Abstract:
A method for controlling preferably an electro-hydraulic automatic transmission of a motor vehicle fitted with a combustion engine provides a gradual kick-down while braking. In particular the kick-down is performed when, in the course of approaching a bend, a condition is activated, which prevents upshifting. The upshift prevention is initiated when the accelerator pedal is released quickly during shearing action. The upshift prevention stops if after an interval, upon detection of tensile action, the vehicle does drive round a bend. The upshift prevention is followed by a gradual adaptation of the gear level to the shift parameter.

Description:
BACKGROUND AND SUMMARY OF THE INVENTION 
     This invention relates to a method for controlling preferably an electro-hydraulic automatic transmission of a motor vehicle specially fitted with a combustion engine, while the combustion engine can be influenced via control elements, preferably an accelerator pedal or a throttle valve, and gear levels of a transmission are shifted via shifting parameters which, at least as a function of the throttle valve position, the traveling speed and motor speed, are shifted automatically. 
     Common automotive transmissions of motor vehicles powered by combustion engines initiate, as a rule, an upshift (reduction of the speed ratio) when releasing the accelerator pedal. This, however, is not always desirable when driving around bends, because this type of change of load may possibly result in unsafe driving conditions or, when reaccelerating the vehicle by stepping on the gas, it is necessary to force one or several kick-downs (increase in the speed ratio). 
     From DE 33 41 652 C2, (having corresponding U.S. counterpart U.S. Pat. No. 4,679,145) it has become common knowledge that this type of upshifting in bends can be avoided through recording the transverse acceleration of the vehicle. However, by these means, one would merely avoid upshifting in bends. 
     In order to be able to avoid upshifting as soon as the vehicle approaches a bend, during the method of controlling an automatic transmission according to DE 39 22 040 A1, the change of speed effected by the accelerator pedal is recorded and by dropping below a specific (negative) limiting value, a signal preventing the upshifting is transmitted if a shearing action is detected. As a result, upshifting is prevented until the tensile action occurs and a fixed interval has passed. 
     DE 39 22 040 A1 (having corresponding U.S. counterpart U.S. Pat. No. 5,157,609) also provides that this interval is a function of an additional parameter (driving activity), which is derived from a multitude of operating or driving parameters of a motor vehicle and evaluates the driver&#39;s style of driving or a momentarily existing traffic situation. 
     In view of the state-of-the-art referred to in the foregoing, it is the object of the present invention to create a method for controlling an automatic transmission of a motor vehicle, which is improved further with respect to shift performance during braking, especially before entering bends. 
     The foregoing object is achieved in the present invention by the characteristic features that a gradual kick-down (increase in the gear ratio) occurs when a service brake of the vehicle is engaged, or alternatively in addition or supplementary thereto, the time variation of the traveling speed is less than a first negative longitudinal acceleration limiting value; and the transversal acceleration recorded by the transversal acceleration sensor lies below a first traveling speed-dependent transversal acceleration limit; and the time variation of the traveling speed is higher than a second negative longitudinal acceleration limiting value; and the traveling speed is less than a second traveling speed acceleration limiting value. Further characteristics as a development of the invention are described herein. 
     The advantages of the invention are primarily that a method for controlling an automatic transmission of a motor vehicle has been created, in which the shifting performance during braking, in particular before entering bends, has been improved further. 
     When reducing a vehicle&#39;s speed by braking, automatic kick-downs can be executed under certain conditions; the maintaining of conditions ensures a safe operation of the vehicle. The method especially ensures that the transversal acceleration is not too high, the vehicle&#39;s deceleration is not too great and the traveling speed is not too high, so as to avoid a loss, especially in the longitudinal and lateral stability of the wheels of the vehicle. 
     The brake torque of the driving (combustion) motor, which after kick-down has a stronger effect on the drive gears, can therefore not have a negative effect on the driving performance of the vehicle. In this case, kick-down occurs gradually, always by an interposition of a specific interval. 
     Kick-down while braking is preferably initiated when an upshift prevention condition is active. This is activated by a known method when the vehicle approaches a bend and the driver releases the accelerator pedal relatively fast. 
     On the one hand, by performing kick-downs during braking, the braking action of the vehicle&#39;s prime mover is intensified when in shearing action, so that the brakes (service brake) of the vehicle are relieved. On the other hand, in connection with maintaining the speed before, in the course of and after driving the bend, the driver, after passing through the bend, can always operate at the optimal gear level to reaccelerate the vehicle. 
