Abstract:
In a process for controlling an automatic gearbox, an electronic gear box control ( 13 ) calculates in a first mode of operation a driving activity and determines the set gradient of the gear box input speed of rotation depending on the driving activity. In a second mode of operation, the electronic gear box control selects a special program among a plurality of special programs and determines the set gradient of the gear box input speed of rotation depending on the selected special program.

Description:
BACKGROUND OF THE INVENTION 
     The invention relates to a process for controlling an automatic transmission where an electronic transmission control, during a gear shift, determines the actual gradient from a transmission input rotational speed by comparing the actual with a standard value and determining the divergence. The clutches involved in the gear shift are then regulated so that the divergence is reduced between actual and set gradient of the transmission input rotational speed. 
     SUMMARY OF THE INVENTION 
     In automatic transmissions, the shift time determines the comfort of a gear shift. Shift time is understood as the space of time during which a transmission input rotational speed changes from a rotational speed level of a first reduction ratio to a rotational speed level of a second rotational speed ratio. Shift time that is too short causes a definite jolt. A shift time that is too long causes an excessively great heat input in the clutches involved in the gear shift. To this extent, the shift time represents a compromise between the two extremes mentioned above. A process for control/regulation of a gear shift is proposed, e.g. in EP-PS 0 339 664. In this process, shift time is adjusted by calculating an actual gradient from the transmission input rotational speed and comparing it to a set gradient. 
     In practice, however, it has been demonstrated that many drivers subjectively find bad constant shift time. Therefore, the problem which the invention solves is to more intimately combine the behavior of the automatic transmission with the driver&#39;s behavior. 
     A first inventive solution consists of a first mode of driving in which electronic transmission control cyclically calculates driving activity from input variables of the vehicle and the driver, and changes the set gradient of the transmission input rotational speed according to the driving activity. In a second mode of driving, the electronic transmission control selects a special program from several, and changes the set gradient of the transmission input rotational speed according to the selected special program. As stated in claim  2 , in the first mode of driving, the set gradient is changed in the sense that a high set gradient is adjusted during high driving activity. 
     The inventive solution and the development thereof offer the advantage that a driver&#39;s behavior determines the shift sequences. In comfort-oriented driving mode, there results smooth, long gear shifts. From a sport mode of driving short gear shifts result. In automatic transmissions having a so-called “intelligent” shift program, a driving activity is calculated for selecting the shift points. Such processes have been disclosed, e.g. in DE-PS 39 22 051 and DE-OS 39 41 999. The inventive solution results in the added advantages that the already determined driving activity can be returned to and the inventive solution can be economically integrated via existing software. 
     In one development of the invention, it is proposed that in the second mode of operation, the set gradient of the transmission input rotational speed be changed in direction of lower values when one of the following special programs is active: winter program, slip regulation of the input gears, cruise control function, or city program. The effect of the development is that the gear shifts are very smoothly performed and, e.g. in the winter program, unsafe driving situations are prevented. 
     In a further development of the invention, it is proposed that in the second mode of operation the set gradient of the transmission input rotational speed be changed in a direction of higher values, i.e. to a short shift time, when one of the special programs such as mountain/trailer, or downhill is active. An advantage results when driving uphill with a trailer when due to the short shift time after the gear shift, a sufficiently high acceleration capacity is available. 
     In a second inventive solution of the problem, it is proposed that the electronic transmission control change the set gradient of the transmission input rotational speed, depending on a shift program activated by means of a program selector switch. The inventive solution can be preferably used in conventional automatic transmissions. In conventional automatic transmissions, the driver can select, via a switch, e.g. between economical “E”, sporting “S” and winter “W” programs. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     A preferred embodiment is shown in the Figures. Shown is: 
     FIG. 1 is a system diagram; 
     FIG. 2 is a table of the clutch logic; 
     FIG. 3 is a program flow chart for the first solution; 
     FIG. 4 is a program flow chart for the second solution; 
     FIG. 5 is a time diagram for a downshift in traction; 
     FIG. 6 is a time diagram for an upshift in traction; 
     FIG. 7 is a time diagram for a downshift in push; 
     FIG. 8 is a time diagram for a double downshift in constant driving activity; and 
     FIG. 9 is a time diagram for a double downshift in changing driving activity. 
