schematic component arrangement according to the invention;

9 an exemplary seventh schematic component arrangement according to the invention;

10 an exemplary eighth schematic component arrangement according to the invention; and

11 an exemplary ninth schematic component arrangement according to the invention.

To clarify the component arrangements according to the invention, in 1 First, a transmission diagram of a multi-stage automatic transmission for a motor vehicle with a standard drive is shown, as in the prior art DE 199 12 480 A1 known. AN denotes a drive shaft of the automatic transmission that is operatively connected to a drive motor (not shown) of the automatic transmission, for example via a torque converter or a starting clutch or a torsion damper or a dual-mass flywheel or a rigid shaft. AB is an output shaft of the automatic transmission, which is operatively connected to at least one drive axle of the motor vehicle. In the illustrated embodiment, drive shaft AN and output shaft AB are arranged coaxially with one another. RS1, RS2 and RS3 designate three coupled single planetary gear sets, which are arranged side by side in a row in a gearbox GG. All three planetary gear sets RS1, RS2, RS3 each have a sun gear SO1, SO2 and SO3, a ring gear HO1, HO2 and HO3, as well as a web ST1, ST2 and ST3 with planet gears PL1, PL2 and PL3, each with sun and Comb the ring gear of the corresponding gear set. A to E denote five shift elements, the first, third and fourth shift elements A, C, D being designed as a brake and the second and fourth shifting elements B, E being designed as a clutch. The respective friction linings of the five shift elements A to E are as disk packs 100 . 200 . 300 . 400 and 500 (each with outer and inner slats or steel and covering slats) indicated. The respective input elements of the five switching elements A to E are included 120 . 220 . 320 . 420 and 520 referred to, the respective output elements of the couplings B and E. 230 and 530 , The kinematic connection of the individual gear set elements and shift elements relative to one another and relative to the input and output shaft has already been described in detail at the beginning, as has the spatial arrangement of these components.

As from the circuit diagram in 2 can be seen, by selective switching of two of the five shift elements A to E six forward gears can be shifted without group shifting, i.e. such that only one shift element is opened and one shifted from one shift into the next higher or next shift gear from the shift elements just actuated further switching element is closed. In the first gear "1", the brakes A and D are closed, in the second gear "2" the brakes A and C, in the third gear "3" brake A and clutch B, in the fourth gear "4" brake A and clutch E, in fifth gear "5" clutches B and E, and in sixth gear "6" brake C and clutch E. In reverse gear "R" clutch B and brake D are closed.

Based on 3 to 11 nine examples of a component arrangement according to the invention will now be explained in detail, for example in FIG Connection with non-coaxial arrangement of input and output shafts.

3 now shows a first schematic component arrangement, exemplary of the solution of the task according to the invention. Starting from the previously described prior art DE 199 12 480 A1 The multi-stage automatic transmission according to the invention has three coupled single planetary gear sets RS1, RS2, RS3 arranged coaxially to one another. Spatially speaking, the second planetary gear set RS2 is arranged axially between the first and third planetary gear sets RS1, RS3 and is axially directly adjacent to the third planetary gear set RS3. Furthermore, the automatic transmission according to the invention has five shift elements A to E. The first, third and fourth shift elements A, C, D are each designed as brakes (in the example each as multi-plate brakes), the second and fifth shift elements B, E each as a clutch (in the example each as multi-plate clutches). A sun gear SO3 of the third planetary gear set RS3 can be fixed via the brake A to a gear housing GG of the automatic transmission. A drive shaft AN of the automatic transmission is constantly connected to a sun gear SO2 of the second planetary gear set RS2. Furthermore, the drive shaft AN can be connected via the clutch B to a sun gear SO1 of the first planetary gear set RS1 and additionally or alternatively via the clutch E to a web ST1 of the first planetary gear set RS1. Alternatively, the sun gear SO1 of the first planetary gear set RS1 can be fixed on the gear housing GG via the brake C and / or the web ST1 of the first planetary gear set RS1 via the brake D.

A Output shaft AB of the multi-stage automatic transmission is always with a ring gear HO1 of the first planetary gear set RS1, this ring gear HO1 in the exemplary coupling shown of the wheelset elements also constantly with a web ST3 of the third planetary gear set RS3 is connected. Furthermore, a web ST2 of the second planetary gear set RS2 is always with a ring gear HO3 of the third planetary gear set RS3, and the web ST1 of the first planetary gear set RS1 with a ring gear HO2 of the second planetary gear set RS2. The corresponding connector between the ring gear HO1 of the first planetary gear set RS1 and the web ST3 of the third planetary gear set RS3 is designed as a cylinder ZYLRS13. This cylinder ZYLRS13 is on the one hand with the ring gear HO1 over a suitable operative connection, for example via a Weldment and extends in the axial direction from the ring gear HO1 over the Ring gear HO3 over. On the other hand, the cylinder ZYLRS13 is on the second planetary gear set Side of the third planetary gear set RS3 facing away from RS2 via a suitable operative connection with a web plate STB3 of the web ST3 connected, for example via a take-away profile. The cylinder ZYLRS13 overlaps the second and third planetary gear sets RS2, RS3 completely.

In the in 3 In the illustrated embodiment, the input shaft AN and the output shaft AB are not arranged coaxially with one another. A spur gear STST is provided as an example for the operative connection between the output shaft AB and the web ST3 of the third planetary gear set RS3 (and the ring gear HO1 of the first planetary gear set RS1 connected to this web ST3). As already mentioned, the cylinder ZYLRS13 completely overlaps the third planetary gear set RS3 in the axial direction. The cylinder ZYLRS13 is connected to the web ST3 on the side of the third planetary gearset RS3 facing away from the second planetary gearset RS2. The web plate of the web ST3 facing the second planetary gear set RS2 is designated STB3 and extends radially inward to a diameter close to the drive shaft AN. The web plate STB3 is connected to a web shaft STW3 on its inside diameter. Starting from the web plate STB3, this web shaft STW3 extends in the opposite direction to the second planetary gear set RS2 coaxially to the drive shaft AN and radially above the drive shaft AN and thereby engages centrally through the sun gear SO3 of the third planetary gear set RS3. On the side of the third planetary gearset RS3 opposite the second planetary gearset RS3, the web shaft STW3 is connected to a first spur gear STR1 of the spur gear stage STST and is mounted on a hub GN fixed to the transmission housing. The web shaft STW3 thus forms the hub of this first spur gear STR1. The sun gear SO3 of the third planetary gear set RS3 is expediently mounted on the web shaft STW3.

All three planetary gear sets RS1, RS2 and RS3 are completely penetrated centrally in the axial direction by the drive shaft AN. In the in 3 The example shown is a drive motor (not shown here for the sake of simplicity) which is operatively connected to the drive shaft AN on the transmission side facing away from the first planetary gear set RS1. Out 3 But it is also easy to see that - in connection with the non-coaxial arrangement of the drive shaft AN and drive shaft AN - the drive motor can be arranged on both end faces of the transmission.

The brake A, by means of which the sun gear SO3 of the third planetary gearset RS3 can be fixed, is spatially located partially radially above the third planetary gearset RS3 and partially on the side of the third planetary gearset RS3 facing away from the second planetary gearset RS2. An input element designed as an inner disk carrier borders 120 brake A axially the web ST3 of the third planetary gear set RS3 on its side facing away from the second planetary gear set RS2. A slat package 100 The brake A with outer and lining plates is arranged on a large diameter in the area of the cylindrical outer wall of the gear housing GG, viewed in the axial direction radially above the third planetary gear set RS3. A suitable driving profile for the outer plates of the plate pack 100 can be easily integrated into the GG gearbox. Of course, a separate outer disk carrier can also be provided for the brake A, which is then connected to the gear housing GG in a form-fitting, force-fitting or material-locking manner by suitable means. On the side of the inner disk carrier facing away from the third planetary gear set RS3 ( 120 ) of brake A, spur gear STR1 axially borders a disk-shaped section of this inner disk carrier ( 120 ) immediately.

Also on the side of the third planetary gearset RS3 facing away from the second planetary gearset RS2, seen in the axial direction in the area between the spur gear STR1 and planetary gearset RS3, viewed in the radial direction in the area of the cylindrical outer wall of the gear housing GG, is a servo device 110 brake A to actuate the plates 100 easily integrated into the gearbox housing GG and a housing wall GW connected (for example screwed) to the gearbox housing GG. Of course, this housing wall can also be designed as part of the transmission housing, that is to say as a housing section of radial extension. Housing wall GW and gear housing GG have a corresponding piston chamber (pressure chamber), in which a pressurizable piston (not shown here for simplification) of the servo device can be pressurized 110 is displaceably mounted, and a corresponding (also not shown here) pressure medium supply to this piston chamber. When this piston chamber is pressurized, the piston of the servo device actuates 110 the slats 100 the brake A axially in the direction of the three planetary gear sets RS1, RS2, RS3. It is clear to the person skilled in the art that the spatial position of the servo device 110 and / or slats 100 the brake A, especially in the axial direction, is not seen in the 3 example shown is limited. So servo equipment 110 and / or slats 100 the brake A, for example, can also be arranged on a smaller diameter in the area axially between the spur gear stage STST and the planetary gear set RS3, or also shifted axially in the direction of the planetary gear set RS1, for example in a region above the second planetary gear set RS2 or the first planetary gear set RS1.

The clutch B, via which the drive shaft AN can be connected to the sun gear SO1 of the first planetary gear set RS1, and the clutch E, via which the drive shaft AN can be connected to the web ST1 of the first planetary gear set RS1, are spatially between the first and second planetary gear sets RS1, RS2 arranged. The clutch E is arranged radially above the clutch B when viewed in the axial direction. The slats loaded with the full drive torque of the drive motor 500 the clutch E therefore have a larger diameter than the plates 200 the clutch B and are thus arranged on a comparatively large diameter radially below the cylinder ZYLRS13.

In the in 3 In the example shown, a common disk carrier ZYLBE is provided for both clutches B, E, which has an outer disk carrier (input element 220 the clutch B) and on the other hand for clutch E an inner plate carrier (input element 520 the clutch E) forms. As in 3 indicated, are the outer plates of the plate pack 200 and the inner plates of the plate pack 500 here preferably designed as steel fins, the inner fins of the plate pack 200 and the outer plates of the plate pack 500 accordingly as covering slats.

