METHOD FOR EVALUATING THE SHIFTING BEHAVIOR OF A MOTOR VEHICLE TRANSMISSION

Abstract

A method for evaluating a transmission device using various characteristic values, wherein said characteristic values can be determined by means of variable or constant parameters.

Claims

1. A method for determining at least one parameter for the evaluation or optimizing of a transmission device for a motor vehicle able to be shifted between a first and at least one second speed ratio which comprises at least one transmission input element and at least one transmission output element and which can be connected in torque-conducting manner to at least one drive unit having a plurality of possible operating points which are at the least characterized by the torque output or input by the drive unit and the engine speed and which is provided in a transmission control unit which controls the shifting processes of the transmission subject to the respective operating point and, if need be, subject to further parameters which specify constant and/or variable properties of a motor vehicle and its environment, wherein operating point changes of the drive unit are effected by a predefined constant or variable target value specification and shifting processes thus induced in the transmission device; that the progression of at least one output parameter is determined, in particular measured, prior to and/or during and/or subsequent the shifting process, which is characteristic of the speed behavior of the at least one transmission output element; that this progression of said output parameter is compared to a predefined, in particular ideal, output parameter progression; and that at least one parameter is determined from the deviations which is representative of said deviations.

2. The method according to claim 1 for the calculating of a characteristic value (upshift/speed value), wherein the rotational speed of the transmission input element, particularly prior to and subsequent a shifting process, is determined during an acceleration process of the vehicle, that the acceleration process starts from vehicle standstill, that the position of the gas pedal is kept constant for the acceleration process, that a first speed difference is formed from the speeds prior to shifting for at least two successive shifting processes, that a second speed difference is formed from the speeds subsequent shifting for at least two successive shifting processes, that an average speed difference is formed from these first and second speed differences, and that a characteristic value for the upshift speed behavior of the transmission device is derived from this averaged speed difference.

3. The method according to claim 1 for the calculating of a characteristic value (upshift/gear period value), wherein the vehicle performs an acceleration process, that the gas pedal position is specified as a constant for this acceleration process and selected such that at least two shifting processes are performed between speed ratios of the transmission device, that the time intervals during which the speed ratios are respectively active are determined, that the time interval of an individual speed ratio being activated is correlated to the longest interval of activated speed ratio, and that a characteristic value for the upshift gear period of the transmission device is derived therefrom.

4. The method according to claim 1 for the calculating of a characteristic value (upshift/start/speed value), wherein the gas pedal position is specified as a constant, that the transmission device executes a shifting process, that the rotational speed of the transmission input element is determined at the beginning of the shifting process, that an expected speed of the transmission input element is calculated for the end of the shifting process as a function of the gas pedal position, that the speed of the transmission input element and the gas pedal position are normalized, and that a characteristic value (upshift/start/speed value) for the speed behavior of the transmission device at the beginning of the shifting process is derived from these normalized parameters.

5. The method according to claim 1 for the calculating of a characteristic value (downshift/acceleration value), wherein the gas pedal position is specified as a constant, that the vehicle accelerates until a specific vehicle speed based on the gas pedal position, that the transmission device executes at least one shifting process during this acceleration, that the actual vehicle acceleration is determined during the acceleration process, that the actual vehicle acceleration is compared to a predefined target vehicle acceleration, that the characteristic value (downshift/acceleration value) for the ideal acceleration is derived from the degree of deviation between the target vehicle acceleration and the actual vehicle acceleration.

6. The method according to claim 1 for the calculating of a characteristic value (speed ratio/active value), wherein the gas pedal position is specified as a constant, that the gas pedal position effects a vehicle acceleration and is selected such that the transmission device executes a downshift process on the basis of the pedal position, that the time until the transmission device executes an upshift process is collected, that a characteristic value (speed ratio/active value) is derived from said collected time for the period of time a speed ratio is activated.

