JP2009168151A - Determination system for parameter - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce the number of man-hours required to determine values of parameters in developing an automatic transmission. <P>SOLUTION: A data detection part 1110 of a computer 1100 detects time-series data indicating the behavior of the automatic transmission during gear change with respect to a plurality of combinations of the values of the respective parameters. An index calculation part 1120 calculates an evaluation index indicating features of the behavior of the automatic transmission based on the detected data. An analysis part 1140 analyzes an impact (contribution) of each parameter with respect to the evaluation index. A determination part 1150 gives priority to the parameter having a larger impact with respect to the evaluation index and sequentially determines (applies) the value of the parameters to satisfy conditions regarding the evaluation index. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a parameter determination system, and more particularly, to a system in which a computer automatically determines a plurality of parameters that define a shift mode of an automatic transmission.

  2. Description of the Related Art Conventionally, there is known an automatic transmission that performs a shift by changing a combination of frictional engagement elements to be engaged among frictional engagement elements such as a clutch and a brake that are operated by hydraulic pressure. In such an automatic transmission, for example, a so-called clutch-to-clutch shift may be performed in which one of the friction engagement elements is released and another friction engagement element is released. When performing clutch-to-clutch shifting, the output shaft torque of the automatic transmission is large during shifting unless the hydraulic pressure supplied to the frictional engagement element to be released and the hydraulic pressure supplied to the frictional engagement element to be engaged are controlled with high accuracy. Fluctuate and shock can occur. Further, if the output shaft torque of the drive source connected to the automatic transmission is large, a shock may occur at the time of shifting. Therefore, at the time of shifting the automatic transmission, it is necessary to control the hydraulic pressure supplied to the friction engagement element, the timing for increasing the hydraulic pressure, the torque input to the automatic transmission at the time of shifting, and the like in consideration of shock.

  Japanese Patent Laying-Open No. 2004-340287 (Patent Document 1) discloses a clutch-to-clutch shift in which one of a plurality of friction engagement devices (friction engagement elements) is released and the other is engaged to switch a gear position. Among the plurality of friction engagement devices involved in the clutch-to-clutch shift, the torque capacity T1 of the friction engagement device on the engagement side, the torque capacity T2 of the friction engagement device on the release side, and the automatic transmission Disclosed is a shift control method for an automatic transmission that sequentially calculates and controls in real time one of the torque capacities on the engagement side and the disengagement side from an equation of motion representing a balance relationship of the input torque Tin.

According to the speed change control method described in this publication, the torque capacity T1 of the engagement side frictional engagement device, the torque capacity T2 of the release side frictional engagement device, and the input torque Tin of the automatic transmission are represented in a balanced relationship. From the equation of motion, the torque capacity on either the engagement side or the release side is sequentially calculated and controlled in real time. This eliminates the need for data relating to the direct control of one torque capacity and the adaptation work. For this reason, for example, the initial value, rate of change, change timing, etc. relating to the other torque control need only be set according to the operating state. As a result, the entire data amount is reduced and troublesome fitting (adjustment) work is reduced.
JP 2004-340287 A

  However, in the speed change control method described in Japanese Patent Application Laid-Open No. 2004-340287, even if it is not necessary to determine a parameter that defines the control mode (pattern) of one friction engagement element, the other friction engagement element It is necessary to determine parameters that define the control mode. For example, it is necessary to evaluate the behavior of the automatic transmission at the time of shifting for every possible combination of parameters and find a combination of parameters that can obtain an optimum result. For this reason, in the development of an automatic transmission, it still requires a great amount of man-hours to determine the parameters that define the control mode of the friction engagement elements.

  The present invention has been made to solve the above-described problems, and provides a parameter determination system that can reduce the man-hours required to determine parameter values in the development of an automatic transmission. It is.

  A parameter determination system according to a first aspect of the present invention is a plurality of parameter determination system that defines a shift mode of an automatic transmission. The determination system includes a detecting means for detecting data indicating the behavior of the automatic transmission for a plurality of combinations of the values of the respective parameters, and characterizing the behavior of the automatic transmission based on the detected data. The calculation means for calculating the indicator to be indicated, the analysis means for analyzing the influence of each parameter on the indicator, and the parameter having a larger influence on the indicator are given priority so as to satisfy a predetermined condition regarding the indicator And determining means for determining parameter values in order.

