DE102008011338A1 - Automatic transmission e.g. differential transmission, for motor vehicle, has braking device for applying brake force causing brake torque, and planetary unit with effective surfaces disposed to part laterally adjacent to planetary wheel - Google Patents

Abstract

The transmission has a drive train arranged in a transmission housing (3) for transmitting or distributing force. A braking device (13) is provided for applying a brake force causing a brake torque. A planetary unit (5) has effective surfaces provided for discharging the brake torque into the planetary unit. The effective surfaces are provided on both sides of a planetary wheel (9) and disposed to a part laterally adjacent to the planetary wheel.

Description

The The invention relates to an automatic transmission for a motor vehicle, in particular for an automatic transmission as a power transmission, but not for Compensating and transfer case, with a gearbox housing and a gear train disposed in the transmission housing for transmitting or distributing a force, the powertrain a Planenteneinheit with a planet and on it arranged planetary gears includes.

Such Gearboxes are, for example, as a manual transmission of an automatic transmission used, in these transmissions then via the planetary gear and the variation of its degrees of freedom, for example, the Switching stages can be realized to be dependent speed, engine load and vehicle speed different ratios to be able to switch between drive and drive wheels. However, the invention is not limited to this application, Rather, the invention is applicable everywhere, where within a Getriebes a planetary gear should be used that through Braking the planetary unit assumes a function. In particular, these can also be transmissions that are related used with hybrid drives.

The Planet unit can have multiple planetary gear pairs and a planet carrier comprising, wherein the Planetenradpaare on with the planet carrier connected Planetenradpaarwellen are arranged and one each having first planetary gear and a second planetary gear.

Such transmissions are known in particular as differential gears, as in the PCT / EP2006 / 008486 are described. Here, the differential gears are used as a transverse compensation of the different speeds of the wheels, resulting in cornering due to the different path lengths of the lanes. The drive torque is to be transmitted symmetrically and therefore free of moments of yaw moment on the individual wheels. In certain driving situations or for influencing the driving character of a motor vehicle, however, it may be desirable to specifically intervene in the driving force distribution to the individual wheels and to optimize the driving behavior thereby or to relieve the driver in critical situations. This can be done by braking intervention as well as by influencing the distribution of the drive power of a differential gear to the individual wheels.

One Differential gear of the type mentioned has the special feature on that on actuation of the brake device, the otherwise with the drive basket and output shaft co-rotating planetary unit can be slowed down or blocked.

at not operated brake device rotates the planetary unit in the block around the output shaft. The differential meets the function of a standard differential. When pressed the braking device is because the individual planet gears the Planetenradpaare have different effective diameter, as a result of deceleration of the planetary unit via the intermediate gear transmitted to the output shaft, a torque that the Output shaft compared to operation when not actuated Braking device accelerates or decelerates. hereby is specifically generated a yaw moment, by the different Speeds of the drive wheels or by the resulting different drive wheel torque or Antriebsraddrehzahlen on both sides of the vehicle is caused.

in the Unlike differentials that only have an active lock, the maximum blocking value of the output shaft speeds at maximum allows, can be achieved even the outside Drive wheel, which is due to a conventional differential the longer outer lane faster turns as the inside drive wheel over which turns the lane length resulting wheel speed is accelerated.

By Targeted activation of a yaw moment can be used in a wide variety of driving situations corrective action is taken in the driving behavior of the vehicle, or it can be a vehicle with special handling characteristics, in particular particular curve turning, be created. Because of the Possible connection of a yaw moment are such Transmission also called "Active-Yaw" transmission.

Such a differential is from the US 6,120,407 known. In this differential gear, the planetary unit can be braked via a arranged on an outer circumferential surface of a disc-shaped base body of the planet carrier braking device. For this purpose, the braking device has a friction lamination stack which can be compressed via a hydraulic unit. In this case, active surfaces in the form of inner disks are provided on the planet carrier, which are arranged non-rotatably on acting as an inner disk carrier planet carrier, while the outer disks are rotatably mounted on the stationary transmission housing.