The plate carrier ZYLBE common to the two clutches B, E is designed as a pot open in the direction of the first planetary gearset RS1, with a disk-shaped pot bottom which axially adjoins the web ST2 of the second planetary gearset RS2 and is connected at its inner diameter to the drive shaft AN is. The cylindrical section of the disk carrier ZYLBE, which extends axially in the direction of the first planetary gear set RS1, has a suitable driving profile for the inner disks of clutch E on its outer diameter and a suitable driving profile for the outer disks of clutch B on its inner diameter. Seen spatially, the driving profile for the inner plates of clutch E is arranged closer to the second planetary gear set RS2 than the driving profile for the outer plates of clutch B. The plate set is also corresponding 500 clutch E is closer to the second planetary gear set RS2 than the disk pack 200 the clutch B. The part of the cylindrical section of the disk carrier ZYLBE with the driving profile for the inner disks of clutch E thus forms the input element together with the disk-shaped pot bottom of the disk carrier ZYLBE 520 of clutch E. Accordingly, the part of the cylindrical section of the disk carrier ZYLBE with the driving profile for the outer disks of clutch B forms the input element 220 the clutch B. The input element 220 the clutch B is consequently via the input element 520 coupling E is connected to drive shaft AN the.

A servo device 210 The clutch B is spatially arranged within the cylinder space of the disk carrier ZYLBE, on the one hand, at least in sections, axially directly adjoins the disk-shaped section (pot bottom) of the disk carrier ZYLBE, on the other hand, spatially, at least in sections, it is also radially below the disk pack 500 the clutch E arranged. The servo device 210 includes at least one pressure chamber (not shown here for simplification) and a piston (also not shown here). When this pressure chamber is pressurized, this piston actuates the plate pack 200 in a known manner against a restoring force of a restoring element of the servo device (likewise not shown here) 210 axially in the direction of the first planetary gear set RS1. Since the disk carrier ZYLBE always rotates at the speed of the drive shaft AN, it is advisable that the servo device 210 also has a dynamic pressure compensation to compensate for the rotary pressure of the pressure chamber of the servo device rotating at the drive shaft speed 210 ,

An output element 230 the clutch B is designed here as a disk-shaped inner disk carrier, which, starting from a suitable driving profile for receiving the inner disks of the clutch B, axially adjacent to the servo device 210 , extends radially inwards up to a sun wave SOW1 to which it is connected. This sun shaft SOW1 is mounted on the drive shaft AN and extends - coaxially to the drive shaft AN - axially initially in the direction of the first planetary gear set RS1 and is connected to the sun gear SO1 of the first planetary gear set RS1. In this axial section, the sun shaft SOW1 thus forms the hub of the inner disk carrier ( 230 ) of the clutch B. In the further axial course, the sun shaft SOW1 completely grips the first planetary gear set RS1 centrally and extends axially up to a housing cover GD which is connected (for example screwed) to the transmission housing GG and forms an end wall of the transmission. Of course, housing cover GD and gear housing GG can also be made in one piece. On the side of the first planetary gear set RS1 facing away from the clutch B, a web plate STB11 of the web ST1 is mounted on the sun shaft SOW1. On the additional kinematic connection of the output element 230 clutch B to brake C will be discussed in detail later.

A servo device 510 the coupling E is spatially above the input element 220 the clutch B arranged. To accommodate this servo device 510 the disk carrier ZYLBE has a further cylinder space which, viewed in the axial direction, is arranged at least predominantly radially above the part of the cylindrical section of the disk carrier ZYLBE with the driving profile for the outer disks of clutch B. The servo device 510 includes at least one pressure chamber (not shown here for simplification) and a piston (also not shown here). When this pressure chamber is pressurized, this piston actuates the plate pack 500 in a known manner against a restoring force of a restoring element of the servo device (likewise not shown here) 210 axially in the direction of the second planetary gear set RS2. Since the disk carrier ZYLBE always rotates at the speed of the drive shaft AN, it is advisable that the servo device 510 has a dynamic pressure compensation to compensate for the rotary pressure of the pressure chamber of the servo device rotating at the drive shaft speed 510 ,

An output element 530 the clutch E is designed here as a disk-shaped outer disk carrier, which, starting from a suitable driving profile for receiving the outer disks of the clutch E, axially adjacent to the servo device 510 , extends radially outwards to a cylinder ZYLRS12 to which it is connected. This cylinder ZYLRS12 forms the kinematic connection between the web ST1 of the first planetary gear set RS1 and the ring gear HO2 of the second planetary gear set RS2, is spatially arranged below the cylinder ZYLRS13 and extends in the axial direction from the ring gear HO2 to the web plate facing the planetary gear set RS2 STB12 of the bridge ST1. In principle, this cylinder ZYLRS12 can also be interpreted as part of the output element of clutch E.

As in 3 Also visible are the brake C, via which the sun gear SO1 of the first planetary gear set RS1 can be fixed to the gear housing GG, and the brake D, via which the web ST1 of the first planetary gear set RS1 (and the ring gear HO2 of the second connected to this web ST1 Planetary gearset RS2) can be fixed on the gearbox housing GG, arranged side by side, spatially seen radially above the planetary gearset on a comparatively large diameter in the area of the inner diameter of the gearbox housing GG. The slat package borders 400 the brake D axially to the disk pack 100 the brake A on and is here, for example, spatially arranged in a region radially above the two immediately adjacent planetary gear sets RS2 and RS3. The slat package 300 the brake C is seen here spatially as an example arranged in a region radially above the planetary gear set RS2 and the clutch E directly adjacent to it. The brake G is thus arranged closer to the first planetary gear set RS1 than the brake D, or the brake D is arranged closer to the third planetary gear set RS3 than the brake C.

In the in 3 In the example shown, the gearbox housing GG simultaneously takes on the function of an outer disk carrier for both brakes C, D. In another design, separate outer disk carriers for the brakes C, D can of course also be provided, which are then connected in a rotationally fixed manner to the gearbox housing by suitable means, or also an outer disk carrier common to both brakes C, D.

The plate packs 400 . 300 assigned servo devices 410 . 310 are axially next to each other axially between these two plate packs 400 . 300 arranged. In the in 3 The example shown are the two servo devices 410 . 310 into a common component fixed to the gearbox housing with corresponding piston chambers (pressure chambers), in each of which at least one displaceably mounted pressurizable piston of the respective servo device 310 respectively. 410 is arranged, integrated. With a pressure medium supply to the piston chamber of the servo device 410 the piston actuates the plate pack 400 the brake D axially in the direction of the brake A or the third planetary gear set RS1 or in the opposite direction to the first planetary gear set RS1. The piston of the servo device operates accordingly 310 with a pressure medium supply to the piston chamber of the servo device 310 the plate pack 300 the brake C axially in the direction of the first planetary gear set RS1. It is easy for the expert to see that the pressure medium supply to these two servo devices 310 . 410 is comparatively simple.

With a suitable design, the two servo devices 410 . 310 can also be integrated directly into the gearbox. If, for example, a common outer disk carrier is provided as a separate component for the two brakes C, D, the servo devices can 410 . 310 can also be integrated in a simple manner in this outer disk carrier, so that in this case a preassembled assembly which is favorable in terms of production technology results.

As in 3 further indicated, the component arrangement described here enables a common parts concept at least for the slats 300 . 400 and possibly also for the servo devices of brakes C and D, but also for the disks 100 . 300 . 400 all three brakes A, C and D of the automatic transmission.

A with 420 The designated input element of the brake D is designed as a cylindrical inner disk carrier, which spatially extends in sections spatially above the cylinder ZYLRS13, radially overlapping the first and second planetary gear sets RS1, RS2 in the axial direction, and on the side of the first planetary gear set facing away from the second planetary gear set RS2 RS1 is connected to the web ST1 of the first planetary gear set RS1. The corresponding web plate of the web ST1 opposite the second planetary gear set RS2 is designated STB11. To support the inner disk carrier ( 420 ) of the brake D, the web plate STB11 is mounted on the sun shaft SOW1.

A with 320 The designated input element of the brake C is designed as a cylindrical inner disk carrier, which spatially, in sections, extends radially above the cylindrical section of the inner disk carrier overlapping the cylinder ZYLRS13 ( 420 ) extends the brake D, radially engaging over the first planetary gearset RS1 and the two clutches B, E in the axial direction, and is connected to the sun shaft SOW1 on the side of the web plate STB11 of the first planetary gearset RS1 facing away from the second planetary gearset RS2. The disc-shaped cylinder bottom of the inner disk carrier ( 320 ) the brake C adjoins the housing cover GD, which - as already described - forms an outer wall of the automatic transmission.

In order to adapt the outer contour of the transmission housing to an installation space that is actually available for the automatic transmission, the spatial position of the two brakes D, C can of course also be in the axial direction compared to that in FIG 3 shown example may be shifted.

By in 3 Component arrangement shown is a spatially overall slim gear structure achieved. Since the drive shaft penetrates the entire gearbox in the axial direction, the in 3 Component arrangement shown with non-coaxial position of the input and output shaft for the person skilled in the art can also be reconstructed in a structurally simple manner for an application with input and output shaft running coaxially to one another.

The circuit diagram of the multi-stage automatic transmission according to 3 corresponds to that in 2 shown circuit diagram. As with the prior art DE 199 12 480 A1 are selectively shiftable from two of the five shift elements, so six forward gears can be shifted freely.

Based on 4 to 8th Five further component arrangements according to the invention are explained in more detail below, all with the first component arrangement according to FIG 3 unchanged kinematic coupling of the planetary gear set elements to each other and to the shifting elements, all also with an assembly consisting of clutches B and E, which is spatially arranged axially between the first and second planetary gear sets RS1, RS2, with clutch B always seen radially below the Coupling E and is arranged in a coupling space formed by this coupling E.

4 now shows a second schematic component arrangement, exemplary of the solution of the task according to the invention. The main differences from the first component arrangement according to 3 are the structural design of the assembly with the two clutches B, E and the spatial arrangement of the servo devices of the three brakes A, C and D relative to their disk packs.