     In the following, the invention is explained in greater detail by means of the drawing and particular embodiments. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 shows a circuit diagram of an electro-hydraulic control of an automatic transmission of a motor vehicle; 
     FIG. 2 shows a limiting characteristic curve for identifying the shearing/tensile action; 
     FIG. 3 shows a parameter of a motor speed-dependent and gear level-dependent parameter value; 
     FIG. 4 shows a first and a second limiting characteristic curve for a transversal acceleration; 
     FIG. 5 shows the parameter of a gear level-dependent and driving activity-dependent factor; 
     FIG. 6 shows a characteristic curve indicating the dependence of the intervals as a function of a driving activity. 
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     FIG. 1 shows an electro-hydraulic control 1 of an automatic motor vehicle transmission 2 as, for example, is described in Bosch&#39;s &#34;Technische Berichte&#34;, 7 (1983) 4, pp. 160 though 166, and in ATZ 85 (19983) 5, pp. 401 through 405. 
     Quantities or signals, which change with time t, are presented in the following with f(t). 
     A controlling apparatus 3 performs the controlling action as a function of a kick-down signal kd(t) of a kick-down transmitter 4 at the accelerator pedal of the motor vehicle, and as a function of an idling signal 11(t) of a throttle valve switch 5, as a function of a throttle valve position alpha(t) of a throttle valve angle transmitter 6 (or an equivalent position transmitter for positioning an element, for example, an accelerator pedal or an injection pump lever of a self-igniting diesel combustion engine, which influences the performance of the prime mover of the vehicle), as a function of a motor speed nmot(t) of a motor speed transmitter 7 of a combustion engine (not shown), and as a function of a traveling speed v(t) (transmission starting speed) of a transmission starting speed transmitter 8, 
     a pressure regulator 9 to regulate the pressure of a hydraulic fluid (signal output ds), 
     a first solenoid-operated valve 10 for controlling a converter or a converter bridging coupler (signal output wk), 
     a second solenoid-operated valve 11 for controlling a gear level change between gear levels I and II (signal output sI/II), 
     a third solenoid-operated valve 12 for controlling a gear level change between gear levels III and III (signal output sII/III), 
     a fourth solenoid-operated valve 13 for controlling a gear level change between gear levels III and IV (signal output sIII/IV). 
     The control system is usually controlled by the operator via a selector lever 14 for preselecting shift levels P, R, N, D, 3, 2, 1. Said lever allows the use of shift level P (parking brake), R (reverse gear level), N (neutral gear level), D (automatic shifting of all four gear levels IV, III, II, I) 3 (automatic shifting of gear levels III, II, I), 2 (automatic shifting of gear levels II, I) I (fixing the first gear level I). 
     With the above-described transmission, a program selector 15 is provided with which at least two shift programs (&#34;E&#34; for a consumption-optimized shift program (shift parameter SKF1), &#34;S&#34; for a performance-optimized (shift parameter SKF5), &#34;M&#34; for a manual program, in which gear levels IV, III, II, I can be preselected directly via positions D, 3, 2 and 1) or two shift parameters SKFj can be selected manually according to which the four gear levels in shift levels D, III and II are shifted automatically. 
     A control method may be implemented in the controlling apparatus 3 as an alternative to the program selector switch 15, which, for example, according to DE 33 48 652 C2 or DE 39 22 051 A1, (corresponding to U.S. Pat. No. 4,679,145 and 5,157,609, the originally filed specifications which corresponding to DE 33 48 652 C2 and DE 39 22 051 A1, respectively, being incorporated by reference herein) makes a long-term evaluation of the driver&#39;s style of driving or his handling of the traffic situation with respect to controlling the vehicle, and concludes a driving activity SK(t) (accelerator pedal activity) from one or several operating or driving parameters. On the basis of this driving activity SK(t), corresponding to the shift position of the change-over switch 15, then one of several shift programs or shift parameters SKFj can be applied for shifting gear levels IV, III, II, I. 
     To execute said method, apart from the transmitters 4 through 7, additional transmitters can be applied, for example, an air flow or supply sensor 16, which detects the air flow or volume ml(t) fed to the combustion engine, as well as a transversal accelerator transmitter 17 (transversal acceleration aq(t) and a brake signal transmitter 18 (brake signal b(t)) are required, and a reference speed transmitter 19, which detects the speed of the wheels of a non-driven axis (reference speed vref(t)). 
     It is, in particular, desirable to avoid an upshift of such a transmission when the vehicle, for example, approaches a bend and the driver releases the accelerator pedal. 
