DE102014217885A1 - Transmission for a motor vehicle and method for operating the same - Google Patents

Abstract

Transmission (1) for a motor vehicle, with a housing (2), with a transmission input shaft (3), with a transmission output shaft (4), with a plurality of planetary gear sets (5, 6, 7), with a plurality of positive switching elements (A, B, C , D, E, F) and with a plurality of frictional power shift elements (K1, K2, B1), wherein a first planetary gear set (5) has a web (8) on which a planetary gear (9) is rotatably mounted, wherein the web (8 ) of the first planetary gear set (5) depending on the switching position of two first positive switching elements (A, B) with the housing (2) or with a web (16) of a third planetary gear set (7) on which a planet gear (13) rotatably mounted is, can be coupled; wherein a second planetary gear set (6) has a web (12) on which the planet gear (13) is rotatably mounted, wherein the ring gear (15) of the second planetary gear set (6) depends on the switching position of two second positive switching elements (E, F ) is coupled to the housing (2) or with the web (12) of the second planetary gear set (6); wherein the web (16) of the third planetary gear set (7) on which a planetary gear (17) is rotatably mounted, depending on the switching position of two third form-locking switching elements (C, D) without intermediate translation with the web (12) of the second planetary gear set ( 6) can be coupled; wherein a first load switching element (K1, B1) either between the web (8) of the first first planetary gear set (5) and with the web (8) of the first planetary gear set (5) cooperating first positive switching elements (A, B) or between the ring gear (11) of the first planetary gear set (5) and the sun gear (18) of the third planetary gear set (7) or between the ring gear (19) of the third planetary gear set (7) and the sun gear (14) of the second planetary gear set (6) or between the sun gear (10) of the first planetary gear set (5) and the housing (2) is connected; and wherein a second load switching element (K2) between the web (16) of the third planetary gear set (7) and with the web (12) of the second planetary gear set (6) cooperating third form-locking switching elements (C, D) is connected.

Description

The invention relates to a transmission for a motor vehicle and a method for operating the same.

From the DE 10 2004 014 082 A1 is a dual-clutch planetary gear known. The dual-clutch transmission has four planetary gear sets, two frictional shift elements and a plurality of form-locking switching elements. The frictional switching elements are provided for connecting different power paths in a power flow of the planetary gear. The interlocking switching elements are in turn provided for setting different gear ratios in the power paths of the planetary gear. Furthermore, the frictional switching elements and the form-locking switching elements are arranged between the shafts of the planetary gear sets, a housing or housing-fixed component of the planetary gear and a transmission input shaft and a transmission output shaft that gear stage changes over the frictional switching elements traction interruption-free feasible.

From the DE 10 2013 202 045 is a group transmission of a motor vehicle known. The group transmission comprises a multi-stage main transmission and a drive unit subordinate to the main transmission range group. The range group is designed in planetary design and includes two coupled planetary gear sets, each with a sun gear, planetary carrier carrying several planetary gears and a ring gear. The two planetary gear sets of the range group are arranged coaxially and axially staggered to one another, wherein the first planetary gear set is arranged axially between the main gear and the second planetary gear set. The sun gear of the first planetary gear set is rotatably connected to the main shaft of the main transmission and thus forms the input element of the range group. The planet carrier of the first planetary gear set is rotatably connected to the ring gear of the second planetary gear set. The ring gear of the first planetary gear set is rotatably connected to the sun gear of the second planetary gear set. The planet carrier of the second planetary gear set is rotatably connected to the output shaft and thus forms the output element of the range group.

From the DE 10 2013 213 590 is a transmission for a motor vehicle, with a housing, with a transmission input shaft, with a transmission output shaft, with several planetary gear sets, with a plurality of form-locking switching elements and with a plurality of frictional power shift elements known.

Proceeding from this, the object of the present invention is to provide a novel transmission, which has a simple structure and is load-shiftable, and a method for operating the same.

This object is achieved by a transmission according to claim 1.

