DE102004017163B4 - Motor vehicle transmission for transverse installation - Google Patents

Abstract

Motor vehicle transmission (10) for transverse installation, with a transmission input shaft (16) which is connectable to a drive motor (12) of the motor vehicle, a plurality of wheelsets (20-30), each having a fixed gear and a loose wheel and by means of respective clutches ( 32-36), a transmission output shaft (18) and a differential (42), wherein the transmission output shaft (18) via an output assembly (40) with an input member (44) of the differential (42) is connected and wherein the an output member (52) of the differential (42) is connectable to a left axle side shaft (56) and the other output member (46) is connectable to a right axle side shaft (50, 56) of the motor vehicle, the output arrangement (40) comprising at least one hollow shaft (66) disposed about one (56) of the axle side shafts (50, 56) and connected to the transmission output shaft (18) via two constant gear sets (60, 62), a clutch assembly (64) a To use one or the other constant gear set (60, 62) for power transmission from the transmission output shaft (18) to the hollow shaft (66), and ...

Description

The The present invention relates to a transverse transmission automotive transmission, with a transmission input shaft connected to a drive motor of the Motor vehicle is connectable, a plurality of wheelsets, the each have a fixed gear and a loose wheel and by means of respective Clutches are switched on and interpreted, a transmission output shaft and a differential, wherein the transmission output shaft via a Output assembly connected to an input member of the differential is and wherein the one output member of the differential with a left axle shaft and the other output member with a right Achsseitenwelle the motor vehicle are connectable.

Such a motor vehicle transmission for the front transverse installation is from the DE 44 44 120 C1 known.

The Output arrangement has in general such front-transverse transmissions a so-called "Final Drive "-Radsatz on. This constant gear set includes on the one hand with the Transmission output shaft firmly connected gear. This gear is available then immediately engaged with another wheel attached to the Input member of the differential is set, in a bevel gear differential usually on the differential carrier.

Consequently the translation takes place from the output shaft of the engine (usually an internal combustion engine) to the axle sideways over two Stages, namely a first step over the gear wheelsets of the transmission, and a second stage via the "Final Drive" wheel set.

For the first Gear and reverse gear are there usually only complete translations of a maximum of 1:18 possible.

Become for example, higher translations needed z. Eg 1:45 and higher, have to separate gear sets are provided in the motor vehicle transmission.

So For example, it is known (Honda ACT4 - 5 + 2 Speed transmission), in parallel to the transmission input shaft, a short auxiliary shaft rotatable on the transmission housing to store.

Around a higher translation in the forward and in reverse Achieve is in axial extension the gear wheelsets a low-range arrangement of two wheelsets provided.

These separate spur gears to lead to a significant extension the axial length. Furthermore, the transmission has a higher overall weight. Also is the Wheelset relatively complex, especially due to the separate to be provided secondary shaft. Finally, the high torque already at the beginning of the transmission chain generated and must then be passed through the transmission. This makes you stronger Shafts and bearings necessary. The output arrangement needs for the increased torque be interpreted. If necessary, even the center distances must be increased. The differential is then exposed to considerable axial forces and tilting moments, so that also the differential case and the storage of the differential must be strengthened.

From the document US-A-5,728,022 An automatic transmission for transverse installation in a motor vehicle is known. It is described there that the stepped transmission of the automatic transmission via a so-called "final drive" with a differential assembly for the front axle is connectable. It is possible to arrange a planetary gear set adjacent to the differential whose input is connected to the final drive and whose output is connected to the input member of the differential. In a second embodiment, the document has adjacent to the differential two planetary gear sets whose input members are connected to the final drive.

From the DE 41 19 387 C2 a drive device for a motor vehicle is known, wherein in a multi-step transmission, a drive wheel is fixedly arranged on a cylindrical end member which is fixed on the drive shaft of the stepped transmission. A universal joint is disposed within the cylindrical end member. The universal joint is connected to a drive half-shaft and to an output member of a transverse differential.

The document DE 42 09 731 A1 shows a drive train for transverse installation in a motor vehicle. The drive train has a spur gear, the output shaft is connected via a Final Drive wheelset with the input member of a front axle differential.