     As is illustrated in DE 39 22 040 A1 and DE 39 22 051 A1, this method of identifying a bend may occur through scanning the time variation of the throttle valve position dalpha(t)/dt. Usually, a driver releases the accelerator pedal--and as a rule also the throttle valve--faster before entering the bend than under normal circumstances to reduce, for example, the driving speed v(t). 
     According to the method, an upshift effected while releasing or not operating the accelerator pedal on common transmission controls with change speed drive is prevented, so long as the condition of upshift prevention hsv is active, hsv=1, while the condition of upshift prevention changes from inactive hsv=0 to active hsv--1 when a time variation dalpha(t)/dt of the throttle valve position alpha(t) goes below a negative limiting value--alphag and the shearing action is identified. The condition of uplift prevention hsv changes to inactive hsv=0, as soon as the tensile action has been identified after completion of the first interval TI(KK(t)). 
     What matters with tensile action and shearing action is the system under consideration, where the following differences may exist: 
     Overall system for motor vehicles: Tensile action is defined as the acceleration of the vehicle (time variation of speed) dv(t)/dtdt&gt;0, while the shearing action corresponds go a deceleration of the vehicle dv(t)/dt&lt;0. 
     System coupling (torque converter/transmission: During tensile action, the input speed of the clutch (of the torque converter) greater than its output speed/the transmission is tensioned in an opposite direction, while during shearing action the input speed is lower that the output speed/the transmission is tensioned in the same direction. 
     System of the combustion engine: Tensile action here is defined as the throttle valve position alpha(t)&gt;0 (throttle valve open) and the time variation of the motor speed dnmot(t)/dt&gt;0, while during shearing action the throttle valve position is alpha(t)=0 (throttle valve closed) and the time variation of the motor speed is dnmot(t)/dt&lt;0. 
     Concerning the transmission control and the overall performance of the vehicle it has proven practical to simulate the terms tensile action and shearing action as follows: 
     Shearing action is identified when the throttle valve position alpha(t) drops below a motor speed-dependent limiting characteristic curve azsg(nmot), as is shown on FIG. 2: alpha(t)&lt;azsg(nmot). 
     Tension action is identified when the throttle valve position alpha(t) exceeds the motor speed-dependent limiting characteristic curve azsg(nmot) according to FIG. 2 and adapts the time variation of the traveling speed dv)t)/dt adapts positive values: alpha(t)&gt;azsg(nmot)∩dv(t)/dt&gt;0. 
     The patent application overall makes reference to the above-defined terms tensile action and shearing action. 
     According to the invention, the braking action enables gradual kick-downs. Gradual kick-downs occurs only when 
     a service brake of the vehicle is engaged, brake signal b(t)=1, or alternatively in addition or supplementary thereto, the time variation of the traveling speed dv(t)/dt is less than a first negative longitudinal acceleration limiting value albg(g, nmot, t), albg(g, nmot, t)&lt;0: dv(t)/dt&lt;albg(g, nmot, t); and 
     the transversal acceleration aq(t) recorded by means of the tranversal acceleration sensor 17 lies below a first traveling speed-dependent transversal acceleration limit aqgl(v(t)): aq(t)&lt;aqgl(v(t)); and 
     the time variation of the traveling speed dv(t)/dt is higher than a second negative longitudinal acceleration limiting value albbg(nmot, g, SK(t), t)=k(g-l , SK(t))*dv/dt| g-l  : dv(t)dt&gt;albbg(nmot, g, SK(t), t); dv(t)dt&gt;=k(g-l, SK(t))*dv/dt| g-l  ; and 
     the traveling speed v(t) is less than a second traveling speed acceleration limiting value vg(g, SK(t), t): v(y)&lt;vg(g, SK(t), t). 
     Kick-down is performed preferably only when the above conditions are met and further, if the condition of the upshift prevention is active, hvs=1. 
     Kick-down is always performed by one gear level, while between shifting actions there lies at least a second interval T2(SK(t)). The gradual kick-down is performed to the gear level g, which is acceptable for the instantaneous operating point of the vehicle in the instantaneously set shift parameter (SKFj) (to avoid overspeeding of the combustion engine). 
     The first negative longitudinal acceleration limiting value albg(g, nmot, t) is a function of the instantaneous values of the engaged gear level g and the motor speed nmot(t) and in this case corresponds to the respective (negative) longitudinal acceleration dv/dt (and thus the deceleration) of the vehicle running with a shut throttle valve alpha=0 in the condition defined herein (loading, tire pressure, environmental factors, etc.) on a level roadway, with the respective pairs of value of the instantaneously engaged gear level g and the motor speed nmot(t). The first negative longitudinal acceleration limiting value albg(g, nmot, t) is determined from the instantaneous values of these quantities, preferably via a first parameter ALB(g, nmot): albg(g, nmot, t)=ALB(g, nmot). An example for such a first parameter ALB(g, nmot) is shown in FIG. 3. As an alternative it is, by all means, possible to determine the longitudinal acceleration limiting values albg(g, nmot, t) via a corresponding functional correlation. 