However, this embodiment has the disadvantage that the braking device and the active surfaces are widely spaced from the planetary unit, resulting in a structurally complex, large and thus also relatively heavy and expensive planetary unit leads. The masses of the planetary unit to be accelerated and braked are relatively high. Also, such a design requires an increased space requirement of the entire differential gear. In addition, due to the different diameters of the first and second planetary gear, the forces acting on these planetary gears apply a moment to the planetary unit, which in the known embodiment has to be absorbed by a complex mounting of the planetary unit. In addition, a complex axial bearing of the planetary unit is also required for location-accurate positioning of the braking device.

task the invention is to provide a transmission of a general kind, that the advantages of decelerating the planetary unit from the described Balancing transmissions takes over so easily and easily also z. B. transmission, in particular automatic transmission, to be able to switch.

These The object is achieved according to the invention in that a braking device is provided, the means for applying having a braking torque causing braking force, and the braking torque Braking the planetary unit relative to the gearbox housing able, wherein the planetary unit has effective surfaces, which are provided for the initiation of the braking torque in the planetary unit and the active surfaces provided on both sides of the Planetenradpaare and at least partially arranged laterally next to the Planetenradpaaren are.

Provided the invention hereinafter partially with reference to a differential is to be considered that essential Core of the invention, the deceleration of the planetary unit over the arrangement of the active surfaces is and not on the here unclaimed differential be limited should. Therefore, the following description shall be understood as that the merits and details described in all ways of transmissions containing a planetary unit, in particular to automatic transmissions of a motor vehicle.

By This arrangement of the active surfaces becomes a more compact design allows. The braking force can be right next to the planetary unit attack. An arrangement of the brake device at a far from the axis of rotation of the intermediate gear spaced location is not required. In the outer area of the planetary unit the masses to be moved are reduced. By arranging the Impact surfaces on both sides of the planetary unit is achieved that the forces and moments in operation over the Planetenradpaare act on the planetary unit, immediately above the effective surfaces act on the braking device and be intercepted by this. braking force and braking torque directly to the planetary unit, without over a constructively complex to be designed planet carrier directed to a radially outboard brake device to have to. This also eliminates one complex axial bearing. An exact positioning of the planetary unit is due to the immediately adjacent to the active surfaces Brake device guaranteed.

The inventive design saves because the smaller space requirement, the simpler structural design and the low weight also costs, both in operation and in the development and production. In addition, leads the low weight and the compact design to one opposite the state of the art more stable and lighter planetary unit, so that intervention of the braking device safer, more precise, can be done faster and better dosed. The regulation and monitoring the interventions is thus optimized.

Around Braking force and braking torque to initiate in the planetary unit is further provided that the braking device for initiating the Braking torque in the planetary unit on both sides of the planetary unit Has Reiblammellen. Reiblamellen have a Reibbelagsschicht on, the usual way on a body is applied and about the required braking torque in a very efficient way over the active surfaces can be transmitted to the planetary unit. Further have friction plates over other measures to initiate a braking torque a very high power to weight ratio and a low footprint with low costs and high durability, resulting in compactness and constructive Simplicity of the differential or automatic transmission contributes.

In a preferred embodiment is at least the means for Applying the braking force facing friction plate as a force introduction lamella slidable in the direction of the braking force and transmits the braking force on the their facing surfaces of the Planetary unit. Thus, this allows for free rotation of the planetary unit required clearance from the force introduction louvre bridges be before the active surfaces of the planetary unit at the Brake device applied and effectively braked.

In order to simplify the differential further constructive, it is preferably provided that the means for applying the braking force are arranged only on one side of the planetary unit and that arranged on the other side of the planetary unit friction plate is designed as Abstützlamelle, the braking force and braking torque at the fixed Gearbox supported.

