JP2006125435A - Hydraulic control device for automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic control device for actualizing accurate hydraulic control of an automatic transmission. <P>SOLUTION: In a memory of an ECU, actual output hydraulic pressure A(0)-E(4) to command pressure A(0)-E(0) for output hydraulic pressure of a hydraulic control linear solenoid is stored as specified values for the output hydraulic pressure (values for the property). These specified values are stored corresponding to original hydraulic pressure P(1)-P(4) and command pressure A(0)-E(0) for the output hydraulic pressure. The ECU corrects the command pressure for the output hydraulic pressure in accordance with the specified values stored in the memory to control the linear solenoid so that the actual output hydraulic pressure is desired output hydraulic pressure. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a hydraulic control device for an automatic transmission, and more particularly to an automatic transmission that stores a characteristic value of an output hydraulic pressure of a pressure adjusting unit that adjusts the hydraulic pressure and controls the pressure adjusting unit based on the stored characteristic value. The present invention relates to a hydraulic control device.

  In an automatic transmission, the line pressure is regulated by a linear solenoid or the like and supplied to a hydraulic servo of a clutch or brake constituting the automatic transmission to control the automatic transmission. However, since linear solenoids and the like have individual differences, it is necessary to control the hydraulic pressure in consideration of these individual differences.

  Japanese Patent Application Laid-Open No. 5-215206 (Patent Document 1) discloses an electronically controlled automatic transmission that prevents the transmission performance of the automatic transmission from varying due to variations in the components of the automatic transmission main body and the control device of the automatic transmission. The machine is disclosed. The electronically controlled automatic transmission described in Patent Document 1 is attached to an automatic transmission electronic control device provided at a predetermined position on a vehicle away from the automatic transmission main body and the automatic transmission main body. Includes property storage. The characteristic storage device includes a storage unit that stores unique characteristics such as a control device and a control component provided in the automatic transmission main body. The characteristic storage device and the electronic control device are electrically connected by wiring.

According to the electronically controlled automatic transmission described in this publication, the characteristics of the control device and control components that affect the shift control of the automatic transmission are input and stored in the characteristic storage device for each automatic transmission. Yes. The electronic control device reads the storage signal stored in the characteristic storage device and corrects the control content accordingly. For example, when an oil temperature sensor that outputs a voltage larger than a reference value corresponding to a predetermined oil temperature is used, this is stored in the characteristic storage device. In the electronic control device, the oil temperature sensor Correction is performed so that actual shift control is performed using a value obtained by subtracting a predetermined value from the output of. In this way, since the characteristic that affects the speed change performance is corrected, the variation in speed change performance among the automatic transmissions can be extremely reduced.
JP-A-5-215206

  By the way, the output hydraulic pressure of a component that regulates hydraulic pressure, such as a linear solenoid, has characteristics according to the supplied hydraulic oil. However, the electronically controlled automatic transmission described in Japanese Patent Application Laid-Open No. 5-215206 does not consider anything about the characteristics of the hydraulic oil supplied to the linear solenoid. Therefore, there is a problem that there is room for further improvement in order to improve the accuracy of output hydraulic pressure such as a linear solenoid.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a hydraulic control device for an automatic transmission that can accurately adjust the hydraulic pressure.

  A hydraulic control device for an automatic transmission according to a first aspect of the invention controls the hydraulic pressure of an automatic transmission that includes a pressure adjusting unit that adjusts the hydraulic pressure of hydraulic oil. This hydraulic control device supports the values related to the characteristics of the output hydraulic pressure with respect to the hydraulic oil supplied to the pressure adjusting section under a plurality of conditions where the output hydraulic pressure of the pressure adjusting section is different. Storage means for storing the data, and control means for controlling the pressure adjusting unit based on the value related to the characteristics.