According to the invention, a first planetary gear set has a web on which a planet gear is rotatably mounted, wherein the web of the first planetary gear depending on the switching position of two first positive switching elements with the housing or with the web of a third planetary gear, on which a planet gear is rotatably mounted , can be coupled. A second planetary gear set has a web on which a planet gear is rotatably mounted, wherein the ring gear of the second planetary gear set can be coupled depending on the switching position of two second interlocking switching elements with the housing or with the web of the second planetary gear set. The web of the third planetary gear, on which the planetary gear is rotatably supported thereof, is coupled depending on the switching position of two third form-fitting switching elements without intermediate translation with the web of the second planetary gear set. A first power shift element is either between the web of the first first planetary gear set and cooperating with the first gearset first interlocking first switching elements or between the ring gear of the first planetary and the sun of the third planetary or between the ring gear of the third planetary gear and the sun gear of the second planetary gear set or between the sun gear of the first planetary gear set and the housing. A second load switching element is connected between the web of the third planetary gear set and cooperating with the web of the second planetary gear third form-locking switching elements. The transmission according to the invention has a simple structure and is power shiftable.

According to an advantageous embodiment of the invention, when the second load switching element and one of the two third form-locking switching elements is closed, the webs of the second planetary and third planetary gear set coupled without intermediate translation, whereas, when the second load switching element and the other of the third form-locking switching elements closed is, the web of the third planetary gear set is coupled to the sun gear of the second planetary gear set without intermediate translation. This embodiment of the transmission according to the invention is to provide a transmission, which has a simple structure and is power shiftable, preferably.

According to a further advantageous embodiment of the invention, when the first load switching element is connected between the web of the first planetary gear and cooperating with the web of the first planetary gear first positive switching elements, the sun gear of the first planetary gear directly to the housing and the ring gear of the first planetary gear without intermediate translation rotatably coupled to the sun gear of the third planetary gear and the ring gear of the third planetary gear set without intermediate translation rotationally fixed to the sun gear of the second planetary gear set; whereas, when the first load switching element is connected between the ring gear of the first planetary gear set and the sun gear of the third planetary gear set, the sun gear of the first planetary gear set is coupled to the housing and the ring gear of the third planetary gear set without rotation transmission to the sun gear of the second planetary gear set; whereas, when the first load switching element is interposed between the ring gear of the third planetary gear set and the sun gear of the second planetary gear set, the sun gear of the first planetary gear set is directly coupled to the housing and the ring gear of the first planetary gear set without rotation transmission to the sun gear of the third planetary gear set; whereas, when the first load switching element is interposed between the sun gear of the first planetary gear set and the housing, the ring gear of the first planetary gear set is non-rotatably coupled to the sun gear of the third planetary gear set and the ring gear of the third planetary gear set without intermediate gear to the sun gear of the second planetary gear set. These embodiments are preferred for providing a transmission which has a simple construction and is load-shiftable.

According to an advantageous development of the invention, the first, second and third planetary gear sets provide a main transmission with six forward gears, the highest of these six forward gears being an overdrive gear and the second highest of these six forward gears being a direct gear. In direct gear, the web of the third planetary gear set is rotatably coupled without intermediate translation with the web of the second planetary gear set.

The main transmission is preceded by a first alternative, a further planetary gear and other form-fitting shift elements comprehensive upstream group, such that six forward gears and six reverse gears are available. According to a second alternative, the main transmission is followed by a two further planetary gear sets and several other form-fitting switching elements comprehensive rear group, such that twelve forward gears and six reverse gears are available. These embodiments are preferred for providing a transmission with reverse gears, which has a simple structure and is power shiftable.

Preferably, all form-locking switching elements and all frictional load switching elements are arranged accessible from the outside in the housing. This embodiment of the transmission according to the invention is to provide a transmission which has a simple structure and is power shiftable, preferred.

The method according to the invention is defined in claim 10.

Preferred developments emerge from the subclaims and the following description. Embodiments of the invention will be described, without being limited thereto, with reference to the drawings. Showing:

1 a diagram of a first transmission according to the invention;

2 a switching matrix for the transmission of 1 ;

3 a diagram of a second transmission according to the invention;

4 a schematic of a third transmission according to the invention;

5 a diagram of a fourth transmission according to the invention;

6 a diagram of a fifth transmission according to the invention; and

7 a diagram of another transmission according to the invention.

The present invention relates to a transmission for a motor vehicle.