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENT 
     FIG. 1 shows a system diagram of an automatic transmission. It consists of the mechanical part proper, a hydrodynamic torque converter  3 , a hydraulic control unit  21  and an electronic transmission control  13 . The automatic transmission is driven by an input unit  1 , preferably an internal combustion engine, via an input shaft  2 . This is non-rotatably connected with the impeller  4  of the hydrodynamic torque converter  3 . As known already, the hydrodynamic torque converter  3  consists of an impeller  4 , a turbine wheel  5  and a stator  6 . Parallel with the hydrodynamic torque converter  3  is situated a torque converter clutch  7 . The torque converter clutch  7  and the turbine wheel  5  lead to a turbine shaft  8 . When the torque converter clutch  7  is actuated, the turbine shaft  8  has the same rotational speed as the input shaft  2 . The mechanical part of the automatic transmission consists of clutches and brakes A to G, a free wheel  10  (FL 1 ), a Ravigneaux set  9  and a rear-mounted planetary gear  11 . The output takes place via a transmission output shaft  12 . This leads to a differential (not shown) which, via two axle half shafts, drives the input gears of a vehicle (not shown). A gear step is defined via an adequate clutch/brake combination. The coordination of the clutch logic to the gear step can be seen in FIG.  2 . For example, in a downshift from the fourth to the third gear, the brake C closes and the clutch E is deactivated. As further seen from Table  2 , the gear shifts from the second up to the fifth ratio steps are each carried out as overlapping gear shifts. Since the mechanical part is not relevant for the understanding of the invention, a detailed description is omitted. 
     Depending on the input variables  18  to  20 , the electronic transmission control  13  selects a corresponding driving step. The electronic transmission control  13  then activates a corresponding clutch/brake combination via the hydraulic control unit  21  where electromagnetic actuators are located. During the gear shifts, the electronic transmission control  13  determines the pressure curve of the clutches/brakes involved in the gear shift. On the electronic transmission control  13 , there are shown as blocks in extensively simplified manner: micro-controller  14 , memory  15 , function block control actuators  16  and function block calculation  17 . In the memory  15  are stored the data relevant to the transmission. Data relevant to the transmission are, e.g. programs, shift characteristic fields and characteristic values specific to the vehicle the same as diagnostic data. The memory  15  is usually designed as EPROM, EEPROM, or buffered RAM. In the function block calculation  17  are calculated from input variables the data relevant for a gear shift curve and the driving activity. The function block control actuators  16  serve to control the actuators located in the hydraulic control unit  21 . Input variables  20  are fed to the electronic transmission control  13 . Input variables  20  are, e.g. a variable representative of the driver&#39;s desired performance such as the accelerator pedal/throttle valve position, manual gear shift requirements, the signal of the torque generated by the internal combustion engine, the rotational speed or temperature of the internal combustion engine, etc. Data specific to the internal combustion engine are usually made available by a motor control unit. This is not shown in FIG.  1 . As added input variables, the electronic transmission control  13  receives the rotational speed of the turbine shaft  18  and of the transmission output shaft  19 . As an alternative to an intelligent system, FIG. 1 shows with reference numeral  22  a program selector switch so that the process can also be used for conventional automatic transmissions. 