  According to the first invention, under a plurality of conditions in which the output hydraulic pressure of the pressure adjusting unit is different, the value related to the characteristic of the output hydraulic pressure with respect to the hydraulic oil supplied to the pressure adjusting unit is the value related to the state of the hydraulic oil and Correspondingly stored. Thereby, for example, the difference between the command pressure of the output hydraulic pressure and the actual output hydraulic pressure is stored as a value relating to the characteristic corresponding to the original hydraulic pressure and the oil temperature. Based on the value relating to this characteristic, the pressure adjusting unit is controlled so that the actual output oil pressure becomes a desired output oil pressure. Therefore, the accuracy of the output hydraulic pressure can be improved. As a result, it is possible to provide a hydraulic control device for an automatic transmission capable of accurately adjusting the hydraulic pressure.

  In the hydraulic control device for an automatic transmission according to the second invention, in addition to the configuration of the first invention, the storage means relates to characteristics obtained by actually measuring the output hydraulic pressure with different values relating to the state. Means are included for storing values in association with values for each state and output hydraulic pressures.

  According to the second invention, for each output hydraulic pressure, a value relating to a characteristic measured by varying a value relating to the state is stored. As a result, the output hydraulic pressure can be controlled with high accuracy using the actually measured value relating to the characteristic with high accuracy.

  In the hydraulic control device for an automatic transmission according to the third invention, in addition to the configuration of the first invention, the storage means measures the output hydraulic pressure when the value relating to the state becomes a predetermined value. Means for storing the value relating to the characteristic obtained by the above in correspondence with a predetermined value and each output hydraulic pressure. The hydraulic control device further includes means for calculating a value related to the characteristic when the value related to the state is different from a predetermined value based on the value related to the characteristic.

  According to the third aspect, the value related to the characteristic when the value related to the state is different from the predetermined value is calculated based on the value related to the actually measured characteristic. Thereby, the characteristic value in a desired combination can be obtained without actually measuring the characteristic value for all combinations of the output hydraulic pressure and the value related to the state. For this reason, it is possible to obtain a value related to a highly accurate characteristic while omitting the trouble of actual measurement.

  In the hydraulic control apparatus for an automatic transmission according to the fourth aspect of the invention, in addition to the configuration of the first aspect, the storage means measures the output hydraulic pressure when the value relating to the state becomes a predetermined value. When the output hydraulic pressure becomes a predetermined pressure, the value related to the characteristic obtained by the above is stored in correspondence with the predetermined value and each output hydraulic pressure. Means for storing the value relating to the characteristic obtained by doing so in correspondence with the value relating to each state and a predetermined pressure. The hydraulic control device further includes means for calculating a value related to the characteristic when the value related to the state is different from the predetermined value and the output hydraulic pressure is different from the predetermined pressure based on the value related to the characteristic.

  According to the fourth aspect of the invention, the value related to the characteristic when the value related to the state is different from the predetermined value and the output hydraulic pressure is different from the predetermined pressure is calculated based on the actually measured value related to the characteristic. Thereby, the characteristic value in a desired combination can be obtained without actually measuring the characteristic value for all combinations of the output hydraulic pressure and the value related to the state. For this reason, it is possible to obtain a value related to a highly accurate characteristic while omitting the trouble of actual measurement.

  In the hydraulic control device for an automatic transmission according to the fifth invention, in addition to the configuration of any one of the first to fourth inventions, the value relating to the state is a pressure.

  According to the fifth aspect, the output hydraulic pressure of the pressure adjusting unit is affected by the original hydraulic pressure. Therefore, the output hydraulic pressure can be accurately controlled by storing a value related to the characteristic of the output hydraulic pressure with respect to the original hydraulic pressure and controlling the pressure adjusting unit based on the value related to the characteristic.

  In the hydraulic control apparatus for an automatic transmission according to the sixth aspect, in addition to the configuration of any one of the first to fourth aspects, the value related to the state is temperature.

  According to the sixth invention, the output hydraulic pressure of the pressure adjusting unit is affected by the temperature of the hydraulic oil supplied to the pressure adjusting unit. Therefore, it is possible to accurately control the output hydraulic pressure by storing a value related to the characteristic of the output hydraulic pressure with respect to the temperature of the hydraulic oil and controlling the pressure adjusting unit based on the value related to the characteristic.