     The limiting curves according to FIG. 3 clearly shows the dependence of the deceleration values of a vehicle driven by a combustion engine from the gear level g and the motor speed nmot(t). The individual limiting curves--without limiting the generality--of the four gear levels I, II, III, IV here allocate the values applied to the horizontal axis for the motor speed nmot in rotations per minute (1/min) to a respective specific value ALB applied to the vertical axis as unit g=9.81. . . meters per second 2  (9.81 m/s 2 ). 
     For growing values of the motor speed nmot(t) the deceleration values increase as a result of concentrated braking effect of the motor and the increasing rolling resistance (drag) of the vehicle. There also is an increase in the deceleration values as the gear level g diminishes, because the brake torque of the combustion engine increases the deceleration rate of the vehicle due to the increase in the gear ratio. 
     The first transversal acceleration limit aqgl(v(t)) in this case is preferably a function of the traveling speed, and the corresponding assigned limiting values as a result of a limit of a specific traveling speed v(t) are reduced as the traveling speed v(t) increases. A corresponding characteristic curve is shown in FIG. 4. 
     The second negative longitudinal acceleration limiting value albbg(nmot, g, SK(t))=k(g-l, SK(t))*dv/dt| g-l  is determined according to a product from a gear level-dependent factor k(g-l, SK(t)) and a value computed with respect to the vehicle&#39;s instantaneous operating condition, which can be expected during acceleration dv/dt| g-l  at the next lowest gear level g-l. 
     In order to determine said longitudinal acceleration dv/dt| g-l  expected at said next lowest gear level g-l, the value of the instantaneous traveling speed v(t) taken from which then is determined the next lowest gear level g-l of the expected motor speed nmot(t)| g-l  =i(g-l)*v(t). For this purpose, the product is formed from the instantaneous value of the traveling speed v(t) and that of the transmission ratio i(g-l) in the next lowest gear level g-l. 
     The value of the longitudinal acceleration dv/dt| g-l  to be expected in the next lowest gear level g-l is ultimately determined via the parameter ALB(g, nmot) from the next lowest gear level g-l and the motor speed nmot(t)| g-l  to be expected in next lowest gear level. 
     The gear level-dependent factor k(g-l, SK(t)) is determine via a second parameter F(g, SK(t)) from the next lowest gear level (g-l): k(g-l, SK(t))=F(g, SK(t)). An example for a second parameter is shown in FIG. 5. 
     The second traveling speed limiting value vg(g, SK(t), t) is a function of the gear level g and the driving activity SK(t). 
     The effect of the individual steps of the method described herein are explained as follows: 
     By monitoring the activity of the vehicle&#39;s service brake (brake signal b(t)=1) or as an alternative or addition hereto, or by checking whether the time variation of the traveling speed dv(t)/dt is below the first negative acceleration limiting value albg(g, nmot), dv(t)/dt&lt;albg(g, nmot), the desired driving speed is obtained after increased deceleration of the vehicle or kick- down. 
     By checking whether the transversal acceleration aq(t) is below the first transversal acceleration limit aqgl(v(t)), it is monitored whether the vehicle is already in a bend at a relatively high transversal acceleration aq(t). If the vehicle actually is driving in the bend, the kick-down is forestalled, so as to prevent loss of frictional connection between wheel and roadway, which otherwise increases due to the increase in the brake effect. 
     A comparative safety function is represented by monitoring the reduction of the second negative longitudinal acceleration limiting value albbg(nmot, g, SK(t): In this case, it is determined whether the expected deceleration of the vehicle, following the required kick-down, would lead to exceeding the static friction limit of the wheels. 
     For this purpose, from the deceleration due to weighting (multiplication) with the gear level-dependent factor k(g-l, SK(t)), which can be expected during the instantaneous driving condition of the vehicle following the kick-down, an instantaneous maximum acceptable deceleration is determined, which is compared with the instantaneous vehicle deceleration dv(t)/dt; if the instantaneous deceleration is higher, the kick- down is prevented. 
     The gear level-dependent factor k(g-l, SK(t)) takes into consideration that the second negative longitudinal acceleration limiting value albbg must be lower than the first negative longitudinal acceleration limiting value albg(g, nmot), i.e. in terms of quantity it is greater (corresponding to a higher deceleration rate). 