     FIG. 3 shows a program flow chart for the first inventive solution. It is preferably used in automatic transmissions having an intelligent shift program. Such an intelligent shift program has been disclosed, e.g. in DE-PS 39 22 051 and DE-OS 39 41 999. In the intelligent shift program, a driving activity FA is determined from variables specific to the vehicle and the driver&#39;s behavior. The driving activity FA ultimately determines the shift point of the automatic transmission. The program flow chart begins at step S 1  with the question whether a gear shift is needed. If that is not the case, the program terminates with step S 2 . In case of positive result to the question, the mode of operation BA is questioned in step S 3 . If the result of the question is that the first mode of operation (BA=1) is active, the loop is traversed with S 4  and S 5 . If established that the second mode of operation (BA=2) is active, the loop is traversed with S 6  and S 7 . If in step S 3 , the result of the question is that the first mode of operation is active; in step S 4 , either the driving activity FA is determined, or the driving activity already calculated by the electronic transmission control to determine the shift points is used. In step S 5 , a gradient set value of the transmission input rotational speed nT(GRAD-SOLL) is then adjusted depending on the driving activity. In practice, this is implemented in a manner such that sport mode of operation results in a higher driving activity and thus a higher gradient set value of one in the sense of a shorter shift time. Conversely, a very economical mode of driving results in a lower driving activity and ultimately to a small gradient set value of the transmission input rotational speed. For safety reasons, the value range within which the gradient set value can be adjusted is defined by a maximum and minimum gradient value. Within the range, the gradient set value can be arbitrarily changed. In step S 3 , if the result of the question is that the second mode of operation (BA=2) is activated; step S 6  then tests which special program is active. Special programs are: winter program, slip regulation of the input gears, cruise control function, city/trailer program, downhill program, and upshift prevention. Step S 7  defines the gradient set value (GRAD-SOLL) of the transmission input rotational speed as a function of the special program. This is implemented in a manner such that the set gradient is changed to smaller values when either the winter program, the slip regulation of input gears, the cruise control function, or the city program is active. The set gradient is likewise adjusted to lower values when the special program upshift prevention terminates. As known, the special program upshift prevention forestalls the carrying out of a gear shift. This development prevents the driver, after the upshift prevention terminates (such as after traversing a curve), being surprised by too hard a gear shift. The set gradient of the transmission input rotational speed is changed in a direction of higher values, in the sense of a shorter shift time, when the mountain/trailer program or the downhill program is activated. It is thereby ensured that, e.g. when driving uphill with a trailer, a sufficiently high output torque is available soon after a traction downshift. Step S 8  determines whether the gear shift develops as traction or pull shift. Step S 9  determines whether an upshift or a downshift is required. Step S 10  then controls/adjusts the clutches involved in the gear shift which, in an overlapping shift, are a first opening clutch K 1  and a second closing clutch K 2 . Thereafter follows, in step S 11 , the question whether the gearshift end (e.g. the synchronization point), has been detected. If this is not the case, a holding pattern is passed through. If the end of the gear shift is detected, the program terminates. 
     FIG. 4 shows the program flow chart for the second invention solution. This program is preferably used in conventional automatic transmissions, wherein the driver can choose by means of a switch from three programs, usually an economic “E”, a sport “S” and a winter “W” program. Up to step S 3 , the program flow chart is identical with that of FIG. 3 so what has been described there applies here. In step S 3 , the position of the program selector switch is determined. In step S 4  is preset, depending on the selector switch of this program, the gradient set value nT(GRAD-SOLL) of the transmission input rotational speed. In practice, this is effected so that in the program switch positions “E” and “W”, a very low set value of the gradient is preset in the sense of a long shift time. The steps S 5  to S 8  are identical with steps S 8  to S 11  of FIG. 3 so that what has been described there also applies here. 
     FIG. 5 shows a time diagram for a downshift in traction. FIG. 5 consists of the parts FIGS. 5A to  5 D. Each one shows in the course of time: 
     FIG. 5A the shift command substantially issued by the electronic transmission control; 
     FIG. 5B the curve of the transmission input rotational speed nT; 
     FIG. 5C the pressure curve of the first disengaging clutch K 1 ; and 
     FIG. 5D the pressure curve of the second engaging clutch K 2 . 
     In FIGS. 5B,  5 C and  5 D, three case examples are shown wherein the same types of lines correspond to the same example. 
     In the first case example, shown in FIGS. 5B to  5 D as a solid line, a compromise between a sporting and a comfortable shift sequence is shown. FIG. 5B thus corresponds to the curve path with the points A and B, FIG. 5C to the curve path with the points E, F and G, and FIG. 5D to the curve path with the points M, N and O. The sequence is as follows: at time t 1  the electronic transmission control  13  issues the shift command substantially to the automatic transmission. Thereby the pressure level of the first clutch K 1  is reduced from a first pressure level p 1  to a second pressure level p 2 . Thereafter a negative pressure ramp begins for the first clutch up to time t 3  at point F. Also between time t 1  and time t 2 , the second clutch K 2  is actuated with a high pressure level, rapid filling pressure. Thereafter begins the filling equalizing phase for the second clutch K 2 . As result of the reduced pressure level of the first clutch K 1 , the transmission input rotational speed nT begins to increase at time t 3 . In the space of time t 3  to t 5 , the pressure level of the first clutch K 1  is reduced according to a second negative pressure ramp. Shortly before time t 5 , the pressure level of the second clutch is intensively raised so that it takes over the load of the internal combustion engine when the transmission input rotational speed nT has reached the synchronization point at time t 5  at point B. Thereafter the pressure level of the second clutch K 2  remains constant. At time t 5 , the first clutch K 1  is disengaged. 