1 shows a first embodiment of a transmission according to the invention 1 for motor vehicle. The gear 1 of the 1 has a housing 2 , a transmission input shaft 3 , a transmission output shaft 4 as well as several planetary gear sets 5 . 6 and 7 , namely in 1 over three planetary gear sets 5 . 6 and 7 wherein each planetary gear set comprises a land, a planet gear, a sun gear and a ring gear.

In addition, the transmission includes 1 of the 1 a plurality of positive switching elements, namely according to 1 six positive-locking switching elements A, B, C, D, E and F, as well as two frictional load switching elements K1 and K2, the after 1 are designed as power shift clutches.

A first planetary gear set 5 has a footbridge 8th on which a planetary gear 9 is rotatably mounted. The jetty 8th of the first planetary gear set 5 is dependent on the switching position of two first positive switching elements A and B to the housing 2 or with the jetty 16 a third planetary gear set 7 coupled.

The two first positive switching elements A and B are according to 1 provided by a double switching element, wherein only one of these two positive switching elements A and B can be closed. Both positive-locking switching elements A and B can be opened.

Then, when the positive switching element B is closed, the web is 8th of the first planetary gear set 5 to the housing 2 coupled, whereas, when the other of these two positive switching elements, namely the switching element A, is closed, the web 8th of the first planetary gear set 5 to the jetty 16 of the third planetary gear set 7 can be coupled.

A second planetary gear set 6 has a footbridge 12 on which a planetary gear 13 is rotatably mounted. The ring gear 15 this second planetary gear set 16 is dependent on the switching position of two second positive switching elements E and F to the housing 2 or with the jetty 12 of the second planetary gear set 6 coupled. The two second positive switching elements E and F are in turn provided by a double switching element, wherein only one of these two positive switching elements E and F can be closed. Both positive-locking switching elements E and F can be opened.

Then, when the switching element E is closed, the ring gear is 15 of the second planetary gear set 6 to the housing 2 coupled. Then, however, when the form-fitting switching element F is closed, are the ring gear 15 of the second planetary gear set 6 and the bridge of the second planetary gear set 6 rotatably coupled.

In addition to the first, input-side planetary gear set 5 and the second gear output side planetary gear set 6 includes the gearbox 1 the third planetary gear set 7 that is between the first planetary gear set 5 and the second planetary gear set 6 is positioned. The jetty 16 of the third planetary gear set 7 on which a planetary gear 17 is rotatably mounted, is dependent on the switching position of two third form-locking switching elements C and D without intermediate translation with the web 12 of the second planetary gear set 6 coupled. The two third interlocking switching elements C and D are in turn provided by a double switching element, wherein only one of these two third interlocking switching elements C and D can be closed. Both form-locking switching elements C and D can be opened.

Then, when the positive switching element D is closed, the web is 16 of the third planetary gear set 7 without intermediate translation with the bridge 12 of the second planetary gear set 6 coupled. Then, however, when the positive switching element C is closed, the web is 16 of the third planetary gear set 7 with the sun wheel 14 of the second planetary gear set 6 Coupled without intermediate translation.

In addition to the above-mentioned positive switching elements A to F, the transmission includes 1 two friction load switching elements K1 and K2.

In 1 is first load switching element K1 between the web 8th of the first planetary gear set 5 and those with the jetty 8th of the first planetary gear set 5 cooperating, first positive switching elements A and B connected. Then, when the load switching element K1 and further the switching element B are both closed, the web is 8th of the first planetary gear set 5 to the housing 2 coupled. Then, however, when the load switching element K1 and the positive switching element A are both closed, the web is 8th of the first planetary gear set 5 rotatably to the bridge 16 of the third planetary gear set 7 coupled.

In the case where the first load switching element K1 of the transmission 1 between the jetty 8th of the first planetary gear set 5 and those with the jetty 8th of the first planetary gear set 5 cooperating first positive switching elements A and B is connected, is the sun gear 10 of the first planetary gear set 5 directly to the housing 2 coupled. Further, the ring gear 11 of the first planetary gear set 5 immediately without intermediate translation rotatably to the sun gear 18 of the third planetary gear set 7 coupled. Further, the ring gear 19 of the third planetary gear set 7 without intermediate translation rotatably to the sun gear 14 of the second planetary gear set 6 coupled.