From the document FR-A-2 681 015 is another drive train for the transverse installation known, wherein an output member of a Vorderachsdifferentials is designed as a hollow shaft portion within which a Achsseitenwellengelenk is indicated.

It is therefore the object of the present invention, an improved Motor vehicle transmission for to provide the transverse installation, the at least one of the above disadvantages avoids.

This object is achieved by a motor vehicle transmission with the features of claim 1. Advantageous embodiments are in the dependent Claims specified.

The Output assembly has a hollow shaft, which is about one of the axle side shafts arranged around and with the transmission output shaft via a Constant wheelset is connected, and the output assembly has a planetary gear set on, being a first member of the planetary gear set is connected to the hollow shaft and wherein a second member of the Planetary gear set connected to the input member of the differential is.

By This measure can the overall translation extending from the two stages (i.e., input shaft to output shaft and Output shaft to hollow shaft) and in addition from the obtainable by means of the planetary gear set translation put together.

It It is understood that the planetary gear set is preferably coaxial with the hollow shaft is arranged.

Provided the planetary gear set in close proximity to the differential is arranged, a simple storage is possible. In particular, that can Differential axialkraft-, radialkraft- and / or tilting moments free be formed.

Also The high torque is only at the end of the transmission chain in the planetary gear set generated adjacent to the differential.

Further results in the transmission itself a simple conventional Wheelset construction so that existing basic gear types are used can.

The axial length extended generally not at all or only a little.

The Hollow shaft is rotatable on its outer circumference stored.

This allows make the hollow shaft comparatively long and thus allows a functional extensibility.

Further is the one axle shaft inside the hollow shaft with a Output member of the differential over a Achsseitenwellengelen is connected.

at this embodiment the hollow shaft is designed so that the Achsseitenwellengelenk is arranged in the interior of the hollow shaft.

hereby let yourself Achieve an axially particularly compact design, even if the hollow shaft builds axially comparatively long.

Also The output arrangement has two constant gear sets and a clutch assembly on to one or the other constant gear set for power transmission from the transmission output shaft to the hollow shaft to use.

at this embodiment the motor vehicle transmission forms a multi-group transmission, wherein all Speed gear sets either over the one constant wheel or the other constant wheelset operable are.

The two constant wheel sets can be trained as high and low regime.

By the arrangement of the axle side shaft joint in the interior of the accordingly a little longer Hollow shaft it is possible despite two constants and an additional clutch assembly to achieve an axially compact arrangement.

From particular preference is when the first member of the sun gear Planetary wheel set is.

hereby let yourself connect the hollow shaft particularly well to the planetary gear set.

Further it is advantageous if the second member of the planet carrier of Planetary wheel set is.

By This measure let yourself achieve an axially compact design.

Further it is advantageous if the third member of the planetary gear set fixed to the housing is.

On that way a translation increase comparatively just set up.

This especially if the third member is the ring gear of the planetary gear set is.

If the sun gear is the input member of the planetary gear set, the planet carrier the output member of the planetary gear set is, and if the ring gear of the planetary gear set is fixed to the housing, let yourself achieve a particularly high ratio with the planetary gear set.

It is particularly preferred when the constant-wheel sets respectively have a loose wheel, which is rotatably mounted on the transmission output shaft is, and if the clutch assembly between the two loose wheels on the transmission output shaft is arranged.

This allows the Schaltkupplungsanord tion for the two constant-wheel sets are formed in a conventional manner, in a similar manner as a clutch assembly for the gear sets.

From It is also particularly advantageous if the differential is a bevel gear differential is. Here is a compact axial arrangement planetary gear and differential possible.

alternative the differential is a planetary differential.

in this connection is advantageous that two structurally similar Radsatzanordnungen can be arranged axially side by side.

It it is understood that the above and the following yet to be explained features not only in the specified combination, but also in other combinations or alone, without to leave the scope of the present invention.

embodiments The invention are illustrated in the drawings and in the following description explained. Show it:

1 a transmission diagram of a motor vehicle transmission according to a first embodiment of the present invention; and

2 a transmission diagram of a motor vehicle transmission according to an embodiment which does not belong to the present invention.