  According to this configuration, data indicating the behavior of the automatic transmission when shifting is detected for a plurality of combinations of parameter values. Based on the detected data, an index indicating the characteristics of the behavior of the automatic transmission is calculated. Furthermore, the influence of each parameter on the index is analyzed. The parameter value is determined in order so that a parameter having a greater influence on the index is prioritized and a predetermined condition regarding the index is satisfied. Thereby, it is possible to find a combination of parameter values that can provide good results without trying all possible combinations of parameter values. Therefore, it is possible to provide a parameter determination system that can reduce the man-hours required to determine parameter values in the development of an automatic transmission.

  In addition to the configuration of the first invention, the parameter determination system according to the second invention further includes means for generating an approximate function representing the relationship between the value of each parameter and the index. The analysis means includes means for analyzing the influence of each parameter on the index based on the approximate function.

  According to this configuration, an approximate function representing the relationship between the value of each parameter and the index is generated. Thereby, data can be interpolated with respect to a combination of parameter values for which data indicating the behavior of the automatic transmission at the time of shifting is not detected. Based on the generated approximate function, the influence of each parameter on the index is analyzed. This can reduce the number of parameter value combinations tested to analyze the impact of each parameter on the index. Therefore, in the development of the automatic transmission, the man-hours required for determining the parameter value can be reduced.

  In the parameter determination system according to the third invention, in addition to the configuration of the second invention, the analysis means calculates the influence of each parameter on the index based on the result of partial differentiation of the approximate function for each of a plurality of parameters. Have means for analysis.

  According to this configuration, the influence of each parameter on the index can be analyzed by partially differentiating the approximate function for each of a plurality of parameters.

  In the parameter determination system according to the fourth invention, in addition to the configuration of the second or third invention, the determination means determines a parameter value having a greater influence on the index from the values obtained by the approximate function. And means for determining a value of a parameter having a smaller influence on the index from values obtained by the approximation function.

  According to this configuration, the value of the parameter having a greater influence on the index is determined from the values obtained by the approximate function. Thereafter, a parameter value having a smaller influence on the index is determined from values obtained by the approximation function. Thereby, the value of a parameter can be determined efficiently.

  The determining means preferably determines the value of the parameter having a large influence from the values obtained by the approximate function, and then performs an additional test to improve the accuracy of the approximate function near the determined value (optimum value). Thereafter, it is preferable to determine a parameter value having a smaller influence on the index.

  In the parameter determination system according to the fifth invention, in addition to the configuration of any one of the first to fourth inventions, the automatic transmission releases the first friction engagement element that operates by hydraulic pressure, and also uses hydraulic pressure. Shifting is performed by engaging the second frictional engagement element that operates. A power source is connected to the input shaft of the automatic transmission. The parameters are: the hydraulic pressure supplied to the first friction engagement element during the shift, the hydraulic pressure supplied to the second friction engagement element during the shift, and the hydraulic pressure supplied to the second friction engagement element during the shift. Is at least one of the timing to increase the output shaft torque and the reduction amount of the output shaft torque of the power source during the shift.

  According to this configuration, the first frictional engagement element that is operated by hydraulic pressure is released, the second frictional engagement element that is operated by hydraulic pressure is engaged, and the power source is connected to the input shaft. In the development of the automatic transmission, it is possible to reduce the man-hours required for determining the hydraulic pressure supplied to the friction engagement element, the timing for increasing the hydraulic pressure, and the amount of reduction in the output shaft torque of the power source.

  In the parameter determination system according to the sixth invention, in addition to the configuration of any one of the first to fifth inventions, the indicator is at least one of a time required for shifting and a degree of fluctuation of the output shaft torque of the automatic transmission. One of them.

  According to this configuration, the time required for shifting and the degree to which the output shaft torque of the automatic transmission fluctuates are used as indices indicating the characteristics of the behavior of the automatic transmission. The value of the parameter is determined so as to satisfy a predetermined condition regarding the index. Thereby, for example, it is possible to determine parameter values that optimize the balance between the time required for shifting and the degree to which the output shaft torque of the automatic transmission varies.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following description, the same parts are denoted by the same reference numerals. Their names and functions are also the same. Therefore, detailed description thereof will not be repeated.

  With reference to FIG. 1, the automatic adaptation system 1000 of this Embodiment is demonstrated. The automatic adaptation system 1000 is a system that supports the development of the automatic transmission 2000. The automatic adaptation system 1000 includes a computer 1100, a display 1200, a printer 1300, an input device 1400, and a bench test machine 1500. Note that the configuration of the automatic adaptation system 1000 is not limited to these.