A Arrangement of the means for applying the braking force on both sides of the Planet unit is not mandatory. At a delay the planetary unit rotating as a whole about the output shaft this initially minimal by the action of the braking force Axially moved around her lateral play until she with the means for applying the braking force opposite side firmly attached to the adjacent friction plate. Then you can the braking forces attack symmetrically on the planetary unit.

The moment transmitted to the planetary unit must be in the fixed Gearbox be supported. This can be done in advantageously achieved by who the that the friction plates rotatably arranged in the fixed gear housing are. The support of the braking torque is then over the friction discs. On other components of the braking device is no moment transferred. They can do that accordingly designed and designed to be simpler.

There the Abstützlamelle in contrast to the force introduction lamella does not have to be displaceable in the axial direction, provided they simultaneously rests on the gear housing, it can be provided that the Support lamella fixed to the stationary gearbox housing connected is. In particular, the Abstützlamelle can thereby be formed, that the friction lining directly on the surface the fixed gear housing is applied. for example he can be screwed or glued hereby. This will be the Construction further simplified and it will be components and costs saved up.

Around the introduction of the braking torque in the planetary unit continues to improve, can be provided that the active surfaces the planetary unit a friction lining on the type of friction lining of a friction plate exhibit. This allows a very efficient friction surface pairing achieve the responsiveness and controllability further improved.

Further can be provided that the planet carrier at least one side has a support ring, the manner of a Friction plate is formed, wherein the active surface on the the Planetenradpaaren opposite side of the carrier ring for cooperation with the friction plates of the brake device with equipped with a friction lining. Such a carrier ring thus forms as a unit both a holding and recording the Planetenradpaare or planetary gears suitable supporting structural element as well as one for the initiation of the braking torque suitable effective area. The friction lining can with the carrier ring glued or screwed. The planet carrier is advantageous constructed largely symmetrical and has the said carrier ring on both sides. On the carrier ring are the Planetenradpaarwellen or the planetary gear shafts fixedly connected to the carrier ring, in particular screwed, riveted or welded.

The Brake device can be advantageous in the fixed gear housing be arranged. This is essentially stationary to the motor vehicle arranged and for operating the brake device necessary power transmission means, for example hydraulic oil, Compressed air or electrical energy can, without sealing relative to each other moving components or without sliding contacts in the fixed gearbox be initiated.

Preferably comprise the means for applying the braking torque causing braking force a hydraulic unit with at least one on or in the fixed Transmission housing arranged pressure cylinder and on a Force introduction lamella acting plunger. Such an arrangement transmits the braking force on the plunger and the force introduction lamella on the planetary unit, wherein the braking torque from the force introduction lamella recorded and, if the force introduction lamella against rotation the fixed gear housing is arranged, from this too is supported.

The Pressure stamps do not come directly with the active surfaces the planetary unit in contact and can constructively simpler be designed because they have no moment to record. For uniform introduction of the braking force the planetary unit are preferably a plurality of plunger about a circumference or it is an annular stamp provided, which upon actuation of the brake device evenly applied to the force introduction lamella can.

Especially advantageous is an embodiment in which the plunger and the force introduction lamella form a component. The printing stamp can be solved with the force introduction lamella over detachable or unsolvable connection means connected, in particular screwed, riveted or welded. It can be provided that the force introduction lamella with the pressure punches of the same Component is formed as a carrier ring with the it arranged Planetenradpaarwellen, resulting in further simplification of the differential gear contributes.

If the planet gears are formed by pairs of planetary gears, each having two different effective diameters, these form an intermediate gear. For the standard transmission ratio of the intermediate gear, 0.85 <i ₀ <0.95 is preferably selected, more preferably 0.89 <i ₀ <0.91. The Standard translation is the translation that results when the planetary unit is blocked. It describes, by way of example with respect to a differential gear, the ratio of the drive basket speed, ie the drive shaft speed, to the output shaft speed. If the intermediate gear does not accelerate the respective output shaft assigned thereto, but decelerates, one of the standard translations corresponding standard ratio greater than 1 can be selected, so that then the respective other output shaft is accelerated via the speed compensation in the planetary or differential gear.