     The second case example, shown in hatched lines in FIG. 5B to  5 D, represents a gear shift sequence in sport mode of driving with high driving activity FA. In FIG. 5B, this corresponds to the curve path of points A and C, FIG. 5C the curve path of points E, H and J and, in FIG. 5D the curve path of points M, N, and P. Up to time t 3 , the curve path is identical with the first case example so that what has been described there applies here. The pressure level at point H of the first clutch K 1  is lower than that at point F. As a consequence of this, the transmission input rotational speed nT begins at time t 3  to rise more quickly than the first case example. For the first clutch K 1 , a negative pressure ramp, end point J, follows in the space of time t 3 /t 4 . Shortly before time t 4 , the pressure level of the second clutch K 2  is quickly raised (pressure level point P), so that at the synchronization point, corresponding to point C in FIG. B, the clutch can reliably take over the load. 
     The third case example drawn in dot-dash line shows a comfortable gear shift sequence. In FIG. 5B, this corresponds to the curve path of points A, D. In FIG. 5C, this corresponds to the curve path of points E, K and L, and in FIG. 5D, this corresponds to the curve path of points M, N and Q. Up to time t 3 , the curve is identical. At time t 3 , the first clutch K 1  has reached the pressure level of point K. The pressure level K is higher than that of point F. Consequently, the transmission input rotational speed nT begins to rise more slowly than in the first case example. For the first clutch K 1 , a negative pressure ramp acts in the time period t 3  to t 6  at point L. Shortly before time t 6 , the pressure level of the second clutch K 2  is raised, corresponding to point Q. At time t 6 , the second clutch K 2  takes over at synchronization point D the load of the internal combustion engine. In FIG. 5B, the curve path A, C corresponds to the maximum possible gradient GRAD(MAX) of the transmission input rotational speed nT. This results from the quickest possible uptake of the internal combustion engine with the condition that the first clutch K 1  be disengaged. The curve path with the points A, D shows the smallest possible gradient GRAD(MIN) of the transmission input rotational speed nT. This results from the maximum admissible heat input of the second clutch K 2 . Between the two curve paths, depending on the driving activity FA, the gradient set value nT(GRAD-SOLL) of the transmission input rotational speed nT can be arbitrarily changed. 
     FIG. 6 shows a time diagram of an upshift in traction. In the course of time, the Figures each show: 
     FIG. 6A the shift command substantially issued by the electronic transmission control; 
     FIG. 6B the curve of the transmission input rotational speed nT; 
     FIG. 6C the pressure curve of the first disengaging clutch K 1 ; and 
     FIG. 6D the pressure curve of the second engaging clutch K 2 . 
     FIGS. 6B and 6D show three case examples wherein lines of the same type correspond to the same example. 
     The first case example, shown in FIGS. 6B and 6D as a solid line, is a compromise between a sport and a comfortable shift sequence. This corresponds in FIG. 6B to the curve path of points A, B. In FIG. 6D, this corresponds to the curve path of points D to H. The sequence is as follows: at time t 1 , the electronic transmission control  13  issues the shift command SB to the automatic transmission. The signal curve in FIG. 6A changes from one to zero. The second clutch K 2  up to time t 2  is filled with rapid filling pressure, pressure level corresponding to point D. A filling compensation phase and a pressure ramp, initial point E and end point F then follows. During the pressure ramp, the second clutch K 2  begins to take over the load, which is detected by the transmission input rotational speed beginning to change at time t 3  at point A. Since the second clutch K 2  begins to take over the load, the first clutch K 1  can be disengaged at time t 3 . Upon reaching the pressure level of point F of the second clutch K 2 , a second pressure ramp, end point G, begins for the clutch K 2 . The end point G or time t 6  corresponds to the synchronization point of the second ratio step. This corresponds in FIG. 6B to point B. Upon reaching the synchronization point at time t 6 , the pressure level of the second clutch K 2  is raised step by step up to the pressure level of point H at time t 7 . Thereafter the gear shift terminates. 