Furthermore, the gearbox has 1 of the 1 via a second load switching element K2, which between the web 16 of the third planetary gear set 7 and those with the jetty 12 of the second planetary gear set 6 cooperating third positive switching elements C, D is connected.

Then, when the power-shift clutch K2 and the positive shift element D are both closed, the webs are 16 and 12 the two planetary gear sets 6 and 7 rotatably coupled and without intermediate translation to each other.

On the other hand, when the second power-shift clutch K2 and the other of the third interlocking shift elements C are both closed, the web is 16 of the third planetary gear set 7 directly and rotationally without intermediate translation to the sun gear 14 of the second planetary gear set 6 coupled.

The transmission of 1 therefore comprises two partial transmissions, wherein a first partial transmission all three planetary gear sets 5 . 6 and 7 uses and a second partial transmission only the third planetary gear 7 uses. With both partial transmissions, a frictional power shift element K1, K2 cooperates to execute load circuits, wherein these power shift clutches K1 and K2 are distributed clutches which have no common drive shaft. Therefore, the in 1 shown gear 1 not a classic dual-clutch transmission.

The first partial transmission 1 , which all three planetary gear sets 5 . 6 and 7 uses, provides four translations or four courses. The two form-fitting switching elements A and B switch thereby two translations or gears. The switching element A switches a so-called underdrive transmission, via the planetary gear sets 5 and 7 is generated, namely such that the sun gear 18 of the third planetary gear set 7 over the first planetary gear set 5 is driven up. The form-locking switching element B switches a so-called overdrive ratio, which is transmitted via the third planetary gear set 7 is generated, in which case the sun 18 of the third planetary gear set 7 is stalled. These two translations are from the second planetary gear set 6 doubled, so that then a total of four forward gears are provided.

The second partial transmission uses only the second planetary gear set 6 , which is used by both partial transmissions. It provides two translations or aisles. The positive switching element C switches for this second partial transmission a so-called direct gear with a ratio of 1.0. This direct gear is via the second planetary gear set 6 used twice. The positive switching element D also switches the direct gear independently of the second planetary gear set 6 , This allows the second planetary gear set 6 be switched without load with the form-locking switching elements E and F as the background circuit.

With the transmission 1 of the 1 can therefore six forward gears using the in 2 shown switching matrix can be provided. Positive shift elements A to F and friction-locked load shift elements K1 and K2, which are closed in the respective forward gear, are in the switching matrix of 2 marked by an X.

Furthermore, the switching matrix shows the 2 exemplary ratios i of the six forward gears and exemplary gear ratios phi between the individual forward gears, assuming a stationary gear ratio i0 of the first planetary gear set 5 of i0 = -1.4, a stationary gear ratio i0 of the second planetary gear set 6 of i0 = -1.79 and a stationary gear ratio i0 of the third planetary gear set 7 of i0 = -2.46. As a result, the gear ratios i and the gear ratios phi of the switching matrix of the 2 ,

The switching matrix of 2 It can be seen that the highest of the six forward gears is an overdrive gear. The second highest of these six forward gears is a direct gear. In the direct gear is the web with closed positive switching element D and closed load clutch K2 16 of the third planetary gear set 7 rotatable and without intermediate translation with the bridge 12 of the second planetary gear set 6 coupled.

In the embodiment of the switching matrix of 2 are identical gear gradations phi for the individual gears, so that accordingly in the embodiment of 1 and 2 a geometric gear gradation is used. Such a geometric gear gradation is advantageous because the second planetary gear 6 for the other two planetary gear sets 5 and 7 acts as a scope group.

By changing the stationary gear ratios i0 for the three planetary gear sets 5 . 6 and 7 can be adapted to the gear step. If smaller gear jumps are desirable, it is advantageous to use the second planetary gear set 6 Run as a so-called Stufenplanetenradsatz to ensure a small amount stationary gear ratio. In such a stepped planetary gear set two planetary gears are arranged on a common web, wherein a first planetary gear meshes only with the sun gear and the other planetary gear with only the ring gear.

In the transmission 1 according to the embodiment of the 1 and 2 are circuits between the forward gears 1 and 2 , the forward gears 2 and 3 , the forward gears 4 and 5 and the forward gears 5 and 6 Conventionally power-shiftable, namely by a change between the frictional power shift clutches K1 and K2.