As in 4 can be seen, the assembly of the two clutches B, E comprises a disk carrier ZYLBE, a radially inner disk pack 200 with servo device 210 clutch B, as well as a radially outer plate pack 500 with servo device 510 the clutch E. In contrast to 3 are the outer plates of both plate packs 200 . 500 preferably designed as steel fins, the inner fins of both sets of plates 200 . 500 accordingly as covering slats. The disk carrier ZYLBE is now designed as a pot-shaped double cylinder, with a disk-shaped pot base, which is connected to the drive shaft AN at its inner diameter, and with two mutually independent cylindrical sections, both of which extend axially from the pot base in the direction of the first planetary gear set. The diameter of the first of these two cylindrical sections is preferably somewhat larger than the web diameter of the adjacent planetary gear sets RS1 and RS2. The diameter of the second of these two cylindrical sections corresponds approximately to the ring gear diameter of the adjacent planetary gear sets RS1 and RS2, but is in any case smaller than the diameter of the cylinder ZYLRS12, which is known to be the operative connection between the ring gear of the second planetary gear set RS2 and the web of the first planetary gear set RS1 forms. The disk carrier ZYLBE is the input element for both clutches B, E 220 respectively. 520 and for both clutches B, E the outer disk carrier. Correspondingly, the (radially inner) first cylindrical section of the disk carrier ZYLBE has a suitable driving profile for the outer disks of the disk pack on its inside diameter 200 the clutch B, and the (radially outer) second cylindrical section of the disk carrier ZYLBE has a suitable driving profile for the outer disks of the disk pack on its inside diameter 500 the clutch E. Spatially seen is the plate pack 500 at least largely radially above the disk pack 200 arranged.

The servo device 210 The clutch B is spatially arranged within the cylinder space of the disk carrier ZYLBE, which is formed by the (radially inner) first cylindrical section of the disk carrier ZYLBE and, at least in sections, axially directly adjoins the disk-shaped section (cup base) of the disk carrier ZYLBE. The servo device 210 includes at least one pressure chamber (not shown here for simplification) and a piston (also not shown here). When this pressure chamber is pressurized, this piston actuates the plate pack 200 the clutch B in a known manner against a restoring force of a restoring element of the servo device (likewise not shown here) 210 axially in the direction of the first planetary gear set RS1.

The servo device 510 the clutch E is spatially arranged within the cylindrical annulus of the disk carrier ZYLBE, which is formed by the (radially outer) second cylindrical section of the cylinder ZYLBE and is limited inwards by the (radially inner) first cylindrical section of the disk carrier ZYLBE. Like the servo device 210 limits the servo device 510 at least in sections axially directly on the disc-shaped section (pot bottom) of the disk carrier ZYLBE. The servo device 510 includes at least one pressure chamber (not shown here for simplification) and a piston (also not shown here). When this pressure chamber is pressurized, this piston actuates the plate pack 500 the clutch E in a known manner against a restoring force of a restoring element of the servo device (likewise not shown here) 510 axially in the direction of the first planetary gear set RS1.

Since the disk carrier ZYLBE always rotates at the speed of the drive shaft AN, it is advisable that both servo devices 210 and 510 also have a dynamic pressure compensation to compensate for the rotary pressure of the pressure chambers of these servo devices rotating with the drive shaft speed 210 respectively. 510 ,

An output element 230 clutch B is - as in 3 - Designed as a disc-shaped inner disk carrier, which is based on a suitable driving profile for receiving the inside slats of the slat package 200 the clutch B, axially adjacent to the servo device 210 the clutch B, extends radially inwards up to a sun shaft SOW1 mounted on the drive shaft AN. As in 3 this sun shaft SOW1 passes through the first planetary gear set RS1 centrally and is connected to the inner disk carrier ( 230 ) of the clutch B, as well as with the sun gear SO1 of the first planetary gear set RS1 and the input element 320 the brake C.

An output element 530 the clutch E is - in contrast to 3 - Designed as an inner disk carrier. Starting from a suitable driving profile for holding the inner plates of the plate pack 500 the coupling E, axially adjacent to the servo device 510 the clutch E, this inner disk carrier extends ( 530 ) on a diameter above the (radially inner) first cylindrical section of the disk carrier ZYLBE axially in the direction of the first planetary gear set RS1 up to the web plate STB12 of the first planetary gear set RS1 and is connected to this web plate STB12.

As in 4 still visible, the brakes A, D, C are similar to in 3 Spatially arranged on the inner diameter of the gearbox housing GG in a region radially above the two planetary gear sets RS3, RS2 and the clutch E, but with opposite 3 changed operating direction for all three servo devices 110 . 410 . 310 brakes A, D, C. Servo devices 110 the brake A and the servo device 410 the brake D are now arranged directly axially next to each other, axially between the disk packs 100 . 400 of the two brakes A, D and, for example, integrated into a common component fixed to the transmission housing. The slat package 100 The brake A is now at least partially seen in the axial direction next to the third planetary gear set RS3 on its side facing away from the second planetary gear set RS2, on a diameter larger than the ZYLRS13, which is known to be the operative connection between the web of the third planetary gear set RS3 and the ring gear of the first planetary gear set RS1 forms. The slat package 400 the brake D is spatially arranged approximately radially above the second planetary gear set RS2 and is closed by the servo device 410 actuated or pressed axially in the direction of the first planetary gear set RS1. The actuation direction of the servo device is correspondingly reversed axially 110 when closing the plate pack 100 the brake A. The disk pack 300 the brake C now borders axially directly on the disk set 400 the brake D and is also spatially arranged approximately radially above the second planetary gear set RS2. The servo device integrated into the GG gearbox is an example 310 the brake C spatially at least predominantly arranged radially above the clutch E and actuates the disk set 300 when closing axially in the direction of the adjacent brake D or in the opposite direction to the first planetary gear set RS1.

The input element 120 The brake A is now at least largely disc-shaped and extends in the radial direction parallel to the third planetary gear set RS3. The input elements 420 the brake D and 320 the brake C are opposite 3 basically unchanged.

5 now shows a third schematic component arrangement as an exemplary solution of the task according to the invention. Compared to the first component arrangement according to 3 Modified is the structural design of the assembly with the two clutches B, E in connection with a changed actuation direction of the clutch E, on the other hand, the spatial arrangement of the brake A relative to the third planetary gear set RS3 and the spur gear (spur gear STST).

As in 5 can be seen, the assembly of the two clutches B, E unchanged includes a plate carrier ZYLBE common to both clutches B and E, a radially inner plate pack 200 with servo device 210 clutch B, as well as a radially outer plate pack 500 with servo device 510 the clutch E. As in 3 The disk carrier ZYLBE forms the input element of both clutches B, E, the outer disk carrier of clutch B and the inner disk carrier of clutch E. As in 3 are the outer plates of the plate pack 200 and the inner plates of the plate pack 500 preferably designed as steel fins, the inner fins of the plate pack 200 and the outer plates of the plate pack 500 accordingly as covering slats.

The design of clutch B as the inner of the two clutches remains unchanged 3 accepted. In contrast to 3 is the direction of actuation of both servo devices 210 . 510 when closing the respective plate pack 200 respectively. 500 now the servo device 510 actuates the slats 500 now also axially in the direction of the first planetary gear set RS1. The servo devices are for this purpose 510 . 210 as well as the plate packs 500 . 200 spatially at least largely arranged radially one above the other. Accordingly, the structural design of the ZYLBE disc carrier is opposite 3 with regard to the pressure chamber or piston chamber of the servo device 510 slightly modified, since this pressure or piston space is now on the second planetary gear set RS2 facing side of the plate pack 500 is arranged.

As in 5 Furthermore, the brake A is now arranged on the side of the first spur gear STR1 of the spur gear stage STST facing away from the third planetary gear set RS3. Accordingly, the first spur gear STR1 now borders axially directly on the third planetary gear set RS3 on its side facing away from the second planetary gear set RS2. A hub STN1 of the first spur gear STR1 is mounted on a housing intermediate wall GZ, which is arranged on the side of the spur gear STR1 facing away from the planetary gear set and is connected in a suitable manner to the gear housing GG. In the example shown, this connection to the transmission housing takes place via a housing wall GW, which at the same time forms an end outer wall of the transmission housing. In principle, the intermediate partition wall GZ can thus be understood as a type of bearing plate for mounting the spur gear hub STN1.

Brake A (with disk pack 100 and servo device 110 ) is spatially arranged axially between the intermediate housing wall GZ and the housing wall GW. The slat package delimits an example 100 the brake A axially on the housing wall GW and the servo device 110 the brake A axially to the intermediate wall GZ. In this example, the pressure or piston chamber, piston and return element of the servo device 110 integrated into the GZ partition wall. When the pressure is applied appropriately, the piston of the servo device actuates 110 the slats 100 axially in the direction opposite to the spur gear STR1 or in the direction opposite to the planetary gear sets.

In another embodiment, it can also be provided, for example, that the plate pack 100 and the associated servo device 110 seen the other way round in the axial direction, the servo device 110 then on the side of the disk set facing away from the spur gear STR1 100 is then arranged to actuate the brake A axially in the direction of the spur gear STR1 or the planetary gear sets. In this case, the pressure or piston chamber, piston and return element of the servo device are expedient 110 integrated in the housing (outer) wall GW.

For kinematic connection of the input element designed as an inner disk carrier 120 The brake A on the sun gear SO3 of the third planetary gear set RS3 is provided with a sun shaft SOW3, which is coaxial with the drive shaft AN, starting from the sun gear SO3 up to this inner disk carrier ( 120 ) extends, the first spur gear STR1 of the spur gear stage STST and the housing intermediate wall GZ penetrates centrally in the axial direction, and is mounted on the drive shaft AN.

6 now shows a fourth schematic component arrangement as an exemplary solution of the task according to the invention. The main modifications compared to the previously described component arrangements according to 3 to 5 relate to the structural design of the assembly with the two clutches B, E and the structural design of the assembly with the brake A on the side of the spur gear stage STST facing away from the planetary gear sets.