In the case of a pair of planetary gears, the ratio Z of the effective diameter of the first planetary gear to the effective diameter of the second planetary gear should be 0.90 to 0.98, preferably 0.93 to 0.95, more preferably 0.94. The ratio S of the effective diameter of the first sun gear to the effective diameter of the second sun gear should be 1.01 to 1.07, preferably 1.03 to 1.05, more preferably 1.04. The ratio R _{1 of} the effective diameter of the first sun gear to the effective diameter of the first planetary gear should be 1.4 to 1.6, preferably 1.48 to 1.52, more preferably 1.50. The ratio R _{2 of} the effective diameter of the second planetary gear to the effective diameter of the second sun gear should be 0.68 to 0.78, preferably 0.72 to 0.74, more preferably 0.735. These specifications allow the compact design with sufficient effective surfaces to initiate the braking torque, the desired standard ratio and good efficiency.

The Application of the invention is of course limited not on the illustrated bevel gear differential assembly. For others Differential gear designs such as spur gear differentials, in particular in planetary construction, or worm wheel differentials can the described System also be used. Further, an application is in a transfer case also conceivable when targeted intervention different in the driving dynamics of a vehicle front and rear axle accelerated or delayed. A differential gear may alternatively or in addition to other control systems such as electronic stability programs be used. Areas of application of the invention are in addition to Classically powered by internal combustion engines powered vehicles In addition, hybrid drives in which a braked planetary unit is used, or a vehicle both drive types exhibiting.

Further Features and advantages of the invention will become apparent from the dependent claims and from the following description of preferred embodiments based on the drawings.

In show the drawings

1a a schematic representation of a prior art differential gear according to the prior art,

1b a deployable in an automatic transmission, braked planetary unit for performing switching operations according to the prior art,

1c a further embodiment of a used in an automatic transmission, braked planetary unit for making switching operations according to the prior art,

2 a possible embodiment of a differential gear according to the invention,

3 a plan view of a force introduction blade or a planet carrier,

4 a side view of a planet carrier in section, and

5 an overview of a possible dimensioning of a differential gear according to the invention,

6a a first used in an automatic transmission, braked planetary unit according to the invention (corresponding 1b )

6b a second embodiment of a used in an automatic transmission, braked planetary unit according to the invention (corresponding 1c ), and

7 A third embodiment of a planetary unit according to the invention, in which the output shaft is formed as a ring gear.

1a respectively. 1b and 1c show a schematic representation of a prior art differential gear or a planetary gear of an automatic transmission and are used to explain the general operation of a transmission with a braked planetary unit 5 used. Drive power is transmitted to the drive cage via a drive shaft 1 or a drive shaft 1 introduced and there in the manner known for differentials on two output shafts 2 distributed. The structure of the differential gear is substantially symmetrical to both output sides. The output shafts 2 in 1a In addition, each have an intermediate gearbox 4 with the drive basket 1 coupled. The same applies to the output shafts 1 in the 1b and 1c , where here only a Zwischenge gear is provided. Differential, drive basket 1 or drive shafts 1 , Output shafts 2 and intermediate gear 4 are at least partially in a fixed gearbox 3 arranged and stored herein.