  In the hydraulic control device for an automatic transmission according to the seventh aspect, in addition to the configuration of any one of the first to fourth aspects, the values relating to the state are pressure and temperature.

  According to the seventh invention, the output pressure of the pressure adjusting unit is affected by the original hydraulic pressure and the temperature of the hydraulic oil supplied to the pressure adjusting unit. Therefore, it is possible to accurately control the output hydraulic pressure by storing the value related to the characteristic of the output hydraulic pressure with respect to the original hydraulic pressure and the temperature and controlling the pressure adjusting unit based on the value related to the characteristic.

  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.

<First Embodiment>
A vehicle equipped with a hydraulic control apparatus according to a first embodiment of the present invention will be described with reference to FIG. This vehicle is an FF (Front engine Front drive) vehicle. A vehicle other than FF may be used.

  The vehicle includes an engine 1000, a transmission 2000, a planetary gear unit 3000 that forms part of the transmission 2000, a hydraulic circuit 4000 that forms part of the transmission 2000, a differential gear 5000, a drive shaft 6000, and front wheels. 7000 and ECU (Electronic Control Unit) 8000.

  Engine 1000 is an internal combustion engine that burns a mixture of fuel and air injected from an injector (not shown) in a combustion chamber of a cylinder. The piston in the cylinder is pushed down by the combustion, and the crankshaft is rotated. An external combustion engine may be used instead of the internal combustion engine. Further, a rotating electrical machine or the like may be used instead of the engine 1000.

  Transmission 2000 includes a planetary gear unit 3000 and a hydraulic circuit 4000. Transmission 2000 changes the rotational speed of the crankshaft to a desired rotational speed by forming a desired gear stage. The output gear of transmission 2000 is meshed with differential gear 5000. The planetary gear unit 3000 and the hydraulic circuit 4000 will be described in detail later.

  A drive shaft 6000 is connected to the differential gear 5000 by spline fitting or the like. Power is transmitted to the left and right front wheels 7000 via the drive shaft 6000.

  The ECU 8000 is connected to a vehicle speed sensor 8002, a position switch 8005 of a shift lever 8004, and an accelerator opening sensor 8007 of an accelerator pedal 8006 via a harness or the like.

  The vehicle speed sensor 8002 detects the vehicle speed of the vehicle from the rotational speed of the drive shaft 6000, and transmits a signal representing the detection result to the ECU 8000. The position of shift lever 8004 is detected by position switch 8005, and a signal representing the detection result is transmitted to ECU 8000. Corresponding to the position of the shift lever 8004, the gear stage of the transmission 2000 is automatically formed. Further, a manual shift mode in which the driver can select an arbitrary gear stage may be selected according to the driver's operation. Throttle opening sensor 8006 detects the opening of accelerator pedal 8006 and transmits a signal representing the detection result to ECU 8000.

  The ECU 8000 determines whether the vehicle is in a desired running state based on the signals sent from the vehicle speed sensor 8002, the position switch 8005, the accelerator opening sensor 8007, etc., the map and the program stored in the memory 8100. To control.

  The planetary gear unit 3000 will be described with reference to FIG. Planetary gear unit 3000 is connected to a torque converter 3200 having an input shaft 3100 coupled to a crankshaft. The 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 the gear case 3600. , C1 clutch 3640, C2 clutch 3650, and one-way clutch F3660.

The first set 3300 is a single pinion type planetary gear mechanism. First set 330
0 includes a sun gear S (UD) 3310, a pinion gear 3320, a ring gear R (UD) 3330, and a carrier C (UD) 3340.

  Sun gear S (UD) 3310 is fixed to output shaft 3210 of torque converter 3200. Pinion gear 3320 is rotatably supported by carrier C (UD) 3340. Pinion gear 3320 is engaged 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 engaged 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 engaged 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 output shaft 3210 of torque converter 3200 by C1 clutch 3640. Ring gear R (1) (R (2)) 3450 is fixed to gear case 3600 by B2 brake 3620 and connected to output shaft 3210 of torque converter 3200 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.