7. The method according to claim 1 for the calculating of a characteristic value (pre-downshift acceleration potential value), wherein a first speed for the vehicle is initially specified, which is selected such that upon this speed dropping, the transmission device immediately executes a downshift process, that the determination of the characteristic value starting from this first speed continues until a second predefinable speed is reached, that the maximum possible vehicle acceleration for the vehicle speed able to be achieved with the drive unit is determined, that same is compared to the acceleration achievable for the vehicle taking the transmission device into account, that a characteristic value (pre-downshift acceleration potential value) for the acceleration potential prior to downshift is derived from said comparison.

8. The method according to claim 1 for the calculating of a characteristic value (absolute pre-downshift acceleration potential value), wherein the first speed for the vehicle is specified, that the maximum drive power able to be drawn from the drive unit is calculated for the first speed and that an achievable vehicle acceleration is derived therefrom, that the acceleration possible at the maximum drive power of the drive unit at this first speed is calculated, that the achievable and the possible acceleration are compared, that a characteristic value (absolute pre-downshift acceleration potential value) for the absolute acceleration potential prior to downshift is derived from said comparison.

9. The method according to claim 1 for the calculating of a characteristic value (post-upshift acceleration potential value), wherein a first driving condition is specified characterized by the vehicle being at least substantially immediately subsequent an upshift process, that the determination of the characteristic value starting from this first driving condition continues until a second predefined driving condition which is characterized in particular by a higher vehicle speed is reached, that the maximum possible vehicle acceleration able to be achieved with the drive unit is determined as a function of the vehicle speed, that same is compared to the acceleration achievable for the vehicle taking the transmission device into account, that a characteristic value (post-upshift acceleration potential value) for the acceleration potential subsequent upshift is derived from said comparison.

10. The method according to claim 1 for the calculating of a characteristic value (absolute post-upshift acceleration potential value), wherein the first driving condition is specified for the vehicle, that the maximum drive power able to be drawn from the drive unit is calculated for the first driving condition and that an achievable vehicle acceleration is derived therefrom, that the acceleration possible at the maximum drive power of the drive unit at this first speed is calculated, that the achievable and the possible acceleration are compared, that a characteristic value (absolute post-upshift acceleration potential value) for the absolute acceleration potential subsequent upshift is derived from said comparison.

11. The method according to claim 1, wherein at least one total characteristic value DR .sub.p is formed from at least two characteristic values DR.sub.final or DR.sub.base for the transmission device, that the total characteristic value is calculated by summation of n individual values/characteristic values, that the individual characteristic values are exponentiated by a weighting function p, that the total characteristic value satisfies the calculation rule: ${\mathrm{DR}}_p\left({\mathrm{DR}}_1,{\mathrm{DR}}_2,\mathrm{.Math.}.Math..Math.{\mathrm{DR}}_n\right)=11-{\left(\frac{1}{n}.Math.\underset{i=1}{\overset{n}{.Math.}}.Math..Math.{\left(11-{\mathrm{DR}}_i\right)}^p\right)}^{\frac{1}{p}}$

12. The method according to claim 11, wherein a global characteristic value DR.sub.pg for the transmission device is determined from I, albeit at least two total characteristic values DR, and that the global characteristic value satisfies the calculation rule: ${\mathrm{DR}}_{\mathrm{pg}}=11-{\left(\frac{1}{{.Math.}_{k=1}^l.Math..Math.w_k}.Math.\underset{k=1}{\overset{l}{.Math.}}.Math..Math.w_k.Math.{\left(11-{\mathrm{DR}}_k\right)}^p\right)}^{\frac{1}{p}}$

13. The method according to claim 1, wherein at least one characteristic value, total characteristic value or global characteristic value is used for the optimization of the transmission device, and that transmission device parameters are varied pursuant to the differential evolution method in the calculation of this at least one characteristic value.