In 1 is a first embodiment of the motor vehicle transmission according to the invention generally with 10 designated.

The motor vehicle transmission 10 is designed for front transverse installation in motor vehicles. The motor vehicle transmission 10 has a transmission input shaft 16 on, which has a starting and separating clutch 14 with the output of an engine 12 of the motor vehicle is connectable, usually an internal combustion engine.

Furthermore, the motor vehicle transmission 10 a transmission output shaft 18 on, which is parallel to the transmission input shaft 16 is arranged, as well as a plurality of wheelsets 20 - 30 ,

The wheelsets 20 - 30 each have a fixed gear and a loose wheel and are each designed as a gear wheelsets. The axial order of the wheelsets, seen from the starting and separating clutch 14 out, is the following: wheelset 20 for first gear, wheelset 30 for reverse gear, wheelset 22 for second gear, wheelset 24 for the third gear, wheelset 26 for the fourth gear, wheelset 28 for the fifth gear.

The loose wheels of the wheelsets 20 . 22 . 24 . 26 . 30 are at the transmission output shaft 18 arranged. The loose wheel of the wheelset 28 for the fifth gear is at the transmission input shaft 16 arranged.

For engaging and disengaging the first and the second and the reverse gear R is between the loose wheels of the wheelsets 20 . 22 a first clutch pack 32 coaxial with the transmission output shaft 18 arranged.

A corresponding second clutch pack 34 for the third and fourth gear is coaxial with the transmission output shaft 18 between the wheelsets 24 and 26 arranged.

Axially outside is also a clutch 36 arranged for the fifth gear, and coaxial with the transmission input shaft 16 ,

The structure of the motor vehicle transmission described so far 10 corresponds to the state of the art. The arrangement and distribution of the wheelsets within the motor vehicle transmission 10 is therefore only to be understood as an example. Furthermore, the motor vehicle transmission 10 be designed in the same way as a six or seven-speed gearbox.

The motor vehicle transmission 10 is over a total of 40 designated output arrangement with a differential 42 connected. The differential 42 is a Vorderachsdifferential and has an input member 44 on. Furthermore, the differential points 42 a first output member 46 on, that via an axle side-shaft joint 48 with a first axle shaft 50 for one of the front wheels of the motor vehicle (eg right front wheel) is connected. The differential 42 has a second output member 52 on top of that, via a second axle side shaft joint 54 with a second axle side shaft 56 is connected (for example, the left front wheel of the motor vehicle).

The input member 44 of the differential 42 is by means of the output arrangement 40 driven. The differential 42 distributes the drive power in a conventional manner to the two axle side shafts 50 . 56 ,

While in conventional automotive transmissions for front transverse installation the output assembly 40 usually only a fixed gear on the transmission output shaft 18 that has a coaxial with the differential 42 arranged and on the input member 44 set further gear is engaged, the output arrangement 40 of the present embodiment as follows builds.

The output arrangement 40 has a first constant gear set 60 for a high-regime (ie usually for the normal operation of the motor vehicle) and a second constant-wheel set 62 for the low regime (eg for a creep operation).

The constant wheel sets 60 . 62 each have an unspecified idler gear on. The loose wheels of the constant wheel sets 60 . 62 are coaxial with the transmission output shaft 18 arranged. Between the loose wheels of the constant wheel sets 60 . 62 is a third clutch pack 64 coaxial to the transmission output shaft 18 arranged. The third clutch pack 64 serves to over the motor vehicle transmission 10 transmitted power either via the first constant gear set 60 or the second constant gear set 62 to transmit downforce.

The output arrangement 40 also has a hollow shaft 66 on. The hollow shaft 66 is coaxial with the differential 42 arranged and has a first hollow shaft section 68 with a comparatively large diameter and an adjoining second hollow shaft section 70 with a comparatively small diameter.

The first hollow shaft section 68 carries the fixed wheels of the first and second constant gear wheels 60 . 62 ,

The second hollow shaft section 70 is between the first hollow shaft section 68 and the differential 42 arranged and is with the sun gear of a planetary gear set 72 connected. The planet wheel set 72 is axially in the immediate vicinity of the differential 42 arranged. The planet carrier of the planetary gear set 72 is with the input member 44 of the differential 42 connected. The ring gear of the planetary gear set 72 is on a housing 74 of the motor vehicle transmission 10 fixed, so is fixed to the housing.