  FIG. 3 is an operation table showing the relationship between each gear position and the operation state of each clutch and each brake. “◯” represents engagement. “X” represents release. “◎” represents engagement only during engine braking. “Δ” represents engagement only during driving. By operating each brake and each clutch with the combination shown in this operation table, a forward gear stage of 1st to 6th speed and a reverse gear stage are formed.

  Since the one-way clutch F3660 is provided in parallel with the B2 brake 3620, as indicated by “エ ン ジ ン” in the operation table, the driving state from the engine side when the first gear (1ST) is formed (during acceleration) There is no need to engage the B2 brake 3620. In the present embodiment, one-way clutch F3660 prevents rotation of ring gear R (1) (R (2)) 3450 when the first gear is driven. When the engine brake is applied, the one-way clutch F3660 does not prevent the ring gear R (1) (R (2)) 3450 from rotating.

  The hydraulic circuit 4000 will be described with reference to FIG. FIG. 4 shows only a part of the hydraulic circuit 4000 related to the present invention. The hydraulic circuit 4000 includes an oil pump 4004, a manual valve 4100, a solenoid modulator valve 4200, a primary regulator valve 4202, an SL1 linear solenoid (hereinafter referred to as SL (1)) 4210, and an SL2 linear solenoid (hereinafter referred to as “hereinafter referred to as SL2”). 4220, SL3 linear solenoid (hereinafter referred to as SL (3)) 4230, SL4 linear solenoid (hereinafter referred to as SL (4)) 4240, and SLT linear solenoid (hereinafter referred to as SL (2)). And 4300).

  Oil pump 4004 is connected to the crankshaft of engine 1000 and is driven by the rotation of the crankshaft to generate hydraulic pressure. The hydraulic pressure generated by the oil pump 4004 is adjusted by a primary regulator valve 4202 that operates using the throttle pressure controlled by the SLT 4300 as a pilot pressure, thereby generating a line pressure. The higher the throttle pressure, the higher the line pressure. The line pressure is supplied to the manual valve 4100, the solenoid modulator valve 4200, and the SL (4) 4240 via the PL oil passage 4010.

  Manual valve 4100 is coupled to shift lever 8004. The position of the spool of the manual valve 4100 is changed according to the position of the shift lever 8004. When the spool is in the drive position (D), the line pressure is supplied to the D range oil passage 4102. When the spool is in the reverse position (R), the hydraulic pressure generated by the oil pump 4004 is supplied to the R range oil passage.

  The solenoid modulator valve 4200 adjusts the line pressure to a constant pressure. Solenoid modulator valve 4200 is connected to SLT 4300. The hydraulic pressure (solenoid modulator pressure) adjusted to a constant pressure by the solenoid modulator valve 4200 is supplied to the SLT 4300.

  SL (1) 4210 is a normally closed type linear solenoid valve that shuts off the hydraulic pressure when not energized. SL (1) 4210 is connected to D-range oil passage 4102. SL (1) 4210 controls the hydraulic pressure supplied to the servo of the C1 clutch 3640.

  SL (2) 4220 is a normally closed type linear solenoid valve that shuts off hydraulic pressure when not energized. SL (2) 4220 is connected to D-range oil passage 4102. SL (2) 4220 controls the hydraulic pressure supplied to the servo of C2 clutch 3650.

  SL (3) 4230 is a normally closed type linear solenoid valve that shuts off the hydraulic pressure when not energized. SL (3) 4230 is connected to the D-range oil passage 4102. SL (3) 4230 controls the hydraulic pressure supplied to the servo of the B1 brake 3610.

  SL (4) 4240 is a normally closed linear solenoid valve that shuts off hydraulic pressure when not energized. SL (4) 4240 is connected to PL oil passage 4010. SL (4) 4240 controls the hydraulic pressure supplied to the servo of the B3 brake 3630.