     The second case example shown in FIGS. 6B and 6D as hatched lines, represents a shift sequence in sport mode of driving. Up to the end of the filling compensation phase of the second clutch K 2 , the curve is identical with that of the first case example. However, the first pressure ramp of the second clutch K 2 , initial point E and end point F 1 , is here designed steeper compared to the first case example. The effect of this is that at time t 3  at point A, the transmission input rotational speed changes with a larger gradient to the synchronization point of the second ratio step, the synchronization point corresponds to point C in FIG.  6 B. When the pressure level F 1  of the second clutch K 2  is reached, a second pressure ramp begins and extends to time t 4 , end point J. Time t 4  corresponds to the time when the transmission input rotational speed nT reaches the synchronization point C. Thereafter the pressure level of clutch K 2  is raised slopingly up to the pressure level of point K, time t 5 . The gear shift terminates here. 
     The third case example shown in FIGS. 6B and 6D as dotted lines, represents a shift sequence in comfort-conscious mode of driving. Up to the end of the filling compensation phase of the second clutch K 2 , the curve is identical with that of the first case example. However, the first pressure ramp of the second clutch K 2 , initial point E, end point F 2 , is designed for shorter time than the pressure ramp in the first case example. Alternately, the first pressure ramp can be designed flatter. Thereafter from point F 2  up to time t 8 , end point L, is the second pressure ramp of the second clutch K 2 . As result of the shorter or flatter first pressure ramp and the flatter second pressure ramp of the second clutch K 2 , the transmission input rotational speed nT changes after point A with a smaller gradient. Time t 8  is reached when the transmission input rotational speed nT arrives at the synchronization point D of the second ratio step. Thereafter the pressure level of the second clutch K 2  is slopingly raised to the pressure level of point M, at time t 9 . Thereafter the gear shift terminates. 
     FIG. 7 shows a time diagram for a downshift in push. FIG. 7 consists of FIGS. 7A to  7 D. Each Figure, respectively, shows in the course of time: 
     FIG. 7A the shift command SB issued by the electronic transmission control; 
     FIG. 7B the curve of the transmission input rotational speed nT; 
     FIG. 7C the pressure curve of the first disengaging clutch K 1 ; and 
     FIG. 7D the pressure curve of the second engaging clutch K 2 . 
     Each one of the FIGS. 7B and 7D shows three case examples wherein the same type of lines correspond to the same example. 
     The first case example, shown in FIGS. 7B and 7D as a solid line, represents a compromise between a sport and a comfortable shift sequence. In FIG. 7B, this corresponds to the curve path of points A, B. In FIG. 7D, this corresponds to the curve path of points E to H. The sequence is as follows: at time t 1 , the electronic transmission control  13  issues the shift command SB to the automatic transmission. The signal curve, in FIG. 7A, changes from one to zero. The second clutch K 2  is loaded up to time t 2  with rapid filling pressure. Thereafter follows up to time t 3  a filling compensation phase followed by a first pressure ramp beginning at point F and ending at point G. At the end of the rapid filling phase of the second clutch K 2  (i.e. at time t 2 ), the pressure level of the first clutch K 1  is slopingly reduced to zero. Consequently, the transmission input rotational speed nT begins to rise at time t 3  at point A. The gradient of the transmission input rotational speed is determined, via the first pressure ramp, points F to G, of the second clutch K 2 . At time t 6 , the transmission input rotational speed nT reaches the synchronization point B of the second ratio step. At this time, the pressure of the second clutch K 2  is then slopingly raised to the pressure level of point H. This is reached at time t 7 , thereafter the gear shift terminates. 
     The second case example, shown in FIGS. 7B and 7D as hatched lines, represents a shift sequence in sport mode of driving. This corresponds in FIG. 7B to the curve path of points A, C and, in FIG. 7D, to the curve path of points E, F, J and K. Up to time t 3 , the curve is identical with that of the first case example so that what has been described there applies here. At time t 3  the first pressure ramp begins for the second clutch K 2 , between initial point F and end point J. This pressure ramp has a larger gradient than the pressure ramp of the first case example. Hereby the transmission input rotational speed nT is, therefore, quickly drawn to the synchronization point C of the second ratio step. The gradient of the transmission input rotational speed is raised in comparison with the first case example. After reaching the synchronization point C, the second clutch is slopingly raised from time t 4  to the pressure level of point K. This is reached at time t 5 , thereafter the gear shift terminates. 