To ensure a load connection between the forward gears 3 and 4 is the circuit between the forward gears 3 and 4 According to the invention designed as a support circuit. In the forward gears 3 and 4 , between which a gear change is performed as a support gear, are two immediately successive courses, of which the higher gear is located directly below the direct gear, in which the webs 16 . 12 the two planetary gear sets 6 . 7 are coupled non-rotatably without interposition. To perform this circuit as a support gear shift from the actual gear in the target gear is driven while driving in the actual gear on the power shift clutch K1 and selected as a support gear that one gear in which the webs 16 . 12 the planetary gear sets 6 . 7 rotatably coupled without intermediate translation. This is done by load-free closing of the switching element D. Subsequently, a load transfer takes place by the load switching element K2 via the support gear. Subsequently, the support gear carries all the load and transmits the whole of a drive unit to the transmission input shaft 3 provided moment, so that the gear change from the actual gear to the target gear can be performed without load. Subsequently, a load transfer takes place back to the power shift clutches K1, so that then can be driven in the target gear.

3 shows a variant of the transmission 1 of the 1 , which differs from the embodiment of 1 only differs by the positioning of the first power-shift clutch K1. Therefore, to avoid unnecessary repetition for the same components same reference numerals are used and it is on the comments on the embodiment of 1 and 2 directed. The gear 1 of the 3 uses the switching matrix of 2 , The embodiment of 3 differs from the embodiment of 1 only in that in the embodiment of the 1 the first power shift clutch K1 between the ring gear 11 of the first planetary gear set 5 and the sun wheel 8th of the third planetary gear set 7 is switched. In this case, the sun gear 10 of the first planetary gear set 5 directly to the housing 2 coupled. When switching element B is closed, the web is also 8th of the first planetary gear set 5 to the housing 2 coupled, whereas, when the positive switching element A is closed, the web 8th of the first planetary gear set 5 directly and rotationally fixed to the bridge 16 of the third planetary gear set 7 is coupled.

Then, when the first load switching element K1 between the ring gear 11 of the first planetary gear set 5 and the sun wheel 18 of the third planetary gear set 7 is switched, is therefore the sun 10 of the first planetary gear set 5 directly to the housing 2 and the ring gear 19 of the third planetary gear set 7 without intermediate translation rotatably to the sun gear 14 of the second planetary gear set 6 coupled.

Another variant of the transmission 1 of the 1 shows 4 , wherein also in the embodiment of 4 to avoid unnecessary repetitions for the same components same reference numerals are used and to the comments on the embodiment of 1 is referenced. The gear 1 of the 4 uses the switching matrix of 2 ,

The embodiment of 4 differs from the embodiment of 1 in that the first power shift clutch K1 between the ring gear 19 of the third planetary gear set 7 and the sun wheel 14 of the second planetary gear set 6 is switched. The sun wheel 10 of the first planetary gear set 5 is in accordance to 3 directly to the housing 2 coupled. In 4 is still the ring gear 11 of the first planetary gear set 5 in accordance to 1 immediately without intermediate translation to the sun gear 18 of the third planetary gear set 7 coupled.

In the embodiments of the 1 to 4 is the first load switching element K1 each designed as a power shift clutch.

In contrast, shows 5 a variant in which the first load switching element is designed as a powershift brake B1, between the sun gear 10 of the first planetary gear set 5 and the case 2 of the transmission 1 is switched. The ring gear 11 of the first planetary gear set 5 is then back to rotation and immediately without intermediate translation to the sun gear 18 of the third planetary gear set 7 coupled. Further, the ring gear 19 of the third planetary gear set 7 without intermediate translation to the sun gear 14 of the second planetary gear set 6 coupled.

With the in 1 to 5 shown gear 1 however, six forward gears each can not provide a reverse gear. 6 and 7 show further developments of the gearbox 1 of the 1 that serve to provide reverse gears.

So is in the variant of 1 the main gearbox of the three planetary gear sets 5 . 6 and 7 which can provide six forward gears, another planetary gear set 20 upstream, which cooperates with two other form-fitting switching elements V and R. On the jetty 21 Furthermore planetary gear 20 is a planetary gear 22 rotatably mounted, the web 21 depending on the switching position of the form-locking switching elements V and R either to the housing 2 or to the transmission input shaft 3 is coupled. The two form-locking switching elements V and R are in turn provided by a double switching element, wherein only one of these form-locking switching elements V and R can be closed.