  The SLT 4300 is a normally open type linear solenoid valve capable of supplying hydraulic pressure when not energized. The SLT 4300 adjusts the solenoid modulator pressure in accordance with the torque information generated based on the accelerator opening of the accelerator pedal 8006, the intake air amount of the engine 1000, the water temperature of the engine 1000, the rotational speed of the engine 1000, etc. To produce. The throttle pressure adjusted by the SLT 4300 is supplied to the primary regulator valve 4202.

  An on / off solenoid is used in place of SL (1) 4210, SL (2) 4220, SL (3) 4230, SL (4) 4240 and SLT 4300, and the hydraulic pressure is controlled by duty control. The hydraulic pressure may be controlled in combination with the control valve.

  SL (1) 4210, SL (2) 4220, SL (3) 4230, SL (4) 4240, and SLT 4300 are controlled by ECU 8000 so that a desired output hydraulic pressure is obtained.

  The ECU 8000 calculates a command pressure to each linear solenoid based on a map stored in the memory 8100 so as to obtain a desired output hydraulic pressure, and controls each linear solenoid at a duty ratio that satisfies this command pressure. To do.

  However, the output hydraulic pressures of SL (1) 4210, SL (2) 4220, SL (3) 4230, SL (4) 4240 and SLT 4300 are different from the command pressure due to the influence of the original hydraulic pressure and the hydraulic oil temperature. There is a case.

  Furthermore, the characteristics of the output oil pressure with respect to the original oil pressure and the oil temperature of the hydraulic oil vary depending on individual differences in the components. Therefore, it is necessary to control SL (1) 4210, SL (2) 4220, SL (3) 4230, SL (4) 4240, and SLT 4300 in consideration of the characteristics of output hydraulic pressure in each individual.

  With reference to FIG. 5, the characteristic value of the output hydraulic pressure stored in memory 8100 will be described. FIG. 5 shows the characteristic value of the output hydraulic pressure of SL (1) 4210. The characteristic values of the output hydraulic pressure of SL (2) 4220, SL (3) 4230, SL (4) 4240, and SLT 4300 are the same as the characteristic values of the output hydraulic pressure of SL (1) 4210. Therefore, detailed description thereof will not be repeated here.

  In the memory 8100, differences A (0) to E (4) between the command pressures A (0) to E (0) of the output hydraulic pressure and the actual output hydraulic pressure are stored as characteristic values (values related to the characteristics) of the output hydraulic pressure. Has been. These characteristic values are stored corresponding to the original hydraulic pressures P (1) to P (4) and the command pressures A (0) to E (0) of the respective output hydraulic pressures. Such characteristic values are stored for each linear solenoid. The actual output hydraulic pressure with respect to the output hydraulic pressure command pressure may be stored.

  The ECU 8000 controls each linear solenoid by correcting the command pressure of the output hydraulic pressure based on the characteristic value stored in the memory 8100 so that the actual output hydraulic pressure becomes a desired output hydraulic pressure.

  The characteristic value is obtained by actual measurement in a state in which the transmission 2000 is assembled or in a state in which each linear solenoid is incorporated in the valve body. Note that the method of obtaining the characteristic value is not limited to this.

  The obtained characteristic value is encoded into a two-dimensional code 9000 such as a barcode. This two-dimensional code 9000 is affixed to the surface of the transmission 2000 as shown in FIG. In the vehicle manufacturing process, the characteristic value is stored in the memory 8100 by reading the two-dimensional code attached to the transmission 2000 by the reading device 9002. Note that the transmission 2000 may be provided with a memory storing characteristic values, and the characteristic values may be read from the memory.

  The operation of ECU 8000 of the control device according to the present embodiment based on the above structure will be described. Here, the operation of ECU 8000 when controlling the output hydraulic pressure of SL (1) 4210 will be described. Controlling the output hydraulic pressure of SL (2) 4220, SL (3) 4230, SL (4) 4240 and SLT 4300 is the same as controlling the output hydraulic pressure of SL (1) 4210. Therefore, detailed description thereof will not be repeated here.