  The computer 1100 is connected to a display 1200, a printer 1300, an input device 1400, and a bench test machine 1500. The computer 1100 executes calculations by executing a program stored in the memory 1102 in a CPU (Central Processing Unit) 1104, and automatically determines (adapts) various parameter values used for controlling the automatic transmission 2000. To do. Note that a program executed by the computer 1100 may be recorded on a recording medium such as a CD (Compact Disc) or a DVD (Digital Versatile Disc) and distributed to the market. The memory 1102 is a general-purpose memory such as a ROM (Read Only Memory).

  The calculation result of the computer 1100 is output to the display 1200 and the printer 1300. You may make it record the calculation result of the computer 1100 on recording media, such as CD and DVD. The user operates the computer 1100 using the input device 1400. The input device 1400 is, for example, a keyboard and a mouse.

  The bench test machine 1500 performs an operation test of the automatic transmission 2000 under predetermined conditions in a state where the automatic transmission 2000 is mounted. The test conditions of the automatic transmission 2000 are input to the bench tester 1500 via the computer 1100 or directly input to the bench tester 1500, for example. Note that a well-known general testing machine may be used as the bench testing machine 1500, and thus detailed description thereof will not be repeated here.

  Data obtained as a result of testing the automatic transmission 2000 by the bench tester 1500 is input to the computer 1100 and stored in the memory 1106. The memory 1106 is a general-purpose memory such as a RAM (Random Access Memory).

  Automatic transmission 2000 is an automatic transmission for a vehicle. When automatic transmission 2000 is mounted on a vehicle, the input shaft of automatic transmission 2000 is connected to a power source such as an engine (not shown) via a torque converter (not shown). A motor may be used as a power source.

  The input shaft rotational speed NI (turbine rotational speed NT of the torque converter) of the automatic transmission 2000 is detected by the input shaft rotational speed sensor 2002 and input to the computer 1100. The output shaft rotational speed NO of automatic transmission 2000 is detected by output shaft rotational speed sensor 2004 and input to computer 1100. The output shaft torque TO of the automatic transmission 2000 is detected by the torque sensor 2006 and input to the computer 1100. The output shaft torque TO may be calculated based on the output shaft rotational speed NO.

  Automatic transmission 2000 includes a planetary gear unit 3000 and a hydraulic circuit 4000. In the present embodiment, automatic transmission 2000 can form 1st to 6th forward gears. It should be noted that a higher gear than the sixth gear, that is, a seventh gear or an eighth gear may be formed.

  The planetary gear unit 3000 will be described with reference to FIG. Planetary gear unit 3000 includes a first set 3300 of planetary gear mechanisms, a second set 3400 of planetary gear mechanisms, an output gear 3500, a B1 brake 3610, a B2 brake 3620 and a B3 brake 3630 fixed to gear case 3600, and C1. Clutch 3640 and C2 clutch 3650, and one-way clutch F3660 are included.

  The first set 3300 is a single pinion type planetary gear mechanism. First set 3300 includes sun gear S (UD) 3310, pinion gear 3320, ring gear R (UD) 3330, and carrier C (UD) 3340.

  Sun gear S (UD) 3310 is coupled to input shaft 3210 of automatic transmission 2000. Pinion gear 3320 is rotatably supported by carrier C (UD) 3340. Pinion gear 3320 is in mesh with sun gear S (UD) 3310 and ring gear R (UD) 3330.

  Ring gear R (UD) 3330 is fixed to gear case 3600 by B3 brake 3630. Carrier C (UD) 3340 is fixed to gear case 3600 by B1 brake 3610.

  The second set 3400 is a Ravigneaux type planetary gear mechanism. The second set 3400 includes a sun gear S (D) 3410, a short pinion gear 3420, a carrier C (1) 3422, a long pinion gear 3430, a carrier C (2) 3432, a sun gear S (S) 3440, and a ring gear R. (1) (R (2)) 3450.

  Sun gear S (D) 3410 is coupled to carrier C (UD) 3340. Short pinion gear 3420 is rotatably supported by carrier C (1) 3422. Short pinion gear 3420 is in mesh with sun gear S (D) 3410 and long pinion gear 3430. Carrier C (1) 3422 is coupled to output gear 3500.

  Long pinion gear 3430 is rotatably supported by carrier C (2) 3432. Long pinion gear 3430 is in mesh with short pinion gear 3420, sun gear S (S) 3440, and ring gear R (1) (R (2)) 3450. Carrier C (2) 3432 is coupled to output gear 3500.