As in 6 can be seen, the assembly of the two clutches B, E comprises a disk carrier ZYLBE as a common inner disk carrier and input element 220 respectively. 520 for both clutches B and E, one outer plate carrier each as an output element 230 respectively. 530 for clutches B and E, a radially inner plate pack 200 with assigned servo device 210 clutch B, as well as a radially outer plate pack 500 with assigned servo device 510 the clutch E. As in 6 the outer plates of both plate packs are indicated 200 . 500 , preferably in the form of steel fins, the inner fins of both sets of plates 200 . 500 accordingly as covering slats.

As a common input element ( 220 . 520 ) for both clutches B, E, the disk carrier ZYLBE is connected to the drive shaft AN and extends in the radial direction parallel to the second planetary gear set RS2, axially immediately adjacent to it.

The radially outer outer plate carrier of clutch E as its output element 530 is designed as a cylinder ZYLRS12, which extends axially from the web plate STB12 (facing the second planetary gear set RS2) of the web ST1 of the first planetary gear set RS1 to the ring gear HO2 of the second planetary gear set RS2, is operatively connected to this web plate STB12 and this ring gear HO2, and which has a suitable driving profile on its cylinder inner diameter for receiving the outer plates of the plate pack 500 the clutch E. Within this cylinder ZYLRS12 is also the servo device 510 the clutch E arranged, spatially seen axially between the disk pack 500 and the web plate STB12, for actuating the plate pack 500 axially in the direction of the second planetary gear set RS2. Because the servo device 510 always rotates at a speed of the web ST1 of the first planetary gear set RS1, it may be appropriate for the servo device 510 also has dynamic pressure compensation. The pressure medium supply to the pressure chamber of the servo device 510 (and possibly the lubricant supply to a pressure compensation chamber of the dynamic pressure compensation) can be supplied, for example, via the web ST1 of the first planetary gear set RS1, the sun shaft SOW1 and the drive shaft AN.

The radially inner outer plate carrier of clutch B as its output element 230 is designed as a pot open in the direction of the second planetary gear set RS2, with a disk-shaped pot bottom, which is connected on its inner diameter to the sun shaft SOW1 mounted on the drive shaft AN and connected to the sun gear SO1 of the first planetary gear set RS1, and with a cylindrical section , which adjoins the outer diameter of this pot base, extends axially in the direction of the second planetary gear set RS2 and has a suitable driving profile on its inner diameter for receiving the outer plates of the plate pack 200 the clutch B. Inside the cylinder space of this outer disk carrier ( 230 ) is also the servo device 210 the clutch B arranged spatially axially between the disk pack 200 and the bottom of the pot for actuating the plate pack 200 axially in the direction of the second planetary gear set RS2. The servo device 210 can also have dynamic pressure equalization. The pressure medium supply to the pressure chamber of the servo device 210 (and possibly the lubricant supply to a pressure compensation chamber of the dynamic pressure compensation) can be supplied, for example, via the sun shaft SOW1 and the drive shaft AN.

Due to this arrangement of the servo devices 210 and 510 the disk carrier ZYLBE has a relatively small axial extent compared to the previously described embodiments according to the invention.

As in 6 still visible, brake A is as in 5 arranged on the side of the first spur gear STR1 of the spur gear stage STST facing away from the third planetary gear set RS3. As already described in the description of 5 hinted at as a possible variation, the plate pack now borders 100 axially to the intermediate wall GZ on which the spur gear STR1 is mounted. The servo device 110 the brake A is now on the side of the disk set facing away from the spur gear STR1 100 arranged and actuated the plate pack 100 when closing axially in the direction of the spur gear STR1 or the planetary gear set RS3. Pressure or piston chamber with pressure medium supply, piston and reset element of the servo device 110 are also integrated into the housing (outer) wall GW as well as a suitable driving profile for holding the outer plates of the plate pack 100 , In this way, pre-assembly of brake A as an assembly is particularly simple in terms of production technology. The kinematic connection of brake A to the third planetary gear set RS3 is similar to that in 5 a sun shaft SOW3 mounted on the drive shaft AN is provided, which is the input element designed as an inner disk carrier 120 the brake A connects to the sun gear SO3 of the third planetary gear set RS3.

As in 6 the spatial arrangement of the two further brakes C and D with their disk packs can also be seen 300 and 400 and the servo devices assigned to them 310 and 410 largely from 4 accepted.

7 now shows a fifth schematic component arrangement as an exemplary solution according to the invention of the task, based on the first component arrangement according to FIG 3 and the third component arrangement according to 5 , The modifications compared to the first component arrangement according to 3 relate essentially to the structural design of the assembly of the two clutches B and E, and the spatial position of the brakes C and D relative to the planetary gear sets.

Regardless of the mirrored representation of the gearbox is in 7 easy to see that the assembly of the two clutches B, E (with disk carrier ZYLBE, the disk packs 200 and 500 , as well as the servo devices 210 and 510 ) out 5 was acquired.

As in 7 still visible, the two neighboring brakes C and D were compared 3 shifted in the axial direction, so that now the brake C is spatially arranged in a region radially above the first planetary gear set RS1 and the brake D adjacent to the brake C in a region radially above the clutch E. Also indicated is a bevel of the gear housing GG in the region of the outer diameter of the housing on the side of the automatic transmission opposite the spur gear. Such a bevel may be necessary, for example, due to a gearbox installation space that is actually present. The inner disk carriers ( 320 . 420 ) Both brakes C, D are structurally adapted to the bevel of the gear housing GG.

As a further detail modification is in 7 a modified bearing of the first spur gear STR1 of the spur gear STST shown. Axially between the input element designed as an inner disk carrier 120 the brake A and the spur gear STST is now provided with a suitable means connected to the gear housing GG intermediate housing wall GZ, which extends radially from the Gearbox outer diameter extends radially inwards up to the web shaft STW3, via which the web ST3 of the third planetary gear set RS3 is connected to the first spur gear STR1 of the spur gear stage STST. The web shaft STW3 is mounted on the drive shaft AN as an example. In contrast to 3 the first spur gear STR1 is now mounted on the intermediate wall GZ and not on the outer end wall GW of the gear housing.

An additional detail is shown in 7 a device for measuring a speed of the drive shaft AN. The corresponding drive speed sensor is designated by NAN, is arranged on an outer end wall of the gear housing GG and is therefore also easily accessible from the outside, here, for example, on the gear side opposite the STST gear stage. In accordance with the exemplary embodiment as an axially scanning sensor, this drive speed sensor NAN is spatially arranged in the area of a hub GN fixed to the transmission housing and scans a sensor wheel NANGR which is connected in a rotationally fixed manner to the drive shaft AN, for example by means of an inductive or Hall measuring principle.

8th now shows a sixth schematic component arrangement as an exemplary solution of the task according to the invention. This sixth component arrangement according to the invention is based on the previously described third schematic component arrangement 5 and primarily relates to the arrangement and design of the pressure chambers and pressure compensation chambers of both servo devices of the assembly with the two clutches B and E.

As in 8th As can be seen, a common disk carrier ZYLBE is provided for both clutches B and E, which forms the outer disk carrier for clutch B and the inner disk carrier for clutch E. Both slat packages are unchanged 200 . 500 the clutches B, E are arranged on the side of the disk carrier ZYLBE facing the first planetary gear set RS1 and are driven by the respective servo device 210 respectively. 510 the clutch B or E is actuated axially in the direction of the planetary gear set RS1 when the clutch closes, the disk set 500 spatially seen radially above the plate pack 200 is arranged. Both servo devices 210 . 510 each have dynamic pressure compensation.

The plate carrier ZYLBE common to the clutches B, E is geometric in the sections 223 . 222 . 221 . 521 , and 522 divided. The hub 223 , the disc-shaped section 222 and the cylindrical section 221 are assigned to the input element of the radially inner clutch B, the cylindrical section 521 and the disc-shaped section 522 the input element of the radially outer clutch E. This is also illustrated by the nomenclature chosen.

The hub 223 of the disk carrier ZYLBE is connected to the drive shaft AN via a suitable operative connection, for example via a driving profile. In the in 8th The example shown is the hub 223 also mounted on a gearbox-fixed hub GN, which - starting from the outer end wall of the gearbox housing GG arranged on the side of the first planetary gearset RS1 facing away from the clutch - extends axially to below the disk carrier ZYLBE (and thereby grips centrally through the first planetary gearset RS1 and concentrically in one Inner diameter of the hub 223 immersed in the axial direction).

On the side of the hub 223 , which faces away from the planetary gear set RS1, the disc-shaped section closes 222 to the hub 223 and extends radially outward to a diameter that is slightly larger than the outer diameter of the plate pack 200 corresponds to the (radially inner) clutch B. The cylindrical section 221 closes on the outer diameter of the disc-shaped section 222 on this and extends in the axial direction up to the plate pack 200 clutch B, relatively close to the first planetary gear set RS1. The cylindrical section has in the area near the adjacent first planetary gear set RS1 221 a driving profile on its inside diameter to accommodate the outer plates of the plate pack 200 , As in 8th indicated, these outer fins are preferably designed as steel fins. The cylindrical section 221 and the disc-shaped section 222 of the plate carrier ZYLBE form a clutch space, inside which the plates 200 and the servo device 210 the clutch B are arranged radially above the hub 223 of the ZYLBE disc carrier. The servo device 210 includes a pressure room 211 , a piston 214 , a restoring element embodied here, for example, as a plate spring 213 , a pressure equalization room 212 and a baffle plate 215 , The pressure room 211 is going through the sections 221 . 222 and 223 of the disk carrier ZYLBE and the piston 214 formed, the pressure compensation space 212 the dynamic pressure compensation of clutch B by the piston 214 and the baffle plate 215 , The pressure equalization room 212 the servo device 210 is therefore closer to the first planetary gear set RS1 than the pressure chamber 211 the servo device 210 ,

One with 218 designated pressure medium supply to the pressure chamber 211 the servo device 210 the radially inner clutch E runs here, for example, as an oblique radial bore through the hub 223 of the ZYLBE disc carrier. This radial bore 218 The pressure medium required to actuate clutch B is supplied here, for example, via the hub GN fixed to the transmission housing, on which the hub 223 of the disk carrier ZYLBE is mounted as already mentioned, the gear housing-fixed hub GN having correspondingly designed pressure medium channels. In another embodiment, the pressure medium can the pressure chamber 211 the servo device 210 can also be supplied to the drive shaft AN via corresponding axial and radial bores.