  While the vehicle is traveling, the command pressure of the output hydraulic pressure of SL (1) 4210 is calculated from the map stored in the memory 8100. At the same time, the line pressure that is the original hydraulic pressure of SL (1) 4210 is calculated. The line pressure is calculated based on the throttle pressure (the output hydraulic pressure of the SLT 4300).

  Here, it is assumed that the command pressure of the output hydraulic pressure is calculated as C (0) and the line pressure is calculated as P (2). The characteristic value C (2) in the combination of the command pressure C (0) and the line pressure P (2) is read from the map stored in the memory 8100. Based on this characteristic value C (2), the command pressure of SL (1) 4210 is corrected so that the actual output oil pressure becomes a desired output oil pressure.

  For example, when the actual output oil pressure is higher than the command pressure, the command pressure is reduced. Conversely, when the actual output oil pressure is lower than the command pressure, the command pressure is increased. As a result, the output hydraulic pressure can be accurately controlled.

  As described above, the ECU according to the present embodiment stores the characteristic value of the output hydraulic pressure of the linear solenoid with respect to the original hydraulic pressure in the memory. The ECU corrects the command pressure of the output hydraulic pressure of the linear solenoid based on the stored characteristic value. As a result, the output hydraulic pressure can be accurately controlled.

  In the first embodiment described above, the characteristic value is stored in association with the original hydraulic pressure. However, as shown in FIG. 7, it may be stored in correspondence with the oil temperature of the hydraulic oil. Thereby, the output hydraulic pressure affected by the oil temperature of the hydraulic oil can be controlled with high accuracy. Further, the characteristic value may be stored in correspondence with both the original hydraulic pressure and the oil temperature.

<Second Embodiment>
The second embodiment of the present invention will be described with reference to FIGS. In the first embodiment described above, characteristic values measured for all combinations of output hydraulic pressure and original hydraulic pressure are stored. However, in the present embodiment, characteristic values measured for some combinations are stored. I remember it. Other structures are the same as those in the first embodiment. The function about them is the same. Therefore, detailed description thereof will not be repeated here.

  The characteristic values stored in the memory 8100 will be described with reference to FIG. FIG. 8 shows the characteristic value of the output hydraulic pressure of SL (1) 4210. The characteristic value of the output hydraulic pressure of SL (2) 4220, SL (3) 4230, SL (4) 4240 and SLT 4300 is the same as the characteristic value of the output hydraulic pressure of SL (1) 4210. Therefore, detailed description thereof will not be repeated here.

  As shown in FIG. 8, the memory 8100 stores characteristic values measured for the output hydraulic pressures A (0) to E (0) when the original hydraulic pressure is P (1). The characteristic value when the original hydraulic pressure is not P (1) is not stored. Instead, the memory 8100 stores a relational expression between the original hydraulic pressure and the characteristic value. That is, a relational expression representing how the characteristic value changes when the original oil pressure changes while the output oil pressure is constant is stored in the memory 8100. This relational expression is obtained in advance by actually measuring the characteristic value of the prototype of the transmission 2000 or by analyzing the output hydraulic pressure for analysis. The method for obtaining the relational expression is not limited to this. Further, the characteristic value calculated by the relational expression obtained in advance may be stored as a map.

  With reference to FIG. 9, a control structure of a program executed by ECU 8000 of the hydraulic control apparatus according to the present embodiment will be described.

  In step (hereinafter, step is abbreviated as S) 100, ECU 8000 calculates the command pressure of the output hydraulic pressure of each linear solenoid based on the map stored in memory 8100. In S102, ECU 8000 calculates the original hydraulic pressure of each linear solenoid based on the map stored in memory 8100.