     The third case example, shown in FIGS. 7B and 7D as a dash-dot line, represents a comfortable shift sequence. In FIG. 7B, this corresponds to the curve path of points A, D. In FIG. 7D, this corresponds to the curve path of points E, F, L and M. Up to time t 3 , the curve is identical with the first and second examples. At time t 3  the first pressure ramp begins for the second clutch K 2  between initial point F and end point L. The first pressure ramp of the second clutch K 2  is flatly laid out. The transmission input rotational speed nT changes less markedly than in the first and second case examples, and the gradient of the transmission input rotational speed is thus smaller. At time t 8 , the transmission input rotational speed nT reaches the synchronization point D of the second ratio step. Thereafter the pressure level of the second clutch K 2  is slopingly raised up to the pressure level of the point M, t 9  moment, thereafter the gear shift terminates. 
     FIG. 8 shows a time diagram for a double downshift with constant driving activity. Here the Figures show in the course of time: 
     FIG. 8A the driver&#39;s desired performance FL; 
     FIG. 8B the shift command SB issued by the electronic transmission control; 
     FIG. 8C the curve of the transmission input rotational speed nT; 
     FIG. 8D the pressure curve of the disengaging clutch K 1 ; and 
     FIG. 8E the pressure curve of the engaging clutch K 2 . 
     FIGS. 8B to  8 E show each of two case examples, lines of the same type correspond to the same example. 
     The first case example, shown in FIGS. 8B to  8 E as solid lines, represents a compromise between a sport and a comfortable shift sequence. In FIG. 8B, this corresponds to the curve path of points D 1 , E 1  and F 1 . In FIG. 8C, this corresponds to the curve path of points A to D. In FIG. 8D, this corresponds to the curve path of points H, J and K for the first disengaging clutch and to the curve path of points H, L and M for the second disengaging clutch. In FIG. 8E, this corresponds to the curve path of points S, T and U for the first closing clutch and the curve path of points V, W and X for the second closing clutch. At time t 1 , the driver desires, as shown in FIG. 8A, a first downshift and at time t 2 , a second downshift. As a result of the downshift desired performance, the electronic transmission control  13  issues a shift command SB. The signal level in FIG. 8B changes from two to one. As a result of the shift command, the pressure level of the first clutch K 1 , from point H slopingly decreases to point J. A rapid filling phase simultaneously begins for the second clutch K 2 , pressure level corresponding to point S, up to time t 2 . At time t 2 , the curve of the transmission input rotational speed nT begins at point A to change in the direction of the synchronization point B. The transmission input rotational speed nT reaches the synchronization point B at time t 5 . During the time period t 2 /t 5 , the pressure level of the first clutch K 1  is kept constant. Alternately, the pressure curve of the first clutch K 1  can also be designed to slightly drop. Shortly before reaching the synchronization point at time t 5 , the pressure level of the second clutch K 2  corresponding to the pressure level of point T is slopingly raised to the pressure level at point U. The pressure level of point U is reached at time t 5  so that the second clutch K 2  can reliably take over the load of the internal combustion engine at synchronization point B. At time t 5 , the first downshift is terminated. Upon detection of synchronization point B, the electronic transmission control issues the shift command for the second downshift. The signal level in FIG. 8B changes from one to zero. As a result of the downshift command, the pressure level of the first clutch K 1  (the second opening clutch), slopingly decreases from point L. Simultaneously the second clutch K 2  (the second closing clutch), begins the rapid filling phase followed by a filling compensation phase which ends in point W. At time t 7 , the transmission input rotational speed nT begins from point C to rise to the new synchronization point D. Shortly before reaching the synchronization point, at time t 8 , the pressure level of the second clutch K 2  slopingly rises to the pressure level at point X so that at time t 8  it can reliably take over the load of the internal combustion engine at the synchronization point D. Likewise at time t 8 , the first clutch K 1  is disengaged at point M. Thereafter the gearshift ends. 