One with 219 designated lubricant supply to the pressure compensation chamber 212 the servo device 210 the radially inner clutch E also runs here, for example, as a straight radial bore through the hub 223 of the ZYLBE disc carrier. This radial bore 219 This is fed to the pressure-free filling of the pressure compensation space 212 Required lubricants here also via the gearbox-fixed hub GN.

The cylindrical section (associated with the radially outer clutch E) 521 of the disk carrier ZYLBE corresponds in principle to the cylindrical section (assigned to the radially inner clutch B) 221 , The cylindrical section faces on its side facing the first planetary gear set RS1 521 a driving profile on its outer diameter to hold the inner plates of the plate pack 200 the clutch B. As in 8th indicated, these inner slats are preferably designed as covering slats. The disc-shaped section closes axially next to this lamella driving profile, on the side of the lamella driving profile facing the planetary gear set RS1 522 of the ZYLBE disc carrier to the cylindrical section 521 and extends - starting from the outer diameter of the cylindrical section 521 - Radially outwards to a diameter which is preferably smaller than the average diameter of the outer plates of the plate pack 500 the radially outer clutch E.

The servo device 510 the (radially outer) coupling E is spatially radially above the cylindrical section 521 of the disk carrier ZYLBE arranged. To form a piston or pressure chamber 511 and a pressure equalization room 512 this servo device 510 is a cylindrical support disc 515 provided that spatially seen radially above the cylindrical portion 521 of the disk carrier ZYLBE is arranged. This support disc has 515 a disc-shaped section whose inner diameter in the region of the axially outer edge of the cylindrical section facing the second planetary gear set RS2 521 on this cylindrical section 521 of the disk carrier ZYLBE is pushed on axially in this area on the cylindrical section 521 is secured and also to the cylindrical section 521 is sealed against pressure medium. On the outside diameter of the disk-shaped section of the support disk 515 is followed by a cylindrical section that axially in the direction of the plate pack 500 or extends axially in the direction of the first planetary gear set RS1. The cylindrical support disc 515 and the cylindrical section 521 of the ZYLBE disc carrier form the piston or pressure chamber 511 the servo device 510 inside which a piston 514 the servo device 510 is axially displaceable. The piston 514 is opposite the cylindrical portion of the support disc 515 as well as opposite the cylindrical section 521 of the ZYLBE disc carrier axially displaceably sealed pressure-tight. The piston 514 the servo device 510 is - similar to the support disc 515 - than towards the plate pack 500 open cylinder formed, the cylinder bottom the interface to the pressure chamber 511 forms. The cylindrical mantle of the piston 514 engages over the disc-shaped section 522 of the disk carrier ZYLBE and extends in the axial direction up to the disk pack 500 the clutch E. Between the cylinder bottom of the piston 514 and the disc-shaped section 522 of the ZYLBE disc carrier is a reset element 513 the servo device 510 clamped, here for example as an annular package with parallel coil springs.

One with 518 designated pressure medium supply to the pressure chamber 511 the servo device 510 the radially outer clutch E extends in sections as a radial bore through the disk-shaped section 222 and the hub 223 of the ZYLBE disc carrier. The pressure medium for actuating the clutch E can, for example, be supplied from the drive shaft AN, the drive shaft AN then having corresponding radial and axial bores. Alternatively, the pressure medium for actuating the clutch E of this radial bore 518 but also via the hub GN fixed to the gearbox housing, on which the disk carrier ZYLBE and the drive shaft AN are mounted here, the hub GN then having correspondingly designed pressure medium channels.

To form a pressure compensation space 512 for dynamic pressure compensation of the servo device 510 is the cylindrical jacket of the piston 514 opposite the disc-shaped section 522 of the ZYLBE disc carrier axially displaceably sealed in a lubricant-tight manner. The pressure equalization chamber is correspondingly 512 through the disc-shaped section 522 and the cylindrical section 521 of the disk carrier ZYLBE and the piston 514 educated.

This pressure compensation chamber is filled with lubricant without pressure 512 the radially outer clutch E from the pressure compensation space 212 the radially inner clutch B. For this purpose, both in the cylindrical section 521 (respectively. 221 ) of the disk carrier ZYLBE as well as in the piston 214 the servo device 210 the clutch B radial bores provided in the pressure equalization chamber 212 or in the pressure equalization room 512 lead. The corresponding lubricant supply is included 519 designated.

Out 8th it can be seen that the servo device 510 the coupling E spatially seen radially above the servo device 210 the clutch B is arranged, the two pressure chambers 211 and 511 , the two pressure equalization rooms 212 and 512 and also the reset devices 213 and 513 spatially are arranged approximately radially one above the other. The section of the lateral surface of the disk carrier ZYLBE common to both clutches B, E, which covers the two pressure chambers 211 . 511 or the two pressure equalization rooms 212 . 512 separates from each other, is in principle the cylindrical section 221 (respectively. 521 ) of the plate carrier ZYLBE common to both clutches B, E.

Based on 9 to 11 Three further component assemblies according to the invention are explained in more detail below, in which - in contrast to the six component assemblies according to the invention described above - the assembly of the two clutches B, E arranged axially between the first planetary gear set RS1 and the second planetary gear set RS2 is now axially arranged side by side plate packs 200 . 500 having. As a result of this arrangement, both plate packs can advantageously 200 . 500 have a comparatively large diameter, corresponding to their high thermal load. With regard to the structural design of this assembly, reference is also made to the unpublished German patent application filed by the applicant with the same filing date as the present application with internal file number ZF 8818 S, the content of which is expressly also to be the subject of the present application.

9 now shows a seventh schematic component arrangement as an exemplary solution of the task according to the invention, based on the first component arrangement according to the invention 3 , As already mentioned, the two clutches B, E form an assembly with disk packs now arranged axially next to one another 200 and 500 , This assembly is axially arranged unchanged between the two planetary gear sets RS1 and RS2.

Similar to 3 , is also according to 9 a plate carrier ZYLBE common to both clutches B, E is provided, which is designed as a pot open in the direction of the first planetary gear set RS1 and is connected to the drive shaft AN. In contrast to 3 The ZYLBE disk carrier now forms the inner disk carrier for both clutches B and E and has a suitable driving profile on its outer diameter for receiving the inner disks of both disk packs 200 and 500 , As in 9 indicated, these inner plates are preferably designed as steel plates and the outer plates of the plate packs 200 and 500 accordingly as covering slats. The slat package 500 the clutch E is arranged near the second planetary gear set RS2, the disk set 200 the clutch B correspondingly on the side of the disk set opposite the second planetary gear set RS2 500 near the first planetary gear set RS1. The disk-shaped pot bottom of the disk carrier ZYLBE and the first cylindrical section adjoining the outside diameter of this pot bottom with the disk driving profile for the inner disks of the clutch E can be used as an input element 520 the clutch E can be understood. Correspondingly, the second cylindrical section with the disk drive profile for the inner disks of clutch B, which adjoins said first cylindrical section with the disk drive profile for the inner disks of clutch E axially in the direction of the first planetary gear set RS1, as an input element 220 clutch B can be understood. The input element 220 the clutch B is therefore via the input element 520 the clutch E connected to the drive shaft AN.

As in 9 As can be seen, the disk carrier ZYLBE common to both clutches B, E has, for example, a cylindrical hub in the diameter range of the drive shaft AN 523 on, which is at least non-rotatably connected to the drive shaft AN by suitable means. This hub 523 extends axially in the direction of the first planetary gear set RS1 from the disk-shaped pot bottom of the disk carrier ZYLBE. Spatially seen radially above this hub 523 are the servo devices 510 . 210 both clutches E, B arranged, with predominant parts of these two servo devices 510 . 210 are also arranged within the cylinder space formed by the lamella driving profiles of the lamella carrier ZYLBE. Here is the servo device 510 the clutch E is closer to the second planetary gear set RS2 than the servo device 210 the clutch B and borders both axially directly on the disk-shaped pot bottom of the disk carrier ZYLBE and radially on the cylindrical section of the disk carrier ZYLBE below its disk drive profiles. For actuating the plate pack tes 500 The servo device points axially in the direction of the second planetary gear set RS2 510 preferably at least three actuating fingers 516 on the cylindrical section of the ZYLBE plate carrier with the plate driving profile for the inner plates of the plate pack 200 grasp in the axial and radial directions, thereby the plate pack 200 or this slat package 200 Grip the associated slat drive profile of the ZYLBE slat carrier completely in the axial direction and onto the slat package 500 from the side of the disk set opposite the second planetary gear set RS2 500 act out.

The servo device is corresponding 210 the clutch B spatially next to the servo device 510 arranged the clutch E, on the first planetary gearset RS1 facing side of this servo device 510 , For actuating the plate pack 200 The servo device points axially in the direction of the second planetary gear set RS2 210 an annular pressure plate 216 on which the actuating fingers 516 the servo device 510 completely in the radial direction and partially in the axial direction and on the disk pack 200 from the side of the disk set opposite the second planetary gear set RS2 200 from works.

In order to save axial overall length, it can also be provided in another embodiment that instead of the annular pressure plate 216 the servo device 210 individual actuating fingers are provided, which are spatially seen axially in the actuating fingers 516 the servo devices 210 . 510 are nested.

According to the design of the disk carrier ZYLBE as an inner disk carrier for both clutches B, E, both are the output element 230 the clutch B as well as the output element 530 the clutch E as an outer disk carrier for receiving the outer disks of the respective disk pack 200 respectively. 500 formed, these outer slats (as already mentioned) are preferably each designed as covering slats. Geometrically, the starting element 230 the clutch B has the shape of a pot open in the direction of the second planetary gear set RS2, with a cylindrical section, a disk-shaped pot base and a hub. The disc-shaped pot bottom of the starting element 230 is axially directly between the first planetary gear set RS1 and the servo device 210 the clutch B arranged. The hub of the output element 230 connects to the bottom of the pot with its inner diameter, extends axially in the direction of the first planetary gear set RS1 and is connected to the sun gear SO1 of the first planetary gear set RS1 via a suitable operative connection, for example by means of a welded connection or driving profile. The cylindrical section of the output element 230 connects to the bottom of the pot with its outer diameter, extends axially in the direction of the second planetary gear set RS2 to beyond the plate pack 200 the clutch B and has a suitable driving profile on its inner diameter for receiving the outer plates of this plate set 200 , The geometric design of the starting element 530 the coupling E corresponds in principle to that in 3 already explained training, the cylinder ZYLRS12 as in 3 the operative connection between the web ST1 of the first planetary gear set RS1 and the ring gear HO2 of the second planetary gear set RS2 and the outer plates of the plate set 500 the clutch E now forms the cylindrical outer plate carrier ( 230 ) overlaps the clutch B.