  In S104, ECU 8000 reads the characteristic value stored in memory 8100. In S106, ECU 8000 determines whether or not the read characteristic value can be used. The ECU 8000 determines whether or not the read characteristic value can be used by determining whether or not the read characteristic value is actually measured by a combination of the calculated command pressure of the output hydraulic pressure and the original hydraulic pressure. Determine. ECU 8000 determines that the read characteristic value can be used when the read characteristic value is actually measured by a combination of the calculated output hydraulic pressure command pressure and the original hydraulic pressure. If the read characteristic value can be used (YES in S106), the process proceeds to S108. If not (NO in S106), the process proceeds to S110.

  In S108, ECU 8000 corrects the command pressure of the output hydraulic pressure based on the read characteristic value so that the actual output hydraulic pressure becomes a desired output hydraulic pressure. Thereafter, this process ends.

  In S110, ECU 8000 reads a relational expression between the original hydraulic pressure and the characteristic value from memory 8100. In S112, ECU 8000 uses the read relational expression and characteristic value to calculate a characteristic value in a combination of the calculated output oil pressure command pressure and the original oil pressure.

  In S114, ECU 8000 corrects the command pressure of the output hydraulic pressure based on the calculated characteristic value so that the actual output hydraulic pressure becomes a desired output hydraulic pressure. Thereafter, this process ends.

  The operation of ECU 8000 of the hydraulic control apparatus according to the present embodiment based on the above-described structure and flowchart will be described. Here, the operation of ECU 8000 when controlling the output hydraulic pressure of SL (1) 4210 will be described. Controlling the output oil pressure of SL (2) 4220, SL (3) 4230, SL (4) 4240 and SLT 4300 is the same as controlling the output oil pressure of SL (1) 4210. Therefore, detailed description thereof will not be repeated here.

  While the vehicle is traveling, the command pressure of the output hydraulic pressure of SL (1) 4210 is calculated based on the map stored in the memory 8100 (S100), and the line pressure that is the original hydraulic pressure of SL (1) 4210 is calculated. (S102).

  Further, the characteristic value stored in the memory 8100 is read (S104), and whether or not the read characteristic value is actually measured by a combination of the calculated command pressure of the output hydraulic pressure and the line pressure. Is discriminated, it is discriminated whether or not the read characteristic value is usable (S106). If the read characteristic value is usable (YES in S106), the command pressure of the output hydraulic pressure is corrected with the read characteristic value (S108).

  On the other hand, when the read characteristic value is not actually measured by the combination of the calculated command pressure of the output hydraulic pressure and the line pressure and cannot be used (NO in S106), the original hydraulic pressure (line pressure) ) And the characteristic value are read from the memory 8100 (S110).

  Using this relational expression and the read characteristic value, the characteristic value in the combination of the calculated output hydraulic pressure command pressure and the line pressure is calculated (S112). Thereby, it is possible to obtain characteristic values in other combinations without actually measuring characteristic values for combinations of command pressures and line pressures of all output hydraulic pressures. The command pressure of the output hydraulic pressure is corrected using the characteristic value calculated in this way (S114). Therefore, it is possible to accurately control the output hydraulic pressure while omitting the trouble of actually measuring the characteristic value.

  As described above, the ECU of the hydraulic control apparatus according to the present embodiment stores actually measured characteristic values in a memory for a predetermined combination of output hydraulic pressure command pressure and original hydraulic pressure. The ECU calculates characteristic values for other combinations based on the stored characteristic values. Thereby, the trouble of actually measuring the characteristic value can be omitted.

  In the second embodiment described above, the relational expression between the original hydraulic pressure and the output hydraulic pressure is obtained in advance. However, as shown in FIG. 10, the command pressure of the output hydraulic pressure is maintained at A (0), The characteristic value when the oil pressure is changed may be measured and stored for each transmission 2000. In this case, a relational expression between the original hydraulic pressure and the output hydraulic pressure can be obtained for each individual based on the actually measured characteristic value. As a result, the characteristic value can be calculated with higher accuracy than in the second embodiment, and the output hydraulic pressure can be controlled with higher accuracy.

  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.