  Sun gear S (S) 3440 is coupled to input shaft 3210 by C1 clutch 3640. Ring gear R (1) (R (2)) 3450 is fixed to gear case 3600 by B2 brake 3620 and connected to input shaft 3210 by C2 clutch 3650. The ring gear R (1) (R (2)) 3450 is connected to the one-way clutch F3660, and cannot rotate when the first gear is driven.

  The one-way clutch F3660 is provided in parallel with the B2 brake 3620. That is, the outer race of the one-way clutch F3660 is fixed to the gear case 3600, and the inner race is connected to the ring gear R (1) (R (2)) 3450 via the rotation shaft.

  FIG. 3 shows an operation table showing the relationship between each gear stage and the operating states of the clutches and brakes which are friction engagement elements. By operating each brake and each clutch with the combinations shown in this operation table, a forward gear stage of 1st to 6th speed and a reverse gear stage are formed.

  The main part of the hydraulic circuit 4000 will be described with reference to FIG. The hydraulic circuit 4000 is not limited to the one described below.

  The hydraulic circuit 4000 includes an oil pump 4004, a primary regulator valve 4006, a manual valve 4100, a solenoid modulator valve 4200, an SL1 linear solenoid valve (hereinafter referred to as SL (1)) 4210, an SL2 linear solenoid valve ( SL220 (hereinafter referred to as SL (2)) 4220, SL3 linear solenoid valve (hereinafter referred to as SL (3)) 4230, SL4 linear solenoid valve (hereinafter referred to as SL (4)) 4240, SLT A linear solenoid valve (hereinafter referred to as SLT) 4300 and a B2 control valve 4500 are included.

  Oil pump 4004 is connected to the output shaft of the power source. As the output shaft of the power source rotates, the oil pump 4004 is driven to generate hydraulic pressure. The hydraulic pressure generated by the oil pump 4004 is regulated by the primary regulator valve 4006 to generate a line pressure.

  Primary regulator valve 4006 operates using the throttle pressure regulated by SLT 4300 as a pilot pressure. The line pressure is supplied to the manual valve 4100 via the line pressure oil passage 4010.

  Manual valve 4100 includes a drain port 4105. From the drain port 4105, the oil pressure in the D range pressure oil passage 4102 and the R range pressure oil passage 4104 is discharged. When the spool of the manual valve 4100 is in the D (drive) position, the line pressure oil passage 4010 and the D range pressure oil passage 4102 are communicated, and the oil pressure is supplied to the D range pressure oil passage 4102. At this time, the R range pressure oil passage 4104 and the drain port 4105 are communicated, and the R range pressure of the R range pressure oil passage 4104 is discharged from the drain port 4105.

  When the spool of the manual valve 4100 is in the R (reverse) position, the line pressure oil passage 4010 and the R range pressure oil passage 4104 are communicated, and the oil pressure is supplied to the R range pressure oil passage 4104. At this time, the D range pressure oil passage 4102 and the drain port 4105 are communicated, and the D range pressure in the D range pressure oil passage 4102 is discharged from the drain port 4105.

  When the spool of the manual valve 4100 is in the N (neutral) position, both the D range pressure oil passage 4102 and the R range pressure oil passage 4104 are connected to the drain port 4105, and the D range pressure oil passage 4102 has a D range. The pressure and the R range pressure of the R range pressure oil passage 4104 are discharged from the drain port 4105.

  The hydraulic pressure supplied to the D range pressure oil passage 4102 is finally supplied to the B1 brake 3610, the B2 brake 3620, the C1 clutch 3640, and the C2 clutch 3650. The hydraulic pressure supplied to the R range pressure oil passage 4104 is finally supplied to the B2 brake 3620.

  The solenoid modulator valve 4200 adjusts the hydraulic pressure (solenoid modulator pressure) supplied to the SLT 4300 to a constant pressure using the line pressure as the original pressure.

  SL (1) 4210 regulates the hydraulic pressure supplied to the C1 clutch 3640. SL (2) 4220 regulates the hydraulic pressure supplied to C2 clutch 3650. SL (3) 4230 regulates the hydraulic pressure supplied to the B1 brake 3610. SL (4) 4240 regulates the hydraulic pressure supplied to the B3 brake 3630.

  The SLT 4300 regulates the solenoid modulator pressure and generates a throttle pressure. The throttle pressure is supplied to the primary regulator valve 4006 via the SLT oil passage 4302. The throttle pressure is used as a pilot pressure for the primary regulator valve 4006.