     By monitoring the gear level-dependent traveling speed limiting value vg(g, SK(t), t), additional safety criteria can be satisfied with respect to kick-down at an excessively high traveling speed or the prevention of an excess of the speed limit of the driving combustion engine after kick-down. These safety criteria are highly vehicle-specific and, therefore, must be adapted individually to each vehicle, so that the presentation of a corresponding parameter is superfluous. 
     Also, in order to prevent a change in the gear level g while driving round a bend after approaching or braking before entering a bend, the transversal acceleration aq(t) of the vehicle is monitored. The change in the gear level g is prevented or the interval T1(SK(t)) is zeroed provided the amount of transversal acceleration (|aq(t)|) exceeds a second transversal acceleration limit aqg2(v(t)) as a function of the traveling speed v(t) according to FIG. 4, or so long as a third interval T3(SK(t)) has not passed after the falling short of the transversal acceleration limit aqg2(v(t)). In this case, the second transversal acceleration limiting value aqg2(v(t)) for detecting bends--as is illustrated in FIG. 4--is clearly lower than the first transversal acceleration limit aqgl(v(t)). 
     Further, even during shearing action, changing gear, especially kick-downs, can be prevented and/or the intervals T1(SK(t)), T2(SK(t)), T3(SK(t)) can be zeroed, provided excessive wheel slip occurs at least at one of the wheels of the vehicle or the frictional connection between at least one wheel of the vehicle and the roadway is interrupted. 
     In this case, shifting is permitted only if the differential speed value Dv(t)=vref(t)-v(t) between the speed vref(t) of a non-driven axis and the traveling speed v(t) recorded on a driven axis does not exceed an acceptable differential speed value Dvzu1(SK(t)): Dv(t)&lt;Dvzu1(SK(t)). 
     Further, when exceeding the acceptable differential speed value Dvzu1(SK(t)), 
     a converter bridging coupling of a transmission fitted with a torque converter can be opened; 
     a stopping time Th can be set, during which an upshift cannot be prevented; 
     the engaged gear level g can be increased by one level (upshift), and 
     kick-downs can be prevented; while these functions can be kicked down when tensile action is detected and positive values of the change in traveling speed v(t) exist. 
     The intervals T1(SK(t)), T2(SK(t)), T3(SK(t)) can both be of similar and varying length, and at least one of the intervals or of the traveling speed limiting value vg(g, SK(t), t) or the gear level-dependent factor k(g-l, SK)t)) or the acceptable differential speed value Dvzu1(SK(t)) are adjustable at random and, preferably together with adjusting the shifting parameters SKFj, can be so adjusted (consumption-optimized shift parameter SKF1, performance-optimized parameter SKF2) by means of the program selector switch 15, that with a greater number of performance-optimized parameters (driving programs) the intervals TI(SK(t)), T3(SK(t)) and the traveling speed limiting value vg(g, SK(t), t) increase and the intervals T2(SK(t)), Th(SK(t)), the gear level-dependent factor k(g-l, SK(t)) and the acceptable differential speed value Dvzu1(SK(t)) decrease (see FIG. 5 or FIG. 6). 
     If the transmission control provides for an automatic adaptation of the shift parameters to the driver&#39;s style of driving or a traffic situation, at least one of the intervals T1(SK(t)), T2(SK(t)) or Th(SK(t)) or at least the traveling speed limiting value vg(g, SK(t)) or the gear level-dependent factor k(g-l, SK(t)) or the acceptable differential speed value Dvzul(SK(t)) may be a function of the driving activity SK(t), which makes a long-term evaluation of the driver&#39;s style of driving or action in a traffic situation with respect to controlling the vehicle. As the driving activity SK(t) grows and becomes more performance-oriented, the intervals T1(SK(t)), T3(SK(t)) and the traveling speed limiting value vg(g, SK(t), t) increase and the intervals T2(SK(t)), Th(SK(t)), the gear level-dependent factor k(g-l, SK(t)) and the acceptable differential speed value Dvzu1(SK(t)) decrease (see FIG. 5 or FIG. 6). 
     The driving activity SK(t) is determined by a long-term evaluation of the driver&#39;s style of driving and action in a traffic situation with respect to functional correlation (continuous mean value formation) of actual and past values or a single operating characteristic quantity of a motor vehicle or a single operating characteristic quantity or a single quantity comprised of several operating characteristic quantities of a motor vehicle. This, for example, can occur analogously to the method illustrated in DE 39 22 051 A1 or DE 33 41 652 C2.