Description

[0207] Shown are:

[0208] FIG. 1 a diagram of the correlation between the gas pedal position and the rotational speed of the transmission input shaft or the drive shaft of the drive unit respectively,

[0209] FIG. 2 a diagram of the length of time the individual speed ratios are activated in the transmission device during an acceleration process,

[0210] FIG. 3 a diagram of the rotational speed progression during a single upshift operation,

[0211] FIG. 4 a diagram of the length of time a speed ratio remains active subsequent a downshift process until the next upshift process,

[0212] FIG. 5 a diagram of the correlation between the gas pedal position and the vehicle speed as well as the vehicle acceleration and the gas pedal position in absolute and normalized representation,

[0213] FIG. 6 a diagram of the given acceleration potential prior to downshift,

[0214] FIG. 7 a diagram of the absolute acceleration potential prior to downshift,

[0215] FIG. 8 a diagram of the given acceleration potential after upshift,

[0216] FIG. 9 a diagram of the absolute acceleration potential after upshift.

[0217] FIG. 1 depicts the rotational speed progression 14a to 14d over multiple shifting processes at different gas pedal positions (PP). The gas pedal position (PP) is kept constant during such an acceleration procedure and can be read from the first y-axis 12. The gas pedal position can be preset between 0 (idle) and 100% (full-load). The rotational speed of the transmission input shaft is represented by graphical representations 14a to 14d. Graphical representation 14a hereby represents a full-load acceleration, gas pedal position 14g, thus acceleration at a gas pedal position of 100%. Common to all the depicted graphical representations 14a to 14b is that they depict four upshift processes. The shifting operations yield a sawtooth-like profile to graphical representations 14a to 14d. Vehicle acceleration 14b is reached with gas pedal position 14h, vehicle acceleration 14c with gas pedal position 14i and vehicle acceleration 14d with gas pedal position 14j.

[0218] The input speed in the transmission device can be read from the second y-axis 13, this corresponds on the one hand to the speed of the transmission input shaft and, on the other, the speed of the drive unit's drive shaft. The acceleration processes (14a to 14d) are in each case depicted over time 1.

[0219] For determining a characteristic value, in the present case the value for the upshift/speed behavior, it is ultimately the speed prior to and subsequent the shifting process, particularly immediately before (see data points 14a1) and after (see data points 14a2) the shifting process, which is of great importance. The data points 14a1 and 14a2 are only indicated for full-load acceleration here, they are also equally provided as 14b to 14d in the graphs.

[0220] The chronological sequence of the vehicle acceleration 16 is plotted for a gas pedal position of 50% in FIG. 2a). Further depicted is the vehicle speed progression over time 17, FIG. 2b), the rotational speed of the transmission input shaft 18, FIG. 2c), and the time during which a speed ratio is activated 19, FIG. 2d). The time 15 is plotted on the x-axis for all the FIGS. 2a) to 2d).

[0221] The depicted relationship notwithstanding, any other gas pedal position would also be possible. Acceleration 16 shows that it decreases after each upshift process, explicitly indicated is the upshifting 16a from 1st into 2nd gear. When the vehicle starts from a standstill, the acceleration initially increases continuously, this is explained by the speed/torque behavior of the drive unit. The vehicle speed 17 increases through all the shifting processes and depends on the progress of the acceleration 16.

[0222] FIG. 2c) depicts the rotational speed of the transmission input shaft or drive shaft of the drive unit respectively over time. At an acceleration from standstill, the engine speed first increases continuously from the idle speed 18a. If the shifting speed 18b for upshift from 1st into 2nd gear is reached, the next speed ratio is activated. The speed initially drops with such an upshift process and then increases again, provided the vehicle continues to accelerate, until reaching the next shifting speed.

[0223] FIG. 2d) depicts for how long which speed ratio is activated. The first gear is first engaged for interval 19a, an upshift then follows into 2nd gear for interval 19b, the 3rd, 4th, 5th and 6th gears are then engaged in sequence for the time intervals 19c, 19d, 19e and 19f until the end of the acceleration process. An important characteristic value can be determined for the transmission device from these times in which the individual speed ratios are activated (19a-19f) with the cited calculation rules.