  The B2 control valve 4500 selectively supplies hydraulic pressure from one of the D range pressure oil passage 4102 and the R range pressure oil passage 4104 to the B2 brake 3620. A D range pressure oil passage 4102 and an R range pressure oil passage 4104 are connected to the B2 control valve 4500. The B2 control valve 4500 is controlled by the hydraulic pressure supplied from the SL solenoid valve (not shown) and the SLU solenoid valve (not shown) and the biasing force of the spring.

  When the SL solenoid valve is off and the SLU solenoid valve is on, the B2 control valve 4500 is in the state on the left side in FIG. In this case, the B2 brake 3620 is supplied with the hydraulic pressure adjusted from the D range pressure using the hydraulic pressure supplied from the SLU solenoid valve as a pilot pressure.

  When the SL solenoid valve is on and the SLU solenoid valve is off, the B2 control valve 4500 is in the state on the right side in FIG. In this case, the R range pressure is supplied to the B2 brake 3620.

  With reference to FIG. 5, an example of a shift mode (shift pattern) of automatic transmission 2000 will be described. In the following description, a form of upshift in which one of the friction engagement elements is released and another friction engagement element is engaged will be described.

  When the upshift is started at time T1, the target hydraulic pressure of the friction engagement element released by the shift is once reduced. Thereafter, the target hydraulic pressure gradually decreases at time T2, and the target hydraulic pressure is reduced to the release hydraulic pressure P1 at time T3. Thereafter, the target hydraulic pressure is gradually reduced until it reaches zero.

  The target hydraulic pressure of the friction engagement element engaged by the speed change is once increased when the upshift is started at time T1. Thereafter, a gradual increase (sweep up) of the target hydraulic pressure is started at time T4, and the target hydraulic pressure increases to the engagement hydraulic pressure P2 at time T5. The time between time T4 and time T5 is defined as engagement time ΔT. That is, the target hydraulic pressure is gradually increased at an increase rate calculated by dividing the difference between the hydraulic pressure before the gradual increase and the engagement hydraulic pressure P2 by the engagement time ΔT. Therefore, the engagement time ΔT indicates the timing at which the target hydraulic pressure is increased to the engagement hydraulic pressure P2. After the hydraulic pressure increases to the engagement hydraulic pressure P2, the hydraulic pressure is increased as the upshift progresses. Ultimately, the hydraulic pressure is increased to a value at which the frictional engagement element is fully engaged.

  During the upshift, in addition to the hydraulic pressure supplied to the friction engagement element, the output shaft torque TE of the power source, that is, the input shaft torque of the automatic transmission 2000 is controlled. In order to reduce the shock at the time of shifting, the output shaft torque TE of the power source connected to the input shaft 3210 of the automatic transmission 2000 is reduced by the torque down amount ΔTE. When an internal combustion engine is used as a power source, for example, the output shaft torque TE is reduced by retarding the ignition timing.

  In the present embodiment, the release hydraulic pressure P1, the engagement hydraulic pressure P2, the engagement time ΔT, and the torque down amount ΔTE are used as parameters that define the mode of shift. The values of the release hydraulic pressure P1, the engagement hydraulic pressure P2, the engagement time ΔT, and the torque down amount ΔTE are automatically determined (adapted) by the computer 1100. Note that values of parameters other than the release hydraulic pressure P1, the engagement hydraulic pressure P2, the engagement time ΔT, and the torque down amount ΔTE may be determined.

  The functions of the computer 1100 will be described with reference to FIG. Note that the functions of the computer 1100 described below may be realized by software or hardware.

  The computer 1100 includes a data detection unit 1110, an index calculation unit 1120, a generation unit 1130, an analysis unit 1140, and a determination unit 1150.

  The data detection unit 1110 displays time series data indicating the behavior of the automatic transmission 2000 when the gear is shifted according to a predetermined release hydraulic pressure P1, engagement hydraulic pressure P2, engagement time ΔT, and torque down amount ΔTE. Detection is performed for a plurality of combinations of values of the combined hydraulic pressure P2, the engagement time ΔT, and the torque down amount ΔTE. In the present embodiment, as an example, input shaft rotational speed NI, output shaft rotational speed NO, and output shaft torque TO of automatic transmission 2000 before and after the shift and during the shift are detected. The detected data is not limited to these.

  A combination of values of the release hydraulic pressure P1, the engagement hydraulic pressure P2, the engagement time ΔT, and the torque down amount ΔTE used to detect time-series data indicating the behavior of the automatic transmission 2000 is previously input to the computer 1100 by the user. . For example, the number of combinations necessary for generating an approximate function (response surface) described later is input.