As in 9 the slat package is still visible 100 the brake A as in 3 seen spatially at least approximately radially above the third planetary gear set RS3 in the region of the large inner diameter of the cylindrical gear housing GG. The servo device 110 the brake A, however, is now spatially arranged approximately radially above the second (middle) planetary gear set RS2 and actuates the disks 100 when brake A is applied axially in the opposite direction to the first planetary gear set RS1.

Furthermore, in 9 the brake D with its disk pack 400 and their servo equipment 410 arranged, for example, in a region approximately radially above the first planetary gear set RS1 on the large inner diameter of the cylindrical gear housing GG. The Sevo facility 410 the brake D is integrated, for example, in the housing cover GD, which forms the outer end face of the transmission opposite the output or the spur gear of the transmission and is connected in a rotationally fixed manner to the transmission housing GG by suitable means, and actuates the plates 400 when the brake D is closed axially in the direction of the third planetary gear set RS3.

Brake C with its disk pack 300 and their servo equipment 310 is now arranged axially next to the first planetary gear set RS1 on its side facing away from the clutch B or the other two planetary gear sets RS2, RS3, directly between the first planetary gear set RS1 and the housing cover GD on a diameter which is approximately the ring gear HO1 of the first planetary gear set RS1 equivalent. The housing cover GD is advantageously as an outer disk carrier of the brake C for receiving the outer disks of the disk pack 300 educated. In addition, the servo device 310 the brake C integrated in this housing cover GD and actuates the slats 300 when the brake C is closed axially in the direction of the first planetary gear set RS1. The directions of actuation of all three brakes C, D and A are thus the same in this embodiment.

As in 3 is also in 9 the drive shaft AN is mounted on the housing cover GD. In contrast to 3 For this purpose, the housing cover GD has a tubular hub GN fixed to the housing cover or fixed to the housing, which extends into the interior of the gear housing GG. The drive shaft AN is mounted on an inner diameter of this hub GN. The input element, which is connected to the sun gear SO1 of the first planetary gear set RS1 and is designed as an inner disk carrier, is on an outer diameter of this hub GN 320 the brake C stored.

10 now shows an eighth schematic component arrangement as an exemplary solution of the task according to the invention, based on the previously 9 seventh component arrangement according to the invention explained in detail. The difference to the seventh component arrangement according to 9 essentially relates to the structural design of the servo device 510 clutch E, with unchanged direction of actuation. As in 9 is this servo device 510 spatially seen radially above the hub 523 of the disk carrier ZYLBE common to both clutches B, E, axially adjacent to the disk-shaped section (“pot bottom”) of this disk carrier ZYLBE. The servo device is to a large extent 510 arranged radially inside the clutch chamber, which through the cylindrical section of the disk carrier ZYLBE with the disk drive profile for the inner disks of the disk pack 500 the clutch E is formed. In contrast to 9 the disk carrier ZYLBE has spatially seen on its radially outer cylinder in an area axially between the two disk packs 200 and 500 preferably at least three openings distributed symmetrically on the circumference. Each of these breakthroughs is an operating finger 516 the servo device 510 assigned. The openings each have a sufficiently large axial extent, so that these actuating fingers 516 on the one hand can reach radially through the openings and on the other hand an axial stroke for actuating the plate pack 500 can perform when clutch closing. The actuating fingers 516 act like in 9 on the surface of the plate pack 500 that the slat package 200 is facing the clutch B or the first planetary gear set RS1.

The servo device 210 the clutch B is axially next to the servo device 510 the clutch E is arranged on the side of the servo device facing the first planetary gear set RS1 510 , The ring-shaped pressure plate 216 the servo device 210 overlaps the slat driving profile of the ZYLBE slat carrier for the inner slats of the slat package 200 in the radial and axial directions and act on the surface of the plate pack 200 facing the first planetary gear set RS1.

11 now shows a ninth schematic component arrangement as an exemplary solution of the task according to the invention, likewise based on the previously 9 seventh component arrangement according to the invention explained in detail. The difference to the seventh component arrangement according to 9 relates essentially to the structural design of the plate carrier ZYLBE common to the two clutches B, E and the servo device 210 . 510 of these couplings B, E.

The disk carrier ZYLBE is designed as an inner disk carrier for both clutches B and E and forms the input element for both clutches B, E ( 220 . 520 ) and is connected to the drive shaft AN according to the kinematic coupling of the transmission diagram. On its outer diameter, the ZYLBE disk carrier has a suitable driving profile for receiving the inner disks of both disk packs 200 and 500 , these inner slats preferably being steel slats and the outer slats of the disk packs 200 and 500 are designed accordingly as covering slats. As in 9 is the plate pack 500 the clutch E arranged near the second planetary gear set RS2, the disk pack 200 the clutch B correspondingly on the side of the disk set opposite the second planetary gear set RS2 500 near the first planetary gear set RS1. The section of the cylindrical plate carrier ZYLBE with the plate driving profile for the inner plates of the plate pack 200 is the input element 220 to be assigned to clutch B, the section of the cylindrical disk carrier ZYLBE with the disk drive profile for the inner disks of the disk pack 500 the input element 520 the clutch E.

In contrast to 9 The cylindrical disk carrier ZYLBE now has a disc-shaped section which is located approximately centrally under the cylindrical section of the disk carrier ZYLBE - spatially approximately between the disk carrier profile for the inner disks of the disk pack 200 and the slat drive profile for the inner slats of the plate pack 500 - extends inwards to a hub 523 of the ZYLBE disc carrier. This hub 523 in turn is connected to the drive shaft AN, in contrast to 9 but now in the axial direction on both sides of the disc-shaped section of the disk carrier ZYLBE, that is, starting from the central disc-shaped section of the disk carrier ZYLBE, on the one hand, seen spatially below the disk pack 200 the clutch B axially in the direction of the first planetary gear set RS1, on the other hand spatially seen below the disk set 500 the clutch E axially in the direction of the second planetary gear set RS2.

A servo device 210 the clutch B is arranged axially on the side of the disk-shaped section of the disk carrier ZYLBE facing the first planetary gear set RS1. Here is this servo device 210 spatially seen above the hub section of the hub facing the first planetary gear set RS1 523 of the disk carrier ZYLBE arranged, at least predominantly within the clutch space, through the disk pack 200 the clutch B and the disc-shaped section of the disk carrier ZYLBE is formed. The servo device limits 210 directly to this disc-shaped section and also to the cylindrical section of the ZYLBE disk carrier with the disk drive profile for the inner disks of the disk pack 200 on. For actuating the plate pack 200 the clutch B axially in the direction of the second planetary gear set RS2 has the servo device 210 preferably at least three actuating fingers 216 on which the cylindrical section of the disk carrier ZYLBE with the disk drive profile for the inner disks of the disk pack 200 grasp in the radial and axial directions and on the end face of the plate pack 200 act, which faces the first planetary gear set RS1.

A servo device 510 the clutch E is arranged axially on the side of the disk-shaped section of the disk carrier ZYLBE facing the second planetary gear set RS2. Here is this servo device 510 spatially seen above the hub section of the hub facing the second planetary gear set RS2 523 of the disk carrier ZYLBE arranged, at least predominantly within the clutch space, through the disk pack 500 the clutch E and the disc-shaped section of the disk carrier ZYLBE is formed. The servo device limits 510 directly to this disc-shaped section and also to the cylindrical section of the ZYLBE disk carrier with the disk drive profile for the inner disks of the disk pack 500 on. For actuating the plate pack 500 the clutch E axially in the direction of the first planetary gear set RS1 has the servo device 510 preferably at least three actuating fingers 516 which packages the cylindrical section of the ZYLBE disc carrier with the disc drive profile for the internal discs of the disc 500 grasp in the radial and axial directions and on the end face of the plate pack 500 act, which faces the second planetary gear set RS2.

In another embodiment, instead of the actuating fingers 216 and or 516 the servo device 210 respectively. 510 an annular pressure plate can also be provided.

The formation of the starting element 230 the clutch B and the output element 530 the clutch E in each case as an outer disk carrier for receiving the outer disks of the respective disk pack, which are preferably designed as lining disks 200 respectively. 500 , as well as the design and arrangement of the other components of the in 11 The illustrated exemplary ninth component arrangement according to the invention was made from 9 accepted.

As already mentioned, some component configurations of all nine component arrangements according to the invention are to be regarded as examples. To save the axial overall length of the automatic transmission, for example, the person skilled in the art will, if necessary, refer to 3 to 11 Replace the spur gear shown with a chain drive. Depending on the installation situation and drive train configuration, the person skilled in the art will combine with all proposed nine component arrangements according to the invention either with an output shaft which is parallel to the drive shaft or with a non-right-angled spur gear (beveloid spur gear) or a (right-angled or non-right-angled) bevel gear. On account of the drive shaft penetrating the entire transmission in the axial direction, the person skilled in the art will reorganize the proposed nine component arrangements according to the invention without any particular effort for an application with a drive and output shaft which run coaxially with one another.

In the 3 to 11 The nine schematic component arrangements shown generally assume multi-disc brakes as a constructive solution for the switching elements to be designed as a brake. In principle, individual or even all multi-disc brakes can be structurally replaced by band brakes. In the non-switched state, band brakes are known to be cheaper than multi-disc brakes in terms of drag torque loss. For all of the component arrangements shown, it is advisable to design the brake D not shifted in the second to sixth forward gear and / or the brake A not shifted in the fifth and sixth forward gear and in the reverse gear as a band brake. Likewise, the individual brakes can also be supported if necessary by an additional freewheel, which is arranged kinematically between the input element of the respective brake and the gear housing and which fixes this input element in one direction of rotation on the gear housing.