     In the second case example drawn in hatched line, a sport shift sequence is shown. In FIG. 8B, this corresponds to the curve path of points D 1 , D 2  and F 1 . In FIG. 8C, this corresponds to the curve path of points A, E, F and G. In FIG. 8D, this corresponds to the curve path of points H, N and O for the first opening clutch and the curve path of points H, P, Q and R for the second opening clutch. In FIG. 8E, this corresponds to the curve path of points S, Y, Z and U for the first engaging clutch and the curve path of points A 1 , B 1  and C 1  for the second engaging clutch. Up to time t 2 , the sequence is identical with the one of the first case example, but unlike the first case example, the negative pressure ramp begun for the first clutch K 1  at point H is reduced to the pressure level at point N. The transmission input rotational speed nT thereby changes more quickly from point A than in the first case example. Shortly before reaching the synchronization point at point E, the second clutch K 2  is guided from the pressure at point Y to the pressure level at point Z so that at time t 3 , it can reliably take over the load of the internal combustion engine at the synchronization point. Simultaneously at time t 3 . the first clutch K 1  is disengaged at point O. At time t 3 , the electronic transmission control, similarly, issues the downshift command SB for the second downshift. The second clutch K 2  is filled with rapid filling pressure, pressure level corresponding to point A 1 . Also at time t 3 , the pressure level of the first clutch K 1  is reduced from point P to point Q. As a result of the dead time of the hydraulic system, only at time t 4  at point F does the transmission input rotational speed nT begin to change in direction of the new synchronization point G. Shortly before reaching the synchronization point G, the pressure level of the second clutch K 2  is raised from the pressure level of point B 1  to point C 1  in order to reliably take over the load of the internal combustion engine at the synchronization point G. The synchronization point G is reached at time t 6  allowing the first clutch to be disengaged at point R, thereafter the gear shift terminates. 
     As shown in FIG. 8C, the gradient of the transmission input rotational speed can thus be changed, depending on the driving activity between the two extreme curve paths, namely, A, B, C and D and A, E, F and G. 
     FIG. 9 shows a time diagram for a double downshift. In this representation it has been assumed that the driving activity changes during the gear shift. The Figures show in the course of time: 
     FIG. 9A the driver&#39;s desired performance FL; 
     FIG. 9B the shift command SB; 
     FIG. 9C the curve of the transmission input rotational speed nT; 
     FIG. 9D the pressure curve of the first clutch K 1 ; and 
     FIG. 9E the pressure curve of the second clutch K 2 . 
     In FIGS. 9B to  9 E, two case examples are again shown. The first case example, drawn as solid line, corresponds to the first case example of FIG. 8 so that a new description is omitted. At time t 3 , the driver desires a second downshift. In FIG. 9A, the signal level FL changes from one to zero and the electronic transmission control issues the shift command SB. This is shown in FIG. 9B by the signal level changing from one to zero. It is now assumed that in the time period t 1  to t 3 , the driving activity FA has increased. As result of the shift command SB the pressure level of the first clutch K 1  from point N slopingly decreases to the pressure level of point O. At time t 2 , the pressure level of the second clutch K 2  slopingly increases according to the line YZ so that at the synchronization point F, it can reliably take over the load at time t 4 . When reaching the synchronization point at time t 4 , the second clutch K 2  (the second engaging clutch), is filled by rapid filling pressure, to the pressure level at point A 1 . Likewise at time t 4 , the pressure level of the first clutch K 1  (the second disengaging clutch here), decreases from point P down to the pressure level of point Q. Consequently, the transmission input rotational speed nT changes overtime in direction of the new synchronization point G. Shortly before reaching the synchronization point, the pressure level of the second clutch K 2  is guided from the pressure level of point B 1  to the pressure level of point C 1  so that it can reliably take over the load at the synchronization point G. At time t 6 , synchronization point G is reached, thereafter the gear shift terminates. 
     As shown in FIG. 9C, a change of the driving activity immediately leads to a change in the gradient of the transmission input rotational speed. A higher activity causes a larger gradient since that the shift time is reduced. 
     In FIGS. 5 to  9 , controlled pressure sequences of the first and second clutch K 1  or K 2  are shown. In practice, an adjustment process can be superimposed on the control process. The adjustment process regulates the gradient of the transmission input rotational speed nT. The first clutch K 1  would thus be additionally adjusted in FIG. 5C; in FIGS. 6D and 7D, the second clutch K 2 ; and in FIG. 8D, the first clutches K 1 . 
     REFERENCE NUMERALS 
       1  input unit 
       2  input shaft 
       3  hydrodynamic torque converter 
       4  impeller 
       5  turbine wheel 
       6  stator 
       7  torque converter clutch 
       8  turbine shaft 
       9  Ravigneaux set 
       10  free wheel FL 1   
       11  planetary gear set 
       12  transmission output shaft 
       13  electronic transmission control 
       14  micro-controller 
       15  memory 
       16  function block control actuators 
       17  function block calculation 
       18  signal of turbine rotational speed 
       19  signal of transmission output rotational speed 
       20  input variables 
       21  hydraulic control unit 
       22  program selector switch