  The index calculation unit 1120 calculates an evaluation index indicating the characteristics of the behavior of the automatic transmission 2000 based on the detected data. In the present embodiment, as an example, a time required for shifting and a shift shock quantitative value are calculated as evaluation indexes.

  The time required for the shift is calculated, for example, as the time from the start of the shift until the input shaft rotational speed NI is synchronized with the synchronized rotational speed after the shift. The synchronous rotation speed is calculated as a product of the gear ratio and the output shaft rotation speed NO. In addition, since the method for calculating the time required for shifting may be a known general technique, further detailed description will not be repeated here.

  The shift shock quantitative value is calculated as a value indicating the degree to which output shaft torque TO of automatic transmission 2000 varies. As shown in FIG. 7, the shift shock quantitative value is calculated using, for example, the following equation 1 when the reduction amounts of the output shaft torque TO during the shift are A and B.

Shifting shock quantitative value = (A + B) / output shaft torque TO (1)
A larger shift shock quantitative value indicates a greater shift shock. The method for calculating the shift shock quantitative value is not limited to this. The amount of decrease in the output shaft torque TO during the shift may be used as it is as an evaluation index. In the present embodiment, the computer 1100 automatically detects a portion where the output shaft torque TO decreases from the time series data of the output shaft torque TO, and calculates a decrease amount of the output shaft torque TO. In addition, the amount by which the input shaft rotational speed NI is larger than the synchronous rotational speed, the heat absorption amount of the friction engagement element, and the like may be calculated as evaluation indexes.

  FIG. 8 shows an example of the time required for the shift and the shift shock quantitative value obtained for a plurality of combinations of the values of the release hydraulic pressure P1, the engagement hydraulic pressure P2, the engagement time ΔT, and the torque down amount ΔTE.

  FIG. 8 shows that among the release oil pressure P1, the engagement time ΔT, and the torque down amount ΔTE when the engagement oil pressure P2 is any one of α, β, γ, and σ (α> β> γ> σ). The time required for the shift and the shift shock quantitative value obtained as a result of changing only one of the parameters in order are shown.

  In the example shown in FIG. 8, the greater the engagement hydraulic pressure P <b> 2, the shorter the time required for shifting and the greater the shift shock quantitative value. The smaller the release hydraulic pressure P1, the shorter the time required for shifting, and the greater the shift shock quantitative value. Further, the contribution to the tendency of the release hydraulic pressure P1 is the engagement that changes depending on the magnitude of the engagement hydraulic pressure P2. The shorter the engagement time ΔT, the shorter the time required for the shift and the greater the shift shock quantitative value. As the torque down amount ΔTE is smaller, the time required for the shift tends to be longer and the shift shock quantitative value tends to be larger.

  The generation unit 1130 generates an approximate function (response surface) that represents the relationship between the value of each parameter and each evaluation index. For example, an approximate function of a quadratic polynomial is generated. The approximate function is not limited to a quadratic polynomial. In addition, about the method itself which produces | generates an approximate function, since what is necessary is just to use a known general technique, the detailed description is not repeated here.

  The analysis unit 1140 analyzes the influence (contribution) of each parameter on the evaluation index. The influence of each parameter is analyzed by comparing the product of the partial differentiation of the approximate function for each variable representing the value of the parameter and the width of the value that each parameter can take.

  For example, when the release hydraulic pressure P1, the engagement hydraulic pressure P2, the engagement time ΔT, and the torque down amount ΔTE are expressed as variables A, B, C, and D, respectively, the partial differentiation of the approximate function by the variable A and the variable A can be taken. The product of the width of the value, the product of the partial differentiation of the approximate function by the variable B and the value width of the variable B, the product of the partial differentiation of the approximate function by the variable C and the width of the value of the variable C, the variable The product of the partial differential of the approximate function by D and the width of the value that the variable D can take is compared. The greater the product of the partial differential and the range of values that the parameter can take, the greater the influence. The range of values that variables A, B, C and D take in is determined by the developer of automatic transmission 2000. Note that the method of analyzing influence is not limited to this.

  The determination unit 1150 determines (adapts) the parameter values in order so that the parameter having a greater influence on the evaluation index is prioritized and the condition regarding the evaluation index is satisfied. As shown in FIG. 9, the optimum value of each parameter is determined (searched) using an approximate function so that the evaluation index becomes a value within a region surrounded by a one-dot chain line. The determined optimum value is determined as the value of the parameter. In FIG. 9, a region surrounded by an alternate long and short dash line is a region where the evaluation index can be considered good.