A

first Switching element, brake

B

second Switching element, clutch

C

third Switching element, brake

D

fourth Switching element, brake

e

fifth switching element, clutch

ZYLBE

Lamellar support of the second and fifth

switching element

ON

drive shaft

FROM

output shaft

GG

gearbox

DG

housing cover

GW

housing wall

GN

transmission housing hub

GZ

Housing partition

NAN

Input speed sensor

NANGR

sensor wheel

RS1

first planetary gear

HO1

ring gear of the first planetary gear set

SO1

sun of the first planetary gear set

ST1

web of the first planetary gear set

PL1

planet of the first planetary gear set

SOW1

sun wave of the first planetary gear set

STB 11

first Web plate of the first planetary gear set

STB12

second Web plate of the first planetary gear set

RS2

second planetary gear

HO2

ring gear of the second planetary gear set

SO2

sun of the second planetary gear set

ST2

web of the second planetary gear set

PL2

planet of the second planetary gear set

RS3

third planetary gear

HO3

ring gear of the third planetary gear set

SO3

sun of the third planetary gear set

ST3

web of the third planetary gear set

PL3

planet of the third planetary gear set

SOW3

sun wave of the third planetary gear set

STB 3

web plate of the third planetary gear set

STW3

web shaft of the third planetary gear set

ZYLRS12

Cylinder, Connection between the web of the

first Planetary gear set and the ring gear of the

second planetary gear

ZYLRS13

Cylinder, Connection between the ring gear of the

first Planetary gear set and the web of the third

planetary gear

STST

spur, spur gearing

STR 1

first Spur gear of the spur gear stage

STN1

hub the first spur gear of the spur gear stage

100

slats of the first switching element

110

servo of the first switching element

120

input element of the first switching element

200

slats of the second switching element

210

servo of the second switching element

211

pressure chamber the servo device of the second switch

element

212

Pressure equalization chamber the servo device of the

second switching element

213

Return element the servo device of the second

switching element

214

piston the servo device of the second switch

element

215

baffle plate the servo device of the second

switching element

216

Andruckteller the servo device of the second

switching element

218

Pressure medium supply to Second press room

switching element

219

Lubricant supply to the Pressure equalization chamber of the

second switching element

220

input element of the second switching element

221

cylindrical Section of the input element of the

second Switching element

222

disc-shaped section of the entrance

element of the second switching element

223

hub of the input element of the second switching

230

output element of the second switching element

300

slats of the third switching element

310

servo of the third switching element

320

input element of the third switching element

400

slats of the fourth switching element

410

servo of the fourth switching element

420

input element of the fourth switching element

500

slats the fifth switching element

510

servo the fifth switching element

511

pressure chamber the fifth switching element

512

Pressure equalization chamber of the fifth switching element

513

Return element the servo device of the fifth

switching element

514

piston the servo device of the fifth switching

element

515

cylindrical support disc the servo device

of fifth switching element

516

actuating fingers the servo device of the fifth

switching element

518

Pressure medium supply to Printing room of the fifth

switching element

519

Lubricant supply to the Pressure equalization chamber of the

fifth switching element

520

input element the fifth switching element

521

cylindrical Section of the entrance

element the fifth switching element

522

disc-shaped section of the input element

of fifth switching element

523

hub of the input element of the fifth switching

element

530

output element the fifth switching element

Claims (52)