The sun wheel 23 the other planetary gear set 20 is non-rotatable with the transmission input shaft 3 and the ring gear 24 the other planetary gear set 20 rotatably to the bridge 16 of the third planetary gear set 7 coupled. To provide forward gears, the positive switching element V and the provision of reverse gears, the positive switching element R is closed, wherein by the transmission 1 of the 6 six forward gears and six reverse gears can be provided.

The reverse gears are translated shorter than the forward gears, namely the factor of the stationary gear ratio i0 of the other planetary gear set 20 , In the shorter reverse gears is a limit of the at the transmission input shaft 3 provided drive torque possible because otherwise the reverse gears with respect to the torque load interpretation relevant to the transmission 1 would.

Short reverse gears are beneficial for sensitive maneuvering and reversing. The forward gears and reverse gears are each power shiftable.

Another variant of the transmission 1 of the 1 shows 7 , where in 7 the main gearbox of the three planetary gear sets 5 . 6 and 7 a downstream group is connected, the two other planetary gear sets 25 and 26 and three other form-fitting switching elements R, H and L includes. As a result, a total of twelve forward gears and six reverse gears are available.

According to 7 is the sun wheel 31 of the inner planetary gear set 25 the Nachschaltgruppe rotatably and immediately without intermediate translation to the bridge 12 of the second planetary gear set 6 coupled to the main transmission. The jetty 27 this inner planetary gear set 25 The rear-mounted group is non-rotatable to the ring gear 33 of the outer planetary gear set 26 coupled to the rear group. The jetty 28 of the outer planetary gear set 26 The rear-mounted group is non-rotatable with the transmission output shaft 4 coupled. The ring gear 32 and the sun wheel 34 the two planetary gear sets 25 and 26 the Nachschaltgruppe are rotatably coupled and are provided in the illustrated embodiment of a component, which depends on the switching position of the form-locking switching elements H and L either to the housing 2 or to the jetty 27 of the inner planetary gear set 25 the rear-group is coupled.

The two form-fitting switching elements H and L are in turn provided by a double switching element, wherein only one of these two positive switching elements H and L can be closed. The switching element R of the Nachschaltgruppe serves to provide a reverse gear, wherein in the reverse gears, the switching element R is closed to the web 27 of the inner planetary gear set 25 the rear group to the housing 2 to dock.

In the transmission 1 of the 7 can be provided twelve forward gears and six reverse gears, so that therefore the forward gears of the planetary gear sets 5 . 6 and 7 comprehensive main gearbox. Gear change between the forward gear 6 and the forward gear 7 , So a change between the form-locking switching elements L and H is only zugkraftunterbrochen executable. All other gear changes between forward gears and reverse gears, however, are power shiftable. The switch between a forward gear and a reverse gear are not power shiftable.

Although the variants of 6 and 7 in connection with the main transmission of 1 are shown, these variants are also with the gears of the 3 to 5 available.

In all the embodiments shown, preferably all interlocking shift elements and all frictional power shift elements are arranged accessible from the outside in the housing, so that therefore all switching elements via shift forks are easily actuated, with no so-called Topfdurchgriffe are required for the shift forks. This allows a particularly simple structural design of the transmission 1 ,

Form-fitting switching elements can either be synchronized conventionally as individually synchronized switching elements or via a central synchronization.

LIST OF REFERENCE NUMBERS

1

transmission

2

casing

3

Transmission input shaft

4

Transmission output shaft

5

planetary gear

6

planetary gear

7

planetary gear

8th

web

9

planet

10

sun

11

ring gear

12

web

13

planet

14

sun

15

ring gear

16

web

17

planet

18

sun

19

ring gear

20

planetary gear

21

web

22

planet

23

sun

24

ring gear

25

planetary gear

26

planetary gear

27

web

28

web

29

planet

30

planet

31

sun

32

ring gear

33

ring gear

34

sun

K1

Load switching element

K2

Load switching element

A

switching element

B

switching element

C

switching element

D

switching element

e

switching element

F

switching element

R

switching element

H

switching element

L

switching element

V

switching element

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• DE 102004014082 A1 [0002]
• DE 102013202045 [0003]
• DE 102013213590 [0004]