[0224] FIG. 3 juxtaposes the speed ratio at the beginning of the shifting process against a precalculated speed ratio 20. The target curve 20 depicted here as a straight line is thereby freely configurable for the precalculated speed ratio such that it can illustrate different operating modes (energy-efficient, sport, comfort or others). In other words, a progression differing from this linear progression is also conceivable, this can make sense for example when specific demands in terms of fuel consumption or sportiness need to be achieved. In the diagram shown in FIG. 3, the gas pedal position 23 is depicted over the speed of the transmission input shaft 22 or drive shaft of the drive unit respectively. The distance between the calculated rotational speed 21 of the transmission input shaft and the precalculated rotational speed 26 for a specific gas pedal position then allows determining the distance 25 between rotational speeds 21 and 26 for this specific gas pedal position 24. An important characteristic value for the evaluation of the transmission device can be derived from distance 26.

[0225] FIG. 4 provides a graphic representation which allows an evaluation of the time interval during which a specific speed ratio is active between a downshift and an upshift, in the depicted example a change from 4th into 3rd gear (and back). Predefined as boundary conditions for determining this characteristic value are the gas pedal position (constant), the start of the time measurement immediately after downshifting (from 4th into 3rd gear) and the end of the time measurement, that when upshifting is initiated (from 3rd into 4th gear). It is thereby clear that this can similarly represent all the other gear changes.

[0226] The stepped line 27 thereby marks the downshift characteristic (start of time measurement). If one assumes a gas pedal position 30 of 80%, downshift 31 is initiated at approximately 48 km/h vehicle speed.

[0227] At a continued constant gas pedal position 30 of 80%, the ensuing upshift occurs at approximately 65 km/h. How long a speed ratio is activated can be derived from this context. This then allows an important characteristic value to be derived for the evaluation of the transmission device as many drivers perceive the selected speed ratio being activated for a long time subsequent a downshift (27) in a positive light. This behavior can be understood in the sense of shifting process hysteresis.

[0228] The difficulty of optimization in this context clearly results from the fact that the individual criteria for calibrating the transmission device influence each other and are to some extent contrary.

[0229] For example, downshifting at a lower speed leads to this speed ratio (gear) being activated for a longer time until the upshift line (28) is reached, which is overall positive for this characteristic value. Likewise, however, this deferral of the downshift characteristic also leads to worsened vehicle acceleration, which is generally negative for another characteristic value.

[0230] FIG. 5a) depicts the correlation between the gas pedal position (pedal [%]) and the vehicle speed (vehicle speed [kph]) for a power train having an 8-speed automatic transmission with torque converter. Here, the pedal position represents the driver's desired driving performance; i.e. at pedal position=100%, the driver calls up the maximum available power at that moment from the drive unit, at pedal position=0%, no driving power is being requested; i.e. the vehicle is at a standstill or in coasting mode. At pedal=100%, the vehicle will continue to accelerate starting from its current driving speed until the gas pedal position is changed or terminal vehicle velocity is reached. This diagram further depicts the shift lines for the upshifting (1a-1g) of the transmission and for the downshifting (2a-2g). Shift line 1 a thereby represents the time points for the gear change from 2nd into 1st gear, shift line 1b represents the time points for the gear change from 3rd into 2nd gear, etc. Correspondingly, shift line 2a represents the time points for the gear change from 1st into 2nd gear, shift line 2b the time points for the gear change from 2nd into 3rd gear, etc. Accordingly derivable from FIG. 5a) is that the last gear, thus the 8th gear in the present case, is always engaged to the right of shift line 2f.

[0231] FIG. 5b) indicates the target value progression 4 for the vehicle acceleration, indicated as being linearly dependent on the gas pedal position (pedal [%]). The target objective 4 thereby yields a straight line. Since the drive motor has on the one hand a rotational speed-dependent variable torque and, on the other, the usable speed range of the combustion engine utilized as the drive motor is relatively small, the drive power which the drive motor is able to deliver is adapted to the driving performance requirements resulting from the driving resistances by means of a transmission device. The goal in doing so is to design and control the power train and thus also the automatic transmission such that the actual vehicle acceleration 5 coincides with the target objective 4 to the greatest extent possible or there is only a slight difference between the two. The driving speed of 50 km/h is expressed as vertical line 3 in FIG. 5a), FIGS. 5a) and 5b) are solely representations of this driving speed.