The drive power is thus either on the first or the second constant gear 60 . 62 on the hollow shaft 66 and from there to the sun gear of the planetary gear set 72 transfer. Because the ring gear of the planetary gear set 72 is fixed to the housing, can be realized in a simple manner, a comparatively large jump in the ratio.

Overall, thus can be from the transmission input shaft 16 to the input member 44 of the differential 42 set up a translation in the range of 1:30 to 1:70.

Due to the fact that a comparatively high jump in the ratio only in the planetary gear set 72 is done over the wheelsets 20 - 30 and the constant wheel sets 60 . 62 only comparatively low torques passed. Consequently, despite the high overall ratio, it is not necessary to provide stronger shafts and bearings.

The differential 42 is due to the immediate vicinity of the planetary gear set 72 axial force, radial force and tilting moments free. This results in a simple storage, and it is a simple, inexpensive differential carrier feasible.

Furthermore, despite the high overall ratio to a standard wheelset of the motor vehicle transmission with the wheelsets 20 - 30 be resorted to.

All gears 1-5, R of the motor vehicle transmission 10 Both H and L can be operated in both the high and low regimes.

The hollow shaft 66 is on the outer periphery of its first hollow shaft section 68 by means of a first bearing 76 and a second camp 78 rotatable on the housing 74 stored.

Due to the comparatively large diameter of the first hollow shaft section 68 (For example, in the range of more than 50 mm, in particular in the range of 60 to 90 mm, in particular in the range of 60 to 80 mm), it is possible, the second Achsseitenwellengelenk 54 inside the first hollow shaft section 68 to arrange.

As a result, a compact axial structure can be achieved despite the two constant-wheel sets 60 . 62 and the interposed third clutch pack 64 realize.

The axle side shaft joint 54 is shown only schematically. For example, the second output member 52 for connection to the second axle side shaft 56 also be designed as follows. In this case, the second output member 52 a short stub shaft in the first hollow shaft section 66 empties. Within the first hollow shaft section 66 is the second output element 52 then itself provided with a hollow shaft portion which is part of the second Achsseitenwellengelenkes 54 can form.

The differential 42 has a differential carrier 80 on that with the input member 44 rotatably connected. The differential carrier 80 has a first basket shaft section 82 and a second basket shaft portion 86 on, which extend coaxially with the front axle. The basket shaft sections 82 . 86 are designed as a hollow shaft stub, which is the first output member 46 or the second output member 52 surround.

The second hollow shaft section 70 is about the second basket shaft section 86 arranged around. The first basket shaft section 82 is on the case 74 by means of a third warehouse 84 stored.

The differential 42 may also be within the hollow shaft in a modified embodiment 66 or between the constant wheel sets 60 . 62 be arranged.

Furthermore, the bevel gear differential 42 replaced by a spur gear differential and parallel to the planetary gear set 72 to be ordered.

Overall, it is with the motor vehicle transmission 10 in a particularly favorable way possible, gears of wheelsets 20 - 30 load under load or partial load. In such switching operations, the clutches of the motor vehicle transmission 10 automatically actuated, wherein a gear change generally takes place so that before laying out a gear initially the gear input side via the separating clutch 14 Pending torque is taken over by a friction clutch of a clutch of the target gear. This can be due to the high ratios in the output arrangement 40 generate high supporting moments, especially when the friction clutch on the transmission output shaft 18 is arranged. But it is also possible, the clutches for such gear change modes on the transmission input shaft 16 to arrange, especially those of the second gear. As a result, particularly high support moments in circuits from gear 1 to gear 2 are possible.

In 2 is another embodiment of a motor vehicle transmission generally with 10 ' designated.

The general structure of the motor vehicle transmission 10 ' and its general operation correspond to those of the motor vehicle transmission 10 of the 1 , to the description of which reference is made in full. In the following, only the differences are explained.

The output arrangement 40 ' of the motor vehicle transmission 10 ' has only a single constant wheel set 60 ' on. The hollow shaft 66 ' is designed as a comparatively short hollow shaft, on which only a fixed gear of the constant gear set 60 ' and the sun gear of the planetary gear set 72 ' are fixed.