Every intermediate gear 4 has a planetary unit 5 on, the z. B. in the case of the differential gear of 1a in the case of zero-torque straight ahead as a whole with the drive basket 1 and output shaft 2 rotates. The planetary units 5 include multiple Planetenradpaare 6 which are expediently arranged at regular intervals along the circumference. In 1a and 1c are each intermediate gear 4 and planetary unit 5 two planetary gear pairs 6 recognizable. 1b In contrast, shows a likewise conventional design in which not only Planetenradpaaren individual planet gears apply. The planet gears or Planetenradpaare are each on a Planetenradpaarwelle 8th arranged with a planet carrier 7 connected is. Each pair of planetary gears 6 has a first planetary gear 9 and a second planetary gear 10 on. The first planetary gear 9 meshes with one with the drive basket 1 rotatably connected first sun gear 11 , the second planetary gear 10 meshes with one with the respective output shaft 2 rotatably connected second sun gear 12 ,

1a shows further per output side a braking device 13 applying a braking force to the planetary unit 5 can transfer. The brake device 13 acts between the stationary gearbox 3 and the planetary unit 5 ,

Will now be in 1a on a driven side the planetary unit 5 braked or blocked, the planetary unit 5 no longer circulating freely or standing opposite the stationary gearbox housing 3 , The over the drive basket 1 from the drive power directly driven first sun gear 11 drives over the first planetary gear 9 and on the rotatably connected second planetary gear 10 the output shaft 2 , A power transmission from the drive basket 1 on the output shaft 2 over the intermediate gear 4 is guaranteed. The differential speed forced between the two output shafts is balanced in the differential. With blocking the planetary unit 5 is the ratio of the drive basket speed to the speeds of the output shafts 2 and the ratio of the speeds of the output shafts 2 fixed to each other, regardless of turning or straight ahead. A simultaneous blocking of both intermediate gears 4 on both output sides is not possible.

1b and 1c show against the 1a no differential, but a planetary gear set as part of an automatic transmission. In 1b the planetary gearset transmits the power via the intermediate gearbox 4 without translation error from the output shaft 1 on the output shaft 2 , but he ensures a reversal of the direction of rotation due to the Ravigneaux set used. In 1c however, is similar to the application in 1a a translation error exists, so that drive shaft 1 and output shaft 2 Although the same direction of rotation, but have different rotational speeds.

In 1a . 1b and 1c are the brake devices 13 recognizable only on one side of the planetary unit 5 and arranged relatively far from the output shaft axes, which leads to the disadvantages mentioned above.

In 2 an embodiment of a differential gear is shown. It is shown only one output side of the differential gear. The drive shaft (not shown) drives the drive cage 1 via bevel gear teeth. The drive basket 1 is rotatable to the fixed gear housing 3 stored. At the end is the first sun wheel 11 arranged with the first planetary gear 9 engaged. The first planetary gear 9 is non-rotatable with the second planetary gear 10 to the planetary gear pair 6 connected and arranged coaxially with this. The second sun wheel 12 stands with the second planetary gear 10 engaged, which in turn with the output shaft 2 rotatably connected.

6a and 6b clarify how the for a differential according to 2 already described invention concept of a planetary unit 5 an automatic transmission was transmitted. The too 2 already described aspects can be easily in the 6a and 6b find again. It shows the 6a an embodiment of the invention in 1b illustrated transmission and 6b an embodiment of the invention in 1c illustrated transmission.

In 6a and 6b drives the drive shaft 1 over the first sun wheel 11 the first planetary gear 9 At the second planetary gear 10 rotatably connected. The second planetary gear 10 in turn drives the second sun gear 12 on, in 6a a Ravigneaux set is used and the first and the second sun gear have identical effective diameters so that it starts from the drive shaft 1 to the output shaft 2 to a reversal of direction comes. In the transmission according to 6b is, however, as well as in 2 , a Planetenradpaar provided with a translation error. Of course, both principles can also connect to each other, so that both a reversal of rotation and a rotation speed change caused by the translation error can be realized.