[0232] It can now be seen in FIG. 5a) that the 5th gear is engaged at driving speed 3. If the driver presses the gas pedal at this time to approximately 17%, the transmission control indicates a downshift and the automatic transmission shifts from 5th back into 4th gear, as indicated at shift point 6e. This downshifting increases the drive torque able to be delivered to the wheels of the vehicle. The rotational speed of the drive wheels initially remains unchanged and the available drive power increases abruptly. This sudden increase 6e in characteristic 5 reflects the jump in the vehicle's acceleration. Should the driver desire even greater acceleration, thus pressing the gas pedal above a gas pedal position of approximately 70%, the automatic transmission then executes a further downshift 6d, i.e. shifts back down from 4th into 3rd gear. This also results in a jump 6d in the actual vehicle acceleration. The target value setting for the acceleration 4 can thereby be briefly exceeded immediately after the shifting due to the speed/torque characteristic of the torque converter. If the driver calls for the vehicle to provide maximum or near-maximum acceleration, thus pressing the gas pedal to approximately 90% or higher, the automatic transmission then executes a further downshift 6f. Here, the 2nd gear engages in the automatic transmission instead of the 3rd gear. Here as well, the actual vehicle acceleration can briefly exceed the target acceleration.

[0233] FIG. 5c) depicts actual vehicle acceleration (FIG. 5b), 5) in normalized form 5 (value range, 0-1) over the normalized gas pedal position 4 (value range, 0-1). This depiction yields the relationship between normalized target acceleration 4 and normalized vehicle acceleration 5, as is in principle already known from FIG. 5b) for the non-normalized values. The depiction is easier to apply to further comparisons and optimizations of the transmission control and the transmission.

[0234] The shift points (6e, 6d, 6f) with their jumps are just as recognizable in the vehicle acceleration as in the non-normalized representation.

[0235] FIG. 6 depicts the correlations between acceleration 34 and vehicle speed 35 as well as the shift characteristics 33a to 33e for the evaluation of a vehicle's acceleration potential.

[0236] With this in mind, the acceleration potential is to be understood as the property of vehicle acceleration without downshifting. Many drivers find vehicle acceleration utilizing the torque of the drive unit and without transmission device downshift to be pleasing. This is generally easier to realize with high-torque drive units than with low-torque drive units.

[0237] Despite this dependence on the drive unit torque, the gradation and control of the transmission device also takes on a significant role with this vehicle property and in the determining of a characteristic value.

[0238] The acceleration potential of the vehicle is on the one hand determined by the full-load acceleration of the vehicle and, on the other, by downshift at a lower speed ratio. The full-load acceleration dictates in this context the maximum possible acceleration at 100% gas pedal position and is thus subject on one hand to the driving speed 33 and, on the other, to the activated speed ratio (1st to n-th gear). Hence, characteristic full-load acceleration curves 32a to 32e result for the full-load acceleration.

[0239] In vehicle acceleration, a general differentiation is made between kick-down acceleration and rising pedal acceleration. In kick-down acceleration, the gas pedal position is immediately engaged to a value of 100%, the transmission device thereby normally initiating at least one downshift. The drive unit's speed increases with this downshift and as a rule so does the drive power and acceleration able to be introduced into the system. Such kick-down acceleration is not under consideration at present.

[0240] In rising pedal acceleration, the gas pedal is engaged more slowly to a value of <100%, the vehicle is then accelerated without a downshift. This is the type of acceleration being taken into account for the characteristic value proposed herein.