Claims (10)

Transmission ( 1 ) for a motor vehicle, with a housing ( 2 ), with a transmission input shaft ( 3 ), with a transmission output shaft ( 4 ), with several planetary gear sets ( 5 . 6 . 7 ), with a plurality of positive shifting elements (A, B, C, D, E, F) and with a plurality of frictional power shift elements (K1, K2, B1), characterized in that a first planetary gear set ( 5 ) a footbridge ( 8th ), on which a planetary gear ( 9 ) is rotatably mounted, wherein the web ( 8th ) of the first planetary gear set ( 5 ) depending on the switching position of two first positive switching elements (A, B) with the housing ( 2 ) or with a bridge ( 16 ) of a third planetary gear set ( 7 ) on which a planetary gear ( 13 ) is rotatably mounted, can be coupled; a second planetary gear set ( 6 ) a footbridge ( 12 ), on which the planetary gear ( 13 ) is rotatably mounted, wherein the ring gear ( 15 ) of the second planetary gear set ( 6 ) depending on the switching position of two second form-locking switching elements (E, F) with the housing ( 2 ) or with the bridge ( 12 ) of the second planetary gear set ( 6 ) can be coupled; the footbridge ( 16 ) of the third planetary gear set ( 7 ) on which a planetary gear ( 17 ) is rotatably mounted, depending on the switching position of two third form-fitting switching elements (C, D) without intermediate translation with the web ( 12 ) of the second planetary gear set ( 6 ) can be coupled; a first load switching element (K1, B1) either between the web ( 8th ) of the first first planetary gear set ( 5 ) and those with the bridge ( 8th ) of the first planetary gear set ( 5 ) cooperating first positive switching elements (A, B) or between the ring gear ( 11 ) of the first planetary gear set ( 5 ) and the sun wheel ( 18 ) of the third planetary gear set ( 7 ) or between the ring gear ( 19 ) of the third planetary gear set ( 7 ) and the sun wheel ( 14 ) of the second planetary gear set ( 6 ) or between the sun wheel ( 10 ) of the first planetary gear set ( 5 ) and the housing ( 2 ) is switched; a second load switching element (K2) between the web ( 16 ) of the third planetary gear set ( 7 ) and those with the bridge ( 12 ) of the second planetary gear set ( 6 ) cooperating third positive switching elements (C, D) is connected. Transmission according to claim 1, characterized in that, when the second load switching element (K2) and one of the two third form-fitting switching elements (D) is closed, the webs ( 16 . 12 ) from the second planetary gear set ( 6 ) and third planetary gear set ( 7 ) are coupled without intermediate translation, and that when the second load switching element (K2) and the other of the third positive-locking switching elements (C) is closed, the web ( 16 ) of the third planetary gear set ( 7 ) to the sun wheel ( 14 ) of the second planetary gear set ( 7 ) is coupled without intermediate translation. Transmission according to claim 1 or 2, characterized in that when the first load switching element (K1) between the web ( 8th ) of the first planetary gear set ( 5 ) and those with the bridge ( 8th ) of the first planetary gear set ( 5 ) cooperating first positive switching elements (A, B) is connected, the sun gear ( 10 ) of the first planetary gear set ( 5 ) directly to the housing ( 2 ) and the ring gear ( 11 ) of the first planetary gear set ( 5 ) without intermediate translation rotatably to the sun gear ( 18 ) of the third planetary gear set ( 7 ) and the ring gear ( 19 ) of the third planetary gear set ( 7 ) without intermediate translation rotatably to the sun gear ( 14 ) of the second planetary gear set ( 6 ) is coupled; when the first load switching element (K1) between the ring gear ( 11 ) of the first planetary gear set ( 5 ) and the sun wheel ( 18 ) of the third planetary gear set ( 7 ), the sun gear ( 10 ) of the first planetary gear set ( 5 ) directly to the housing ( 2 ) and the ring gear ( 19 ) of the third planetary gear set ( 7 ) without intermediate translation rotatably to the sun gear ( 14 ) of the second planetary gear set ( 6 ) is coupled; when the first load switching element (K1) between the ring gear ( 19 ) of the third planetary gear set ( 7 ) and the sun wheel ( 14 ) of the second planetary gear set ( 6 ), the sun gear ( 10 ) of the first planetary gear set ( 5 ) directly to the housing ( 2 ) and the ring gear ( 11 ) of the first planetary gear set ( 5 ) without intermediate translation rotatably to the sun gear ( 18 ) of the third planetary gear set ( 7 ) is coupled; when the first load switching element (B1) between the sun gear ( 10 ) of the first planetary gear set ( 5 ) and the housing is connected, the ring gear ( 11 ) of the first planetary gear set without intermediate translation rotatably to the sun gear ( 18 ) of the third planetary gear set ( 7 ) and the ring gear ( 19 ) of the third planetary gear set without intermediate translation to the sun gear ( 14 ) of the second planetary gear set is coupled. Transmission according to one of claims 1 to 3, characterized in that the first planetary gear set ( 5 ), the second planetary gear set ( 6 ) and the third planetary gear set ( 7 ) provide a main transmission with six forward gears, wherein the highest of said six forward gear is an overdrive gear, and wherein the second highest of said six forward gear is a direct gear, in which the web ( 16 ) of the third planetary gear set ( 7 ) rotatably without intermediate translation with the bridge ( 12 ) of the second planetary gear set ( 6 ) is coupled. Transmission according to claim 4, characterized in that the main transmission is a further planetary gear ( 20 ) and two other form-locking switching elements (V, R) comprehensive upstream group is connected in such a way that six Forward gears and six reverse gears are available. Transmission according to claim 5, characterized in that a sun gear ( 23 ) of the further planetary gear set ( 20 ) to the transmission input shaft ( 3 ) is rotatably coupled, wherein a ring gear ( 24 ) of the further planetary gear set ( 20 ) to the pier ( 16 ) of the third planetary gear set ( 7 ) is rotatably coupled, wherein a first of the further switching elements (V) for providing the forward gears of the web ( 21 ) of the further planetary gear set ( 20 ) to the transmission input shaft ( 3 rotatably coupled, and wherein a second of the further switching elements (R) for providing the reverse gears of the web ( 21 ) of the further planetary gear set ( 20 ) to the housing ( 2 ) couples. Transmission according to Claim 4, characterized in that the main gearbox has an inner and outer planetary gear set ( 25 . 26 ) and a plurality of other form-fitting switching elements (R, H, L) comprehensive downstream group is followed, such that twelve forward gears and six reverse gears are available. Transmission according to claim 7, characterized in that the sun gear ( 31 ) of the inner planetary gear set ( 25 ) with the bridge ( 12 ) of the second planetary gear set ( 6 ) is rotatably coupled, wherein the web ( 27 ) of the inner planetary gear set ( 25 ) with the ring gear ( 33 ) of the outer planetary gear set ( 26 ) is rotatably coupled, wherein the ring gear ( 32 ) of the outer planetary gear set with the sun gear ( 34 ) of the inner planetary gear set is rotatably coupled, and wherein the web ( 28 ) of the outer planetary gear set ( 26 ) rotatably with the transmission output shaft ( 4 ) is coupled. Transmission according to one of claims 1 to 8, characterized in that all the positive switching elements (A, B, C, D, E, F) and all frictional load switching elements (K1, K2, B2) accessible from the outside (in the housing 2 ) are arranged. A method of operating a transmission according to any one of claims 1 to 9, characterized in that a gear change from an actual gear to a target gear between two immediately successive gears, of which the higher gear is immediately below that gear, in which the Footbridge ( 16 ) of the third planetary gear set ( 7 ) rotatably without intermediate translation with the bridge ( 12 ) of the second planetary gear set ( 6 ), is executed as a support gearshift, namely such that when driving in the actual gear that passage in which the web ( 16 ) of the third planetary gear set ( 7 ) rotatably without intermediate translation with the bridge ( 12 ) of the second planetary gear set ( 6 ), is selected as a support gear, then a load transfer from the actual gear is performed in the support gear, then the gear change is performed by the actual gear in the target gear load-free, and then a load transfer from the support gear in the target gear is carried out.

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