Below are the 2 . 6a and 6b described. The pair of planetary gears shown 6 is on the planetary gear pair shaft 8th rotatably mounted and can rotate around this. The planetary gear pair shaft 8th is on both sides, each with a carrier ring 16 connected. The planet carrier 7 includes the carrier rings 16 and planetary gear pair shafts 8th , the planetary unit 5 In addition, also includes the Planetenradpaare 6 ,

On the side of the left carrier ring 16 is a friction plate 15 arranged as the force introduction lamella 15 ' is trained. The brake device 13 , in the 2 . 6a and 6b exemplified as a hydraulic brake device brings about a plunger 17 a braking force on the force introduction lamella 15 ' on. This is designed annular and rotationally fixed via a toothing located on the outer edge but in the direction of the axes of rotation of the wear shaft 2 , the drive basket 1 or the drive shaft 1 and the intermediate gear 4 slidable in the fixed gearbox 3 stored. The brake device 13 is suitably designed so that a uniform pressure on the force application lambs 15 ' can raise.

On the side of the right carrier ring 16 is also a friction plate 15 provided as a support lamella 15 '' is trained. Also the support lamella 15 '' is rotationally fixed and in the same direction as the force introduction lamella 15 ' slidable in the fixed gearbox 3 arranged. The mobility of the Abstützlamelle 15 ' However, it is not significant for the function of the differential gear. The support lamella 15 '' Can also be directly on the stationary gearbox 3 be applied or attached to this, so that on a Abstützlamelle 15 '' can be dispensed with as a separate component. In 6a respectively. 6b becomes the support lamella 15 '' via a form-fitting in the transmission housing 3 engaging support ring held axially. This absorbs the axial forces occurring during braking.

At the carrier rings 16 effective areas are provided. These are the areas over the braking force and braking torque in the planetary unit 5 be introduced. They are preferably located on both sides of the Planetenradpaare 6 at the friction plates 15 facing side surfaces of the carrier rings 16 , The side surfaces of the carrier rings 16 can serve themselves in whole or only partially as effective area. As active surfaces are preferably friction surfaces, the nature of the friction surfaces of the friction plates 15 correspond to the side surfaces of the carrier rings 16 placed.

With The embodiment described above becomes a compact, easy-to-adjust, lightweight and cost-effective differential or created automatic transmission. Also due to the simple Construction, it has a long life and is characterized by a small space requirement and low constructive complexity out.

The two sides of the planetary unit 5 arranged friction plates 15 with little play to the sides in the fixed gearbox 3 are accommodated, ensure by forming an abutment stable storage of the planetary unit 5 , The in the intermediate gear 4 occurring forces and moments, especially when delaying or blocking the planetary unit, ie when using the intermediate gear 4 , by the braking device 13 occur through the two sides of the planetary unit 5 arranged components effectively collected and in the fixed gearbox 3 initiated. The planetary unit 5 comes, therefore, as in 2 shown without an additional axial bearing. Due to the compact design and the resulting low masses results in a fast and efficient controllability of engagement by the braking device.

3a shows an embodiment of a friction plate 15 in a top view. Front side regularly distributed over the circumference friction surfaces are visible, which face the active surfaces of the planetary unit. At the outer edge is a toothing, the non-rotatable and simultaneously axially displaceable mounting in the fixed gear housing 3 allows. In a particular embodiment of the differential gear or the automatic transmission is provided that the in 3a shown friction plate 15 component same or at least the type as a carrier ring 16 Use finds. It can affect the friction plates 15 to act dry or wet fins. Preference is given to wet blades are used in the manner of a hydraulic clutch blade.

3b shows a possible embodiment of a planet carrier 7 with two carrier rings 16 , which is essentially the embodiment of in 3a shown friction plate 15 correspond. Between the carrier rings 16 and fixedly connected to them is the planetary gear pair shaft 8th shown on the how in 2 recognizable, the Planetenradpaare 6 are rotatably mounted. The planetary gear waves 8th In addition, keep the carrier rings 16 upon exposure of the braking force to distance to ensure the free rotation of the Planetenradpaare. To evenly load the carrier rings 16 To ensure further support elements between the support rings can be provided, the deformation and thus an uneven loading of the active surfaces of the support rings 16 prevent the action of the braking force. On the side surfaces of the carrier rings 16 is similar to a friction plate on a friction lining brought.

