Patent Grant
7461568
This application is a national stage completion of PCT/EP2004/014204 filed Dec. 14, 2004 which claims priority from German Application Ser. No. 10 2004 002 283.6 filed Jan. 16, 2004.
The invention concerns a drive device with a transmission.
Drive devices with a transmission and, for example, a main engine designed as an internal combustion engine, are generally known in vehicle construction. With such drive devices, the main engine is actively connected with a drive shaft which, on its part, starts the input side of a shifting clutch assigned to the transmission. The output of this shifting clutch is then connected drive-technically with the input shaft of the transmission, whose output acts upon the vehicle wheels being propelled via a differential gear.
As a rule, such transmissions are designed as multi-step transmissions with whose operation it comes to a tractive force interruption with the gear change, which incidentally also is true for the so-called automated multi-step transmissions. From this generally ensues the demand to keep the phases of the tractive force interruption as short as possible in terms of increased driving comfort.
With the gearshift of a synchronized transmission this time has already been shortened through an increase in the operating force as well as an increase of the performance capability of the synchronizer meshes. With unsynchronized transmissions in this regard a corresponding design of a so-called clutch brake has become known.
Since the shifting clutch is opened with synchronized transmissions with shifting operations between the main engine and transmission generally, and with unsynchronized transmissions with an upward gearshift, with the achieved shortening of the tractive force interruption, thus the shortening of the time span for the mechanical gear change, the problem increasingly arises of reducing the currently existing revolution speed difference at the conclusion of the gear change via the shifting clutch without losses in comfort as well as at the same time wear resistant clashing with the clutch and main engine torque.
It would be offered as the path to a solution of this problem, to first begin with the closing procedure of the shifting clutch, when the two revolution speeds, adjacent to the shifting clutch, have converged as far as possible. These measures, however, run contrary to the already achieved shortening of the time for the mechanical gear change.
Against this background, the task, which underlies the invention, is to design a drive device with a transmission, such that the time span for the tractive force interruption with a gear change is further minimized and the breakdown in the tractive force is reduced.
The invention envisions that a shifting brake clutch is ordered in the performance transmission path of the main engine to the transmission between the driveline and the shifting clutch, and that the output of the shifting brake clutch can be brought into active connection with the gear output.
This has the advantage that through the interplay of the shifting clutch and the shifting brake clutch, the decrease in tractive force, typically due to the opening phase of the shifting clutch, is connected via the active connection of the shifting brake clutch with the gear output, i.e., the main engine torque supports itself in this phase in the transmission output. With a gear change, the two clutches operate in an intersecting manner whereby the main engine torque is advantageously reduced through the torque support to a transferable degree by the shifting brake clutch.
With a gearshift up to the next higher gear, a sinking of the main engine revolution speed is thus successfully achieved by that amount, which ensues from the revolution speed change of the gear change, under simultaneous support of the torque in the transmission output. With the drive device, according to the invention, both the complete collapse of the tractive force transmission occurring typically in the drive devices, according to the state of the art, is thus prevented and the time span is clearly lessened with reduced tractive force.
In a favorable manner, an otherwise usual transmission brake, as known for example from DE 196 52 916 A1, can be dispensed with.
Preferably it is provided that the support torque is received, via an auxiliary shaft propellable by the shifting brake clutch, which transfers this torque to the gear output in a torque path preferably parallel to the transmission.
In the advantageous design of this invention, the location of the torque discharge in this gear output can be designed switchably for the further increase of the torque in the gear output. For this purpose, idle gears can preferably be ordered to the auxiliary shaft, which are optionally and alternately connectable to the gear output by way of a coupling mechanism. In doing so, a secondary switching group is ordered to the transmission, for example, in the form of a planetary gear stage. The gear output shaft ordered directly to the transmission is thereby actively connected to the planetary gear stage, whose output in the form of a main output shaft, for example, drives the cardan shaft of a vehicle designed with this drive device via a differential gear.
In the concrete design of the invention, in particular, it can be provided that the output of the shifting brake clutch is rotationally fixed with an idle gear, which is rotationally fixed on the drive shaft. This idle gear preferably meshes with an intermediate wheel mounted on the gear housing which, moreover, is engaged with a fixed wheel on the auxiliary shaft.
Preferably, at least two idle gears are assigned to the output of the auxiliary shaft, which are mounted on these and are combinable optionally and alternately with a mechanical coupling mechanism with the gear output. This coupling mechanism is designed, for example, as a sliding collar.
Furthermore with this drive device, it is provided that the idle gear close to the transmission meshes with another idle gear, which is engaged with a gear wheel attached to the gear output shaft of the transmission. The idle gear distant from the transmission combs, in contrast, with an intermediate wheel, which is engaged with a gear wheel attached to the main output shaft of the drive device.
Another study of the invention provides that the gear output shaft of the transmission is actively connected with the input of a secondary switching group, whose output is formed by the main output shaft.
In this connection, it can be provided that the intermediate wheel, which meshes with the gear wheel attached to the main drive shaft, is a planetary wheel of a secondary switching stage designed as a planetary gear.
The invention will now be described, by way of example, with reference to the accompanying drawings in which:
In
These specified units are structurally unified inside a housing 8 with the exception of the internal combustion engine 1. Between the drive shaft 2 and the shifting clutch 3, serving also as a start-up clutch, a shifting brake clutch 9 is arranged, whereby the drive shaft 2 permanently drives a radial inner disk pact 10 of the shifting brake clutch 9. The drive shaft 2 is executed axially by the shifting brake clutch 9 and acts permanently on an input-sided clutch surface 11 of the shifting clutch 3.