  After first determining the value of the parameter having the greatest influence, the value of the parameter having the next largest influence is determined in a state where the determined parameter is fixed. Thereafter, in the same manner, values are determined in the order of parameters having the greatest influence.

  For example, it is assumed that the influence is large in the order of the engagement hydraulic pressure P2, the release hydraulic pressure P1, the engagement time ΔT, and the torque down amount ΔTE. In this case, the values are determined in the order of the engagement hydraulic pressure P2, the release hydraulic pressure P1, the engagement time ΔT, and the torque down amount ΔTE. When the influence is equal, the optimum values of a plurality of parameters may be determined at the same time.

  With reference to FIG. 10, a control structure of a program executed by CPU 1104 of computer 1100 will be described.

  In step (hereinafter, step is abbreviated as S) 100, CPU 1104 performs automatic transmission when shifting according to a predetermined combination of release hydraulic pressure P1, engagement hydraulic pressure P2, engagement time ΔT, and torque down amount ΔTE. Time-series data indicating 2000 behavior is detected.

  In S102, CPU 1104 calculates an evaluation index based on the detected data. That is, the time required for shifting and the shift shock quantitative value are calculated. In S104, CPU 1104 generates an approximate function.

  In S106, CPU 1104 analyzes the influence of each parameter on the evaluation index. That is, the influence of the release hydraulic pressure P1, the engagement hydraulic pressure P2, the engagement time ΔT, and the torque down amount ΔTE on the time required for the shift and the shift shock quantitative value is analyzed.

  In S108, CPU 1104 determines the optimum value of the parameter having the greatest influence among the parameters whose values have not been determined. In S110, CPU 1104 determines the optimum value as the parameter value.

  In S112, CPU 1104 determines whether or not all parameter values have been determined. If all parameter values have been determined (YES in S112), this process ends. If not (NO in S112), the process returns to S100.

  An operation of computer 1100 in the present embodiment based on the above structure and flowchart will be described.

  Time-series data indicating the behavior of automatic transmission 2000 when a shift is made according to a predetermined combination of values of release hydraulic pressure P1, engagement hydraulic pressure P2, engagement time ΔT and torque down amount ΔTE is detected (S100). Based on the detected data, an evaluation index, that is, a time required for shifting and a shift shock quantitative value are calculated (S102). Further, an approximate function is generated (S104). Based on the generated approximate function, the influence of each parameter on the evaluation index is analyzed (S106). That is, the influence of the release hydraulic pressure P1, the engagement hydraulic pressure P2, the engagement time ΔT, and the torque down amount ΔTE on the time required for the shift and the shift shock quantitative value is analyzed.

  Hereinafter, it is assumed that the influence on the time required for the shift and the shift shock quantitative value is large in the order of the engagement hydraulic pressure P2, the release hydraulic pressure P1, the engagement time ΔT, and the torque down amount ΔTE.

  In this case, the optimum value of the engagement hydraulic pressure P2 is first determined so that the time required for the shift and the shift shock quantitative value become values in a region considered good (S108). The determined optimum value is determined as the value of the engagement hydraulic pressure P2 (S110).

  Since the values of release hydraulic pressure P1, engagement time ΔT and torque-down amount ΔTE have not been determined (NO in S112), the engagement hydraulic pressure P2 is fixed to the optimum value, and an additional test is performed to perform automatic transmission. Time-series data indicating 2000 behavior is detected (S100). An evaluation index is calculated based on the detected data (S102). Further, an approximate function is generated (S104). This improves the accuracy of the approximate function near the optimum value.

  Next, the optimum value of the release hydraulic pressure P1 is determined (S108). The determined optimum value is determined as the value of the release hydraulic pressure P1 (S110).

  Since the values of engagement time ΔT and torque down amount ΔTE have not been determined (NO in S112), the engagement hydraulic pressure P2 and the release hydraulic pressure P1 are fixed to optimum values, and an additional test is performed, so that the automatic transmission Time-series data indicating 2000 behavior is detected (S100). An evaluation index is calculated based on the detected data (S102). Further, an approximate function is generated (S104).

  Next, the optimum value of the engagement time ΔT is determined (S108). The determined optimum value is determined as the value of the engagement time ΔT (S110).

  Since the value of torque reduction amount ΔTE has not been determined (NO in S112), the engagement hydraulic pressure P2, the release hydraulic pressure P1 and the engagement time ΔT are fixed to the optimum values, and an additional test is performed, so that the automatic transmission Time-series data indicating 2000 behavior is detected (S100). An evaluation index is calculated based on the detected data (S102). Further, an approximate function is generated (S104).