[0241] The downshifts are indicated by the characteristic downshift curves 33a to 33e, the acceleration potentials can be derived from the correlation between the characteristic full-load acceleration curves 32a to 32e and the characteristic downshift curves 33a to 33e. By calculating the surface area between a full-load characteristic (32a to 32e) and the associated downshift characteristic (33a to 33e), it is possible to determine a characteristic value, that for the quantitative evaluation of the acceleration potential with rising pedal acceleration.

[0242] The calculation of the acceleration potential prior to downshift clearly proceeds from the lowest speed at which a specific speed ratio (straight line) is still activated. If the vehicle were thus to continue to lose speed, a downshift would then be initiated in the transmission device. Based on these speeds 36a to 36e, the acceleration potential up to the respectively associated speeds 37a to 37e is determined. The speeds 37a to 37e are in each case higher by about speed 38, here 20 km/h, than speeds 36a to 36e. The vehicle acceleration can be read from the x-axis 34 and the vehicle speed from the y-axis 33.

[0243] As in FIG. 6, the vehicle acceleration 34 is also plotted over the vehicle speed 33 in FIG. 7. A further important characteristic value for the acceleration potential prior to downshift can be determined from this representation, in this case the absolute acceleration potential.

[0244] For the evaluation of the transmission device, the acceleration potential able to be achieved by the vehicle independent of the activated speed ratio is determined for the previously determined speeds 36a to 36e. In contrast to the acceleration potential (FIG. 6) no speed range (FIG. 6, no. 38) needs to be specified for the absolute acceleration potential calculation.

[0245] The basic situations (FIG. 6, FIG. 7) are similar, the lowest speed ratio possible for a specific speed is run for the calculation; i.e. a further decrease in vehicle speed, as of these speeds (36a to 36e), would result in a transmission device downshifting.

[0246] Additionally plotted is the target function/reference function for the vehicle acceleration 39, this acceleration is independent of the activated speed ratio and can for example be derived from an analysis of pre-existing vehicles, it is thereby preferential for the acceleration potential dictated by the target function to be larger than the acceleration potential of the existing vehicles. The absolute vehicle acceleration 39 is compared to the vehicle accelerations 40a to 40e attainable at the respective speed ratios at speeds 36a to 36e.

[0247] The absolute acceleration potentials 41a to 41e are determined from this comparison and a characteristic value derived pursuant to the related calculation rules.

[0248] FIG. 8 depicts a diagram on the basis of which a further characteristic value is formed, in this case the value for the acceleration potential after an upshift. For the determination of this value, the calculation starts from a short offset 44 following an upshifting (upshift point+4 km/h) and ends at the end of the calculation period 45, wherein 20 km/h is indicated here as the calculation period.

[0249] The relevant upshift points are the result of the freely configurable characteristic upshift curves (43a to 43f). The acceleration attainable with the drive unit at a specific speed ratio is indicated by the characteristic curves 42a to 42g. In this context, meaning immediately after the upshift, 4 km/h (44) according hereto. This calculation likewise ends, as does the calculation for the acceleration potential value prior to downshift (FIG. 7), after a certain speed difference (45). In the present case, the calculation interval is 20 km/h.

[0250] FIG. 9 shows a diagram for the determination of the absolute acceleration potential subsequent to an upshift. FIG. 9 thereby corresponds substantially to FIG. 8 such that the following will largely address the differences between the figures. The upshift point 46 is on the upshift characteristic curve 43d. Additionally indicated is the target function/reference function for the vehicle acceleration 39. As set forth, this refers to accelerations which can be attained at low drive unit speeds, which is why the actual vehicle acceleration attainable at higher speeds, here 1st and 2nd gear, can be higher than this target function. The distance 47 between the reference function/target function 39 and the upshift point is a measure of the vehicle's absolute acceleration potential, particularly at low drive unit speed, and can be quantified utilizing the proposed calculation rules.

[0251] Corresponding to FIG. 7, the calculation of multiple acceleration potentials is also afforded in FIG. 9, these individual absolute acceleration potentials are not depicted in this figure in favor of greater clarity.