1 is a control block diagram showing a vehicle equipped with a hydraulic control device according to a first embodiment of the present invention. It is a skeleton figure which shows a planetary gear unit. It is a figure which shows the operation | movement table | surface showing the response | compatibility of each gear stage, each brake, and each clutch. It is a figure which shows a part of hydraulic circuit. It is a figure (the 1) which shows the characteristic value memorize | stored in the memory of the hydraulic control apparatus which concerns on the 1st Embodiment of this invention. It is a figure which shows the storage method of a characteristic value. It is FIG. (2) which shows the characteristic value memorize | stored in the memory of the hydraulic control apparatus which concerns on the 1st Embodiment of this invention. It is FIG. (1) which shows the characteristic value memorize | stored in the memory of the hydraulic control apparatus which concerns on the 2nd Embodiment of this invention. It is a flowchart which shows the control structure of the program which ECU of the hydraulic control apparatus which concerns on the 2nd Embodiment of this invention performs. It is FIG. (2) which shows the characteristic value memorize | stored in the memory of the hydraulic control apparatus which concerns on the 2nd Embodiment of this invention.

Explanation of symbols

  2000 Transmission, 3000 Planetary gear unit, 3610 B1 brake, 3620 B2 brake, 3630 B3 brake, 3640 C1 clutch, 3650 C2 clutch, 3660 One-way clutch F, 4000 Hydraulic circuit, 4004 Oil pump, 4010 PL oil path, 4100 Manual valve 4200 Solenoid modulator valve, 4202 Primary regulator valve, 4210 SL1 linear solenoid, 4220 SL2 linear solenoid, 4230 SL3 linear solenoid, 4240 SL4 linear solenoid, 4300 SLT linear solenoid, 8000 ECU, 8100 Memory, 9000 Two-dimensional code, 9002 Reading device .

Claims (7)

A hydraulic control device for an automatic transmission including a pressure adjusting unit for adjusting hydraulic pressure of hydraulic oil,
Under a plurality of conditions in which the output hydraulic pressure of the pressure adjusting unit is different, the value related to the characteristic of the output hydraulic pressure with respect to the hydraulic oil supplied to the pressure adjusting unit is made to correspond to the value related to the state of the hydraulic oil and each output hydraulic pressure. Storage means for storing
And a control unit for controlling the pressure adjusting unit based on a value related to the characteristic.   The storage means stores, for each output hydraulic pressure, a value related to the characteristic obtained by actual measurement with different values related to the state, corresponding to the value related to each state and each output hydraulic pressure. The hydraulic control device for an automatic transmission according to claim 1, comprising: The storage means corresponds to the predetermined value and each output hydraulic pressure with respect to the value obtained by actually measuring the output hydraulic pressure when the value related to the state becomes a predetermined value. Means for storing and storing,
The automatic transmission according to claim 1, wherein the hydraulic control device further includes means for calculating a value related to the characteristic when the value related to the state is different from the predetermined value based on the value related to the characteristic. Hydraulic control device for the machine. The storage means
For each output hydraulic pressure, a value related to a characteristic obtained by actual measurement when a value related to the state becomes a predetermined value is stored in association with the predetermined value and each output hydraulic pressure. Means of
When the output hydraulic pressure becomes a predetermined pressure, the value related to the characteristic obtained by actually measuring the value related to the state is made to correspond to the value related to each state and the predetermined pressure. Including means for storing,
The hydraulic control device calculates a value related to the characteristic when the value related to the state is different from the predetermined value and the output hydraulic pressure is different from the predetermined pressure based on the value related to the characteristic. The hydraulic control device for an automatic transmission according to claim 1, further comprising:   The hydraulic control device for an automatic transmission according to claim 1, wherein the value related to the state is a pressure.   The hydraulic control device for an automatic transmission according to claim 1, wherein the value related to the state is a temperature.   The hydraulic control device for an automatic transmission according to any one of claims 1 to 4, wherein the values relating to the state are pressure and temperature.

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