  The optimum value of the torque down amount ΔTE is finally determined (S108). The determined optimum value is determined as the value of the torque down amount ΔTE (S110).

  As described above, according to the parameter determination system according to the present embodiment, data indicating the behavior of the automatic transmission at the time of shifting is detected for a plurality of combinations of the values of each parameter. Based on the detected data, an evaluation index indicating the characteristics of the behavior of the automatic transmission is calculated. Further, the influence of each parameter on the evaluation index is analyzed. The parameter value is determined in order so that a parameter having a greater influence on the evaluation index is prioritized and a predetermined condition regarding the evaluation index is satisfied. Thereby, it is possible to find a combination of parameter values that can provide good results without trying all possible combinations of parameter values. For this reason, it is possible to reduce the man-hours required for determining the parameters in the development of the automatic transmission.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

It is a schematic block diagram which shows the automatic adaptation system of an automatic transmission. It is a figure which shows the planetary gear unit of an automatic transmission. It is a figure which shows the operation | movement table | surface of an automatic transmission. It is a figure which shows the hydraulic circuit of an automatic transmission. It is a timing chart which shows the speed change form of an automatic transmission. It is a functional block diagram of a computer. It is a figure which shows the output shaft torque TO of an automatic transmission. It is a figure which shows the time which shift requires, and a shift shock fixed value. It is a figure which shows the area | region which can be considered that the time required for the shift which is an evaluation parameter | index, and the shift shock quantitative value are favorable. It is a flowchart which shows the control structure of the program which CPU of a computer performs.

Explanation of symbols

  1000 automatic adaptation system, 1100 computer, 1102, 1106 memory, 1104 CPU, 1110 data detection unit, 1120 index calculation unit, 1130 generation unit, 1140 analysis unit, 1150 determination unit, 1200 display, 1300 printer, 1400 input device, 1500 bench Test machine, 2000 Automatic transmission, 2002 Input shaft speed sensor, 2004 Output shaft speed sensor, 2006 Torque sensor, 3200 Torque converter, 3610 B1 brake, 3620 B2 brake, 3630 B3 brake, 3640 C1 clutch, 3650 C2 clutch, 4000 Hydraulic circuit, 4210 SL1 linear solenoid valve, 4220 SL2 linear solenoid valve, 4230 SL3 linear Renoidobarubu, 4240 SL4 linear solenoid valve.

Claims (6)

A system for determining a plurality of parameters defining a shift mode of an automatic transmission,
Detecting means for detecting data indicating the behavior of the automatic transmission when shifting, for a plurality of combinations of the values of the parameters;
Calculation means for calculating an index indicating characteristics of the behavior of the automatic transmission based on the detected data;
Analyzing means for analyzing the influence of each of the parameters on the indicator;
A parameter determination system comprising: a determination unit that prioritizes a parameter having a greater influence on the index and sequentially determines a value of the parameter so as to satisfy a predetermined condition regarding the index. Means for generating an approximate function representing the relationship between the value of each parameter and the indicator;
The parameter determination system according to claim 1, wherein the analysis means includes means for analyzing the influence of each parameter on the index based on the approximate function.   3. The parameter determination according to claim 2, wherein the analysis unit includes a unit configured to analyze an influence of each parameter on the index based on a result of partial differentiation of the approximate function for each of the plurality of parameters. system.   The determining means determines a parameter value having a greater influence on the index from values obtained by the approximation function, and then obtaining a parameter value having a smaller influence on the index by the approximation function. 4. The parameter determination system according to claim 2 or 3, comprising means for determining from among. The automatic transmission releases a first friction engagement element that is operated by hydraulic pressure, and shifts by engaging a second friction engagement element that is operated by hydraulic pressure, and is applied to an input shaft of the automatic transmission. Is connected to the power source,
The parameters include the hydraulic pressure supplied to the first friction engagement element during a shift, the hydraulic pressure supplied to the second friction engagement element during a shift, and the second friction engagement element during a shift. 5. The parameter determination system according to claim 1, wherein the parameter determination system is at least one of a timing of increasing the supplied hydraulic pressure and a reduction amount of the output shaft torque of the power source during a shift.   The parameter determination system according to any one of claims 1 to 5, wherein the index is at least one of a time required for a shift and a degree of fluctuation of an output shaft torque of the automatic transmission.

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