Multi-stage automatic transmission, with an input shaft (AN), an output shaft (AB), at least three individual planetary gear sets (RS1, RS2, RS3), and at least five shift elements (A to E), whereby - the three planetary gear sets (RS1, RS2, RS3) are arranged coaxially to each other, - the second and third planetary gear sets (RS2, RS3) are arranged axially next to each other, - a sun gear (SO3) of the third planetary gear set (RS3) via the first switching element (A) on a gearbox (GG) of the multi-stage - Automatic transmission can be fixed, - the drive shaft (AN) is connected to a sun gear (SO2) of the second planetary gear set (RS2), - the drive shaft (AN) via the second switching element (B) to a sun gear (SO1) of the first planetary gear set (RS1 ) and / or via the fifth switching element (E) with a web (ST1) of the first planetary gear set (RS1), - alternatively the sun gear (SO1) of the first planetary gear set (RS1) via the third switching element (C) and / o which the web (ST1) of the first planetary gear set (RS1) via the fourth switching element (D) on the transmission housing (GG) can be fixed, and wherein - either the output shaft (AB) and a ring gear (HO1) of the first planetary gear set (RS1) and a web (ST3) of the third planetary gear set (RS3) are connected to one another and a web (ST2) of the second planetary gear set (RS2) is connected to a ring gear (HO3) of the third planetary gear set (RS3) and the web (ST1) of the first planetary gear set ( RS1) is connected to a ring gear (HO2) of the second planetary gear set (RS2), - or the output shaft (AB) and the ring gear (HO1) of the first planetary gear set (RS1) and the web (ST2) of the second planetary gear set (RS2) are connected to one another and the web (ST3) of the third planetary gear set (RS3) is connected to the ring gear (HO2) of the second planetary gear set (RS2) and the web (ST1) of the first planetary gear set (RS1) is connected to the ring gear (HO3) of the third planetary gear set (RS3 ) is connected t, characterized in that the second and fifth shifting elements (B, E) are spatially arranged axially between the first and second planetary gear sets (RS1, RS2). Multi-stage automatic transmission according to claim 1, characterized characterized in that the first planetary gear set (RS1) and / or the second planetary gear set (RS2) only one shaft completely penetrates centrally in the axial direction becomes. Multi-stage automatic transmission according to claim 2, characterized characterized that the the first and / or second planetary gear set (RS1, RS2) in axial Direction through shaft the drive shaft (AN) of the automatic transmission is. Multi-stage automatic transmission according to claim 1, 2 or 3, characterized in that a plate pack ( 500 ) of the fifth switching element (E) is arranged on a larger diameter than a plate pack ( 200 ) of the second switching element (B). Multi-stage automatic transmission according to one of claims 1 to 4, characterized in that the second and fifth shifting elements (B, E) are combined as one assembly, with - the disk packs ( 200 . 500 ) of the second and fifth switching elements (B, E), - one servo device each ( 210 . 510 ) of the second and fifth switching element (B, E) for actuation of the respective plate packs ( 200 . 500 ) of the second or fifth switching element (B, E), and - a plate carrier (ZYLBE) common to the second and fifth switching element (B, E) for receiving the outer or covering plates of the plate packs ( 200 . 500 ) of the second and fifth switching element (B, E). Multi-stage automatic transmission according to one of claims 1 to 5, characterized in that an inner friction surface diameter of lining plates of the plate pack ( 200 ) of the second switching element (B) is smaller than an outer friction surface diameter of lining plates of the plate pack ( 500 ) of the fifth switching element (E). Multi-stage automatic transmission according to one of claims 1 to 6, characterized in that the connecting element between the web (ST1) of the first planetary gear set (RS1) and the Ring gear (HO2) of the second planetary gear set (RS2) also one External disk carrier of the fifth Switching element (E) forms. Multi-stage automatic transmission according to claim 7, characterized in that the covering plates of the plate pack ( 500 ) have on their outer diameter a driving profile which engages axially displaceably in a corresponding lamella driving profile of the outer disk carrier of the fifth switching element (E). Multi-stage automatic transmission according to claim 7 or 8, characterized in that the plate carrier (ZYLBE) common to the second and fifth shifting elements (B, E) forms a clutch chamber within which the plate set ( 200 ) of the second switching element (B) and the servo device ( 210 ) of the second switching element (B) are arranged. Multi-stage automatic transmission according to one of claims 1 to 9, characterized in that the servo device ( 510 ) of the fifth switching element (E) and / or the servo device ( 210 ) of the second switching element (B) the associated disk pack ( 500 . 200 ) actuated axially in the direction of the first planetary gear set (RS1) when the fifth or second switching element (E, B) is closed. Multi-stage automatic transmission according to claim 10, characterized in that the servo device ( 510 ) of the fifth switching element (E) and / or the servo device ( 210 ) of the second switching element (B) seen spatially axially between the disk pack assigned to it ( 500 . 200 ) and the second planetary gear set (RS2). Multi-stage automatic transmission according to one of claims 1 to 9, characterized in that the servo device ( 510 ) of the fifth switching element (E) and / or the servo device ( 210 ) of the second switching element (B) the associated disk pack ( 500 . 200 ) actuated axially in the direction of the second planetary gear set (RS2) when the fifth or second switching element (E, B) is closed. Multi-stage automatic transmission according to claim 12, characterized in that the servo device ( 510 ) of the fifth switching element (E) and / or the servo device ( 210 ) of the second switching element (B) seen spatially axially between the disk pack assigned to it ( 500 . 200 ) and the first planetary gear set (RS1) is arranged. Multi-stage automatic transmission according to one of claims 1 to 13, characterized in that the servo device ( 510 ) of the fifth switching element (E) and / or the servo device ( 210 ) of the second switching element (B) have dynamic pressure compensation. Multi-stage automatic transmission according to one of claims 1 to 14, characterized in that the servo device ( 210 ) of the second switching element (B) and / or the servo device ( 510 ) of the fifth switching element (E) is mounted on the shaft which passes through the first planetary gear set (RS1) centrally, in particular on the drive shaft (AN). Multi-stage automatic transmission according to one of claims 1 to 14, characterized in that the servo device ( 210 ) of the second switching element (B) and / or the servo device ( 510 ) of the fifth switching element (E) on the sun gear (SO1) of the first planetary gear set (RS1). Multi-stage automatic transmission according to one of claims 1 to 16, characterized in that the third and fourth switching element (C, D) seen in the axial direction in a region radially above the planetary gear sets (RS1, RS2, RS3) are arranged. Multi-stage automatic transmission according to claim 17, characterized in that the third and fourth shifting elements (C, D) are arranged axially next to one another, in particular plate packs ( 300 . 400 ) of the third and fourth switching elements (C, D) are arranged on an at least similar diameter. Multi-stage automatic transmission according to claims 17 and 18, characterized in that the third and fourth shifting elements (C, D) form a preassembled assembly which comprises the disk packs ( 300 . 400 ) of the third and fourth switching element (C, D) and a common for the third and fourth switching element (C, D) outer plate carrier, where with a servo device ( 310 ) for actuating the plate pack ( 300 ) of the third switching element (C) and a servo device ( 410 ) for actuating the plate pack ( 400 ) of the fourth switching element (D) are at least partially integrated in this common outer disk carrier. Multi-stage automatic transmission according to one of claims 1 to 16, characterized in that the third switching element (C) spatially seen axially next to the first planetary gear set (RS1) on its second planetary gear set (RS2) facing away, and that that fourth switching element (D) spatially seen in an area radially above the planetary gear sets (RS1, RS2, RS3) is arranged. Multi-stage automatic transmission according to claim 17, 18 or 20, characterized in that an outer disk carrier of the third and / or fourth switching element (C, D) in the transmission housing (GG) is integrated. Multi-stage automatic transmission according to one of claims 1 to 21, characterized in that the actuating direction of the servo device ( 310 ) of the third switching element (C) and the direction of actuation of the servo device ( 410 ) of the fourth switching element (D) are opposite to each other when switching on the respective switching element (C, D). Multi-stage automatic transmission according to one of claims 1 to 21, characterized in that the actuating direction of the servo device ( 310 ) of the third switching element (C) and the direction of actuation of the servo device ( 410 ) of the fourth switching element (D) are rectified when the respective switching element (C, D) is switched on. Multi-stage automatic transmission according to one of claims 1 to 23, characterized in that at least one of the two servo devices ( 310 . 410 ) of the third and fourth switching element (C, D) axially between the disk packs ( 300 . 400 ) of the third and fourth switching element (C, D) is arranged. Multi-stage automatic transmission according to one of claims 1 to 24, characterized in that the servo device ( 310 ) of the third switching element (C) and / or the servo device ( 410 ) of the fourth switching element (D) is at least partially integrated in the gear housing (GG) or in a housing wall (GW) which is fixed to the gear housing and forms an outer wall of the gear housing (GG). Multi-stage automatic transmission according to one of claims 1 to 25, characterized in that the first switching element (A) spatially seen on the side facing away from the second planetary gear set (RS2) of the third planetary gear set (RS3) is arranged. Multi-stage automatic transmission according to claim 26, characterized characterized that the first switching element (A) axially adjacent to the third planetary gear set (RS3). Multi-stage automatic transmission according to one of claims 1 to 27, characterized in that the first switching element (A) on an outer wall of the gear housing (GG) or on a gearbox cover, the one with the gearbox (GG) is non-rotatably connected and an outer wall of the automatic transmission forms, borders. Multi-stage automatic transmission according to one of claims 1 to 25, characterized in that the first switching element (A) seen in the axial direction in one area radially above the planetary gear sets (RS1, RS2, RS3) is arranged, in particular in an area in seen in the axial direction radially over the third planetary gear set (RS3). Multi-stage automatic transmission according to Claim 29, characterized in that the first and fourth shifting elements (A, D) are arranged axially next to one another, in particular plate packs ( 100 . 400 ) of the first and fourth switching elements (A, D) are arranged on an at least similar diameter. Multi-stage automatic transmission according to claim 29 or 30, characterized in that the first and fourth shifting elements (A, D) form a preassembled assembly which comprises the disk packs ( 100 . 400 ) of the first and fourth switching element (A, D) and an outer disk carrier common to the first and fourth switching element (A, D), a servo device ( 110 ) for actuating the plate pack ( 100 ) of the first switching element (A) and a servo device ( 410 ) for actuating the plate pack ( 400 ) of the fourth switching element (D) are at least partially integrated in this common outer, plate carrier. Multi-stage automatic transmission according to one of claims 1 to 30, characterized in that a External disk carrier of the first switching element (A) in the gear housing (GG) or in one with the gearbox (GG) non-rotatably connected partition wall (GZ) or in a gearbox-fixed housing wall (GW) which is an outer wall of the gearbox (GG) forms, is integrated. Multi-stage automatic transmission according to one of claims 1 to 30 or 32, characterized in that the servo device ( 110 ) of the first scarf telementes (A) in the gear housing (GG) or in a non-rotatably connected to the gear housing (GG) housing intermediate wall (GZ) or in a gear housing fixed housing wall (GW), which forms an outer wall of the gear housing (GG), is integrated. Multi-stage automatic transmission according to one of claims 1 to 32, characterized in that the actuating direction of the servo device ( 110 ) of the first switching element (A) and the direction of actuation of the servo device ( 410 ) of the fourth switching element (D) are opposite to each other when the respective switching element (A, D) is switched on. Multi-stage automatic transmission according to one of claims 1 to 33, characterized in that the actuating direction of the servo device ( 110 ) of the first switching element (A) and the direction of actuation of the servo device ( 410 ) of the fourth switching element (D) are rectified when the respective switching element (A, D) is switched on. Multi-stage automatic transmission according to one of claims 1 to 35, characterized in that at least one of the two servo devices ( 110 . 410 ) of the first and fourth switching elements (A, D) axially between the disk packs ( 100 . 400 ) of the first and fourth switching elements (C, D) is arranged. Multi-stage automatic transmission according to one of claims 1 to 36, characterized in that the drive shaft (AN) and output shaft (AB) are not coaxial to each other, especially that drive shaft (AN) and output shaft (AB) axially parallel or at an angle to each other run. Multi-stage automatic transmission according to one of claims 1 to 37, characterized in that a Spur gear stage (STST) or a chain drive is provided via the the ring gear (HO1) of the first planetary gear set (RS1) and with this ring gear (HO1) connected web (ST3, ST2) of the third or second planetary gear set (RS3, RS2) with the output shaft (AB) is operatively connected, a first spur gear (STR1) of the spur gear stage (STST) or a first sprocket of the chain drive axially between the third planetary gear set (RS3) and the first switching element (A) arranged is. Multi-stage automatic transmission according to claim 38, characterized characterized that the first spur gear (STR1) of the spur gear stage (STST) or the first sprocket of the chain drive on a partition wall (GZ) is mounted axially between the spur gear stage (STST) or Chain drive and third planetary gear set (RS3) is arranged, wherein this partition wall (GZ) non-rotatably connected to the gearbox housing (GG) or together with the gearbox (GG) in one piece accomplished is. Multi-stage automatic transmission according to claim 38, characterized characterized that the first spur gear (STR1) of the spur gear stage (STST) or the first sprocket of the chain drive on a partition wall (GZ) is mounted axially between the spur gear stage (STST) or Chain drive and the first switching element (A) is arranged, these Housing partition (GZ) non-rotatably connected to the gearbox housing (GG) or together with the gearbox (GG) in one piece accomplished is. Multi-stage automatic transmission according to Claim 38, 39 or 40, characterized in that the sun gear (SO3) of the third planetary gear set (RS3) or a sun shaft (SOW3) operatively connected to the sun gear (SO3) of the third planetary gear set (RS3) or a hub of the input element ( 120 ) of the first switching element engages centrally between the intermediate housing wall (GZ) and the first spur gear (STR1) of the spur gear stage (STST) or the first sprocket of the chain drive. Multi-stage automatic transmission according to one of claims 1 to 37, characterized in that a Spur gear stage (STST) or a chain drive is provided via the the ring gear (HO1) of the first planetary gear set (RS1) and with this ring gear (HO1) connected web (ST3, ST2) of the third or second planetary gear set (RS3, RS2) with the output shaft (AB) is operatively connected, a first spur gear (STR1) of the spur gear stage (STST) or a first chain wheel of the chain drive on an outer wall of the gearbox (GG) or a gearbox-fixed housing cover borders. Multi-stage automatic transmission according to claim 42, characterized characterized that the first spur gear (STR1) of the spur gear stage (STST) or the first sprocket of the chain drive on the outer wall of the gearbox (GG) or the gearbox fixed housing cover and / or is mounted on the drive shaft (AN). Multi-stage automatic transmission according to claim 42 or 43, characterized in that the first switching element (A) spatially seen between the third planetary gear set (RS3) and the first Spur gear (STR1) of the spur gear stage (STST) or between the third Planetary gear set (RS3) and the first chain wheel of the chain drive is arranged. Multi-stage automatic transmission according to claim 42 or 43, characterized in that the first shift element (A) is spatially arranged within a cylinder space which is formed by the first chain wheel of the chain drive, the first shift element (A) axially on the third planet wheelset (RS3) adjacent. Multi-stage automatic transmission according to claim 45, characterized in that a plate pack ( 100 ) of the first switching element (A) axially adjacent to the third planetary gear set (RS3). Multi-stage automatic transmission according to one of claims 1 to 36, characterized in that the drive shaft (AN) and output shaft (AB) run coaxially to each other. Multi-stage automatic transmission according to claim 47, characterized characterized that the connected to the ring gear (HO1) of the first planetary gear set (RS1) Output shaft (AB) the third planetary gear set (RS3) in axial Direction reaches through centrally. Multi-stage automatic transmission according to claim 47 or 48, characterized in that the output shaft (AB), which is operatively connected to the ring gear (HO1) of the first planetary gear set (RS1), has a clutch chamber of the first shift element (A), which is in particular provided by a disk carrier and / or the servo device ( 110 ) of the first switching element (A) is formed, penetrates centrally in the axial direction. Multi-stage automatic transmission according to claim 47, 48 or 49, characterized in that the drive shaft (AN) in the output shaft (AB) is mounted. Multi-stage automatic transmission according to one of claims 1 to 50, characterized in that by selective closing the switching elements (A to E) at least six forward gears in this way are switchable that for Switch from one gear to the next higher or next following lower gear from the shift elements just actuated each only one switching element opened and another switching element is closed. Multi-stage automatic transmission according to one of claims 1 to 51, characterized in that in the first forward gear the first and fourth shift elements (A, D), in the second forward gear the first and third shift elements (A, C), in the third forward gear the first and second shift elements (A, B), in the fourth forward gear the first and fifth Switching element (A, E), in the fifth forward gear the second and fifth Shift element (B, E), the third and fifth shift element in the sixth forward gear (C, E), and in a reverse gear that second and fourth switching element (B, D) are closed.