4 shows an overview of an exemplary suitable dimensioning of a differential gear, wherein the planetary unit 5 with planetary gear pairs 6 is designed and as part of an intermediate gear 4 acts, the Planetenradpaare 6 have different effective diameter, so a deliberate translation error. As vehicle data, the dynamic tire radius R _dyn = 0.315 m and the axle ratio i _axle = 3.5 are given arbitrarily but realistically. The radius of the first sun gear is r ₁ = 30 mm, that of the first planetary gear r ₂ = 20 mm, that of the second planetary gear r ₃ = 21.2 mm and finally that of the second sun gear r ₄ = 28.85 mm. The web radius, ie the radius on which the planetary gear pairs 6 rotate about the output shaft axis or the radius with which the Planetenradpaarwellen 8th are spaced from the output shaft axis, r _web = 50 mm.

This results in a ratio Z of the effective diameter of the first planetary gear to the effective diameter of the second planetary gear of 0.94 and a ratio S of the effective diameter of the first sun gear to the effective diameter of the second sun gear of 1.04. The ratio R _{1 of} the effective diameter of the first sun gear to the effective diameter of the first planetary gear is 1.50, while the ratio R _{2 of} the effective diameter of the second planet gear to the effective diameter of the second sun gear is 0.735. The standard ratio of the intermediate gear follows from this information with i ₀ = 0.907.

• – n_Propshaft (Antriebswellendrehzahl oder Motordrehzahl)
• – n_Diff (Antriebskorbdrehzahl)
• – Δn (relative Differenzdrehzahl zwischen Abtriebswelle und Antriebskorb)
• – n_RL (Abtriebswellendrehzahl)
• – n_Steg (Rotationsdrehzahl der Planeteneinheit)
• – n_23/Steg (Drehzahl der Planetenradpaare um die Planetenradpaarwelle)

If these values are taken as a basis, the following can be taken from the table in FIG. 1 for the assumed output side for respectively assumed vehicle speeds 4 calculate removable sizes:

• - n _Propshaft (drive shaft speed or engine speed)
• - n _Diff (drive _{basket speed} )
• - Δn (relative differential speed between output shaft and drive cage)
• - n _RL (output shaft speed)
• - n _bridge (rotational speed of the planetary unit)
• N _{23 / bridge} (rotational speed of the planetary gear pairs about the planetary gear pair shaft)

In addition to the above data, the table in 4 a rough calculation of the caused by the differential _gear or the braking device for the respective vehicle _speeds V loss line P _verl. , The calculation is in each case an assumed output torque of an output shaft of .DELTA.T ₄ = 1200 nm and a resulting due to the standard translation of the intermediate gear of i ₀ = 0.907 following drive torque of the drive cage T ₁ = 1320nm based. The clutch torque T _K , that is, the braking torque acting on the planetary unit, corresponding to the standard ratio of the intermediate gear of i ₀ = 0.907 is about 10% of ΔT ₄ = 1200 Nm, ie T _K = 120 Nm.

In 7 is shown a further embodiment of the invention, wherein the drive shaft 1 also drives a planetary unit, which has a braking device 13 can be braked. Unlike in the 2 . 6a and 6b described gear is in the embodiment according to 7 the output shaft 2 as a ring gear 18 formed with an internal toothing. This ring gear 18 can, for example in conjunction with a further to be provided external toothing (not shown) for direct output of the drive power or the direct drive of another drive body can be used. The intermediate gear 4 is doing of first planetary gears 9 formed by the drive shaft 1 transmitted drive power in the ring gear 18 initiate.