A radial external disk pack 12 of the shifting brake clutch 9 is radially fixed in a clutch housing 13, which drives a co-axial gear wheel 14 ordered to the drive shaft 2. This gear wheel 14 is engaged with an intermediate wheel 15 supported in the housing 8, which meshes with a torque proof drive wheel 17 ordered to an auxiliary shaft 16. This auxiliary shaft 16 is radially fixed in the housing 8.
At the end of the auxiliary shaft 16 opposite the drive wheel 17, an output 18 is assigned to the gear output 5. For this purpose, two idle gears 19, 20 are mounted on the auxiliary shaft 16. A coupler mechanism 21 rotationally fixed in an axially moveable manner with the auxiliary shaft 16 can be brought optionally or alternately into engagement with one of the idle gears 19, 20.
A secondary switching group 22, designed as a planetary wheel stage, is arranged between the gear output shaft 6 and the main output shaft 7. The idle gear 19, arranged in this example to the left next to the coupling mechanism 21, engages an intermediate wheel 23 which, on its side, meshes with a slip free gear wheel 24 ordered to the gear output shaft 6, while the other idle gear 20 is engaged via an intermediate wheel 25 with a slip free gear wheel 26 ordered to the main output shaft 7. The intermediate wheel 25 is preferably a planetary wheel of the planetary wheel stage.
The operating mode of the drive device now follows:
In the running internal combustion engine 1, the opened shifting brake clutch 9, and the closed shifting clutch 3, the drive performance of the drive shaft 2 is transferred via the shifting clutch 3 to the transmission 4 and from there, after the torque conversion, via the gear output shaft 6 is stamped on a solar wheel of the secondary switching group 22 (not shown). The output from the secondary switching group 22 on the main output shaft 7 occurs via the intermediate wheel 25.
In the case of a gear change in the transmission 4 to a higher gear, the following takes place. While the shifting clutch 3 opens, the shifting brake clutch 9 approaches in an intersecting manner, whereby it comes to a friction force transfer within the shifting brake clutch 9 and, as a result, a torque flow occurs via the auxiliary shaft 16. Either the idle gear 19 or the idle gear 20 is launched via the coupling mechanism 21 in the output 18 of the auxiliary shaft 16. In both cases, the torque, adjacent to the auxiliary shaft 16, supports itself in the gear output 5. Through this, the main engine torque is reduced and the revolution speed of the drive shaft 2 is reduced by that amount, which corresponds to the revolution speed change from the current gear transition.
With the completion of the switching operation, the self-closing startup clutch 3, intersecting with the opening shifting brake clutch 9, undertakes the main engine torque such that, after the completion of the switching operation, the whole torque flow occurs in the by-passing of the auxiliary shaft 16.
For clarification of the connections, the processes with respect to time of some magnitudes relevant to the drive device are represented relative. to one another in
In the horizontal axis, the time t is plotted respectively, whereby the points in time t1 or t2 represent the beginning or the end of a mechanical gear change process.
Starting from the bottom in
Up to the point in time t1, at the start of the mechanical switching operation, the torque flow occurs via the closed shifting clutch 3, whose transferred torque after the point in time t1 is reduced by a steered, slip-afflicted opening up to a value equal to or approaching zero. Nearly to the same degree, the shifting brake clutch 9 undertakes a rising torque through a steered, slip-afflicted approach. At the point in time t2, at the end of the mechanical switching operation, the shifting clutch 3 undertakes torque again, while the torque transferred via the shifting brake clutch 9 is reduced.
Curve 34, shown lying above it in
Curves 38 or 40 portray the process of the main engine torque or the transmission torque in the case of a shift upwards, whereby the process of curve 40 is marked by way of dashes. Only in the time interval between the points in time t1 and t2 do these two curves 38, 40 deviate from one another.
From the process of curve 34, it is readily discernible that the tractive force is indeed diminished by the intersection of the torque processes 30 and 32, but advantageously does not completely collapse.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2004 002 283 | Jan 2004 | DE | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/EP2004/014204 | 12/14/2004 | WO | 00 | 6/28/2006 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2005/068879 | 7/28/2005 | WO | A |
| Number | Name | Date | Kind |
|---|---|---|---|
| 3527119 | Nasvytis | Sep 1970 | A |
| 4261216 | Braun | Apr 1981 | A |
| 4544057 | Webster et al. | Oct 1985 | A |
| 4583426 | Chassagnette et al. | Apr 1986 | A |
| RE33126 | Wittke | Dec 1989 | E |
| 5030179 | Ganoung | Jul 1991 | A |
| 6095001 | Ruehle et al. | Aug 2000 | A |
| 7070534 | Pelouch | Jul 2006 | B2 |
| Number | Date | Country |
|---|---|---|
| 958 081 | Feb 1957 | DE |
| 196 52 916 | Jun 1998 | DE |
| 198 44 783 | Mar 2000 | DE |
| 0 933 558 | Aug 1999 | EP |
| 1 096 172 | May 2001 | EP |
| 1 190 887 | Mar 2002 | EP |
| 1 251 296 | Oct 2002 | EP |
| 2 831 234 | Apr 2003 | FR |
| 632861 | Dec 1949 | GB |
| Number | Date | Country | |
|---|---|---|---|
| 20070150150 A1 | Jun 2007 | US |