The hollow shaft 66 ' can be formed with a comparatively small diameter. Furthermore, the hollow shaft 66 ' directly on the associated basket shaft section 86 ' of the differential 42 ' be rotatably mounted.

One opposite the hollow shaft 66 ' axially projecting portion of the second basket shaft portion 86 ' is by means of a warehouse 90 on the housing 74 ' stored.

The first basket shaft section 82 is, just like the motor vehicle transmission 10 of the 1 , about a camp 84 on the housing 84 stored.

In the motor vehicle transmission 10 ' There is no possibility to switch between a high and a low regime.

Overall, however, can be about the output arrangement 40 ' with the constant wheel set 60 ' and the planetary gear set 72 ' produce a comparatively high overall ratio in the output. Consequently, here also the above for motor vehicle transmission arise 10 explained advantages.

Furthermore, in the motor vehicle transmission 10 ' the same modified embodiments concerning the arrangement of the differential 42 ' or the type of differential 42 ' (Spur gear differential) possible.

For both motor vehicle transmissions 10 . 10 ' applies that for the realization of a motor vehicle with four-wheel drive, it is possible, for example, to the input member 44 of the differential 42 . 42 ' to connect an output for the rear axle, for example via a transfer case.

Furthermore, it is generally possible, the motor vehicle transmission 10 . 10 ' to be installed in the area of the rear axle, namely on vehicles with rear axle drive.

Claims (8)

Motor vehicle transmission ( 10 ) for transverse installation, with a transmission input shaft ( 16 ), which are powered by a drive motor ( 12 ) of the motor vehicle is connectable, a plurality of wheelsets ( 20 - 30 ), each having a fixed gear and a loose wheel and by means of respective clutches ( 32 - 36 ) are in and out, a transmission output shaft ( 18 ) and a differential ( 42 ), wherein the transmission output shaft ( 18 ) via an output arrangement ( 40 ) with an input member ( 44 ) of the differential ( 42 ) and wherein the one output member ( 52 ) of the differential ( 42 ) with a left axle shaft ( 56 ) and the other output member ( 46 ) with a right axle shaft ( 50 . 56 ) of the motor vehicle are connectable, wherein the output arrangement ( 40 ) at least one hollow shaft ( 66 ), which is surrounded by a 56 ) of the axial side shafts ( 50 . 56 ) around and with the transmission output shaft ( 18 ) via two constant gear sets ( 60 . 62 ), a clutch assembly ( 64 ) to one or the other constant gear set ( 60 . 62 ) for power transmission from the transmission output shaft ( 18 ) to the hollow shaft ( 66 ) and a planetary gear set ( 72 ), wherein a first member of the planetary gear set ( 72 ) with the hollow shaft ( 66 ) and wherein a second member of the planetary gear set ( 72 ) with the input member ( 44 ) of the differential ( 42 ), wherein the hollow shaft ( 66 ) is rotatably mounted on its outer circumference, and wherein the one axle side shaft ( 56 ) inside the hollow shaft ( 66 ) with an output member ( 52 ) of the differential ( 42 ) via an axle side shaft joint ( 54 ) connected is. Transmission according to claim 1, wherein the first member is the sun gear ( 72 ) of the planetary gear set is. Transmission according to claim 1 or 2, wherein the second member of the planet carrier of the planetary gear set ( 72 ). Transmission according to one of claims 1 to 3, wherein a third member of the planetary gear set ( 72 ) is fixed to the housing. Transmission according to claim 4, wherein the third member is the ring gear of the planetary gear set ( 72 ). Transmission according to one of claims 1 to 5, wherein the constant-wheel sets ( 60 . 62 ) each have a loose wheel on the transmission output shaft ( 18 ) is rotatably mounted, and wherein the clutch assembly ( 64 ) between the two idler gears on the transmission output shaft ( 18 ) is arranged. Transmission according to one of claims 1 to 6, wherein the differential ( 42 ) a bevel gear differential ( 42 ). Transmission according to one of claims 1 to 6, wherein the differential is a planetary differential.