In 7 combs the first sun gear 11 over the planet 9 with the ring gear 18 , contrary to 2 . 6a and 6b no Planetenradpaar is provided. Also is in 7 not like in 6a a Ravigneaux set provided. Of course, the embodiments described in the various figures and the associated technical aspects can also be applied to the embodiment according to FIG 7 transferred and vice versa. The person skilled in the art will know how to adapt the gearbox on the basis of the respective requirements of a specific application.

1

Drive basket / drive shaft

2

output shaft

3

fixed gearbox

4

intermediate gear

5

planetary unit

6

planet wheel

7

planet

8th

Planetenradpaarwelle

9

first planet

10

second planet

11

first sun

12

second sun

13

braking device

14

active surfaces

15

friction plate

15 '

Force application plate

15 ''

Abstützlamelle

16

support ring

17

plunger

18

ring gear

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - EP 2006/008486 [0004]
• US 6120407 [0009]

Claims (13)

Automatic transmission of a motor vehicle, except differential, with a transmission housing ( 3 ) And arranged in the transmission housing gear train for transmitting or distributing a force, wherein the drive train comprises a planetary unit with a planet carrier and planetary gears arranged thereon, characterized in that a braking device is provided which has means for applying a braking torque causing braking force, and Braking moment the planetary unit ( 5 ) is able to decelerate relative to the transmission housing, wherein the planetary unit active surfaces ( 14 ), which is used to initiate the braking torque in the planetary unit ( 5 ) are provided and the active surfaces ( 14 ) on both sides of the planetary gears ( 6 ) and at least partially laterally next to the planetary gears ( 6 ) are arranged. Transmission according to claim 1, characterized in that the braking device ( 14 ) for introducing the braking torque into the planetary unit ( 5 ) on both sides of the planetary unit ( 5 ) Reiblammellen ( 15 ) having. Transmission according to Claim 2, characterized in that at least the friction plate facing the means for applying the braking force ( 15 ) as a force introduction lamella ( 15 ' ) is displaceable in the direction of the output shaft axis and the braking force on the active surfaces facing it ( 14 ) transmits the planetary unit. Transmission according to one of the two preceding claims, characterized in that the means for applying the braking force only on one side of the planetary unit ( 5 ) arranged on the other side of the planetary unit ( 5 ) arranged friction plate ( 15 ) as Abstützlamelle ( 15 '' ) is formed, the braking force and braking torque on the fixed gear housing ( 3 ) is supported. Transmission according to one of claims 2 to 4, characterized in that the friction plates ( 15 ) rotationally fixed in the fixed gear housing ( 3 ) are arranged. Transmission according to one of the two preceding claims, characterized in that the Abstützlamelle ( 15 '' ) fixed to the stationary gear housing ( 3 ) connected is. Transmission according to one of the preceding claims, characterized in that the active surfaces ( 14 ) of the planetary unit ( 5 ) a friction lining according to the type of friction lining of a friction plate ( 15 ) exhibit. Transmission according to one of the preceding claims, characterized in that the planet carrier ( 7 ) at least one side a support ring ( 16 ), which is designed in the manner of a friction plate, wherein the active surface ( 14 ) on the side facing away from the planetary gears of the carrier ring ( 16 ) for the interaction of the braking device ( 13 ) is equipped with a friction lining. Transmission according to one of the preceding claims, characterized in that the braking device ( 13 ) in the fixed gear housing ( 3 ) is arranged. Transmission according to one of claims 3 to 9, characterized in that the means for applying the braking torque causing braking force a hydraulic unit with at least one on or in the stationary transmission housing ( 3 ) arranged pressure cylinder and on a force introduction lamella ( 15 ' ) acting plunger ( 17 ). Transmission, except as a differential, according to claim 10, characterized in that the plunger ( 17 ) and the force introduction lamella form a component. Transmission according to one of the preceding claims, characterized in that the planet gears in as Planetenradpaare are formed. Transmission according to one of the preceding claims, characterized in that the output shaft 2 is formed in the